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RENEWABLE ENERGY APPLICATIONS IN RESIDENTIAL HOMES
AND SMALL-SCALE DESALINATION PROCESSES
A THESIS SUBMITTED TO THE GRADUATE DIVISION OF THE UNIVERSITY OF HAWAI‘I AT MĀNOA IN PARTIAL FULFILLMENT OF
THE REQUIREMENTS FOR THE DEGREE OF
MASTER OF SCIENCE
IN
MECHANICAL ENGINEERING
DECEMBER 2012
By Tyler Thomas Phillips
Thesis Committee:
Weilin Qu, Chairperson David Garmire Reza Ghorbani
©Copyright 2012
By
Tyler Thomas Phillips
All Rights Reserved
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ACKNOWLEDGEMENTS
There were many people who worked on the mechanical system since the beginning of engineering’s involvement on the Team Hawai‘i Solar Decathlon home. A special thanks needs to be made to Team Hawai‘i’s Project Manager David Cook, School of Architecture, who began the work and designed the initial mechanical system upon which the final design was based. The mechanical team was comprised of a group of Mechanical Engineering undergraduate students: Trevor Johnson, Kwok Hin Ko, Byron Blandchard, Huilin Xie, Chaoming Liang, Sonya Ling, and Angela Menghini. These students’ work was influential in the completion of the overall design. Huilin Xie did a tremendous job taking the lead on the Fire Protection system and worked closely with industry professionals from Thermal Engineering Corporation to complete a safe and effective fire suppression system design. Melvin Harano and Derick Kam from Thermal Eng. Corp (through collaboration with SFPE Hawai‘i) gave of lot of time and effort to help Huilin and the team complete this task.
Of course, without faculty support none of this would have been possible. The lead Mechanical Engineering faculty, Dr. Weilin Qu, formed the mechanical team after being approached by the Principal Investigator of Team Hawai‘i, David Rockwood from the School of Architecture. Dr. Qu’s constant guidance and support were pivotal in the design completion as well as the construction planning by finding industrial contacts for design assistance and product donations. Jim Moore, from Ferguson Hawaii, assisted not only in the design of the solar thermal system but also in offers of equipment procurement. Scott Inatsaka, from WSP Lincolne Scott, worked with the team to design the HVAC system to ensure code compliance and maximum efficiency. The plumbing system design was overseen by Norman Tada of Oahu Plumbing & Sheet Metal, Ltd, of the Sen Plex Corporation. The knowledge and experience of these industry professionals was essential for the mechanical team to complete all the systems, and their help is greatly appreciated.
The work on HDH desalination would have also not been possible without the constant guidance and support of Dr. Weilin Qu. The tremendous research and development work done by Riley McGivern on his HDH system with direct contact condensation, was the basis for this work. The resources and funding provided by the REIS program at UH Mānoa for this research is greatly appreciated and has allowed this work to be done.
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ABSTRACT:
The conservation and replenishing of our world’s energy and fresh water sources is of pivotal importance for the next generations. The global fossil-fuel reserves are dwindling as are the fresh water aquifers. The need for fresh water, however, may not be as apparent as the energy needs; especially in affluent countries where rising gasoline and electricity prices will be noticed by many, and where piped water supply is standard but bottled water is preferred by most. Even though this fresh water need may be unnoticed in the most developed countries the underground aquifers upon which they rely for bottled water production are depleting and going less restored each year. In reaction to the continual increasing of energy costs, the United States has experienced a surge of renewable energy research and has implemented requirements for the integration of many large-scale renewable energy generation methods all over the country. However, other much more impoverished countries have been utilizing small-scale renewable and sustainable sources of energy, food, and water for generations and the US could learn much from these “undeveloped” nations. There are many rural areas in developing countries where fresh water sources are lacking severely and there is high need for local water production with low energy and costs demands. There is also a potential for a range of classes within the developed countries to achieve sustainability through the use of small-scale renewable methods which can be adapted for any style of living. This work, therefore, is a comprisal of two projects which address the energy and fresh water needs that are facing our world today.
The first section of this work focuses on the effective integration of new and old sustainable methods of renewable energy generation into residential homes. This was done through a university wide project to design and build a net-zero home for the Department of Energy’s Solar Decathlon 2011 competition. An esthetically creative, highly efficient, net-zero home design will be presented which is coupled with the innovative sustainable food and oxygen production system known as aquaponics. This modern home not only provides its occupants will all energy needs through PV and solar thermal panels, but also with fresh produce and fish through the aquaponics system. The use of a thermal storage system with phase change materials is implemented to provide highly efficient home heating and cooling
The second section then focuses on the fresh water need, specifically of those rural areas of developing countries where conditions are dry and solar insolation is high. The high potential of these areas for solar energy generation through PV and solar thermal panels make them prime locations for the integration of solar desalination processes for fresh water production. A number of solar humidification dehumidification (HDH) desalination processes are presented and the optimal configurations identified for use in decentralized arid regions. A detailed analysis of the top modeling techniques used for the optimization of these processes is also described.
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TABLE OF CONTENTS
ACKNOWLEDGEMENTS ................................................................................................................. iii
ABSTRACT ..................................................................................................................................... iv
LIST OF TABLES ............................................................................................................................ viii
LIST OF FIGURES ........................................................................................................................... viii
SECTION 1: U.S. DEPARTMENT OF ENERGY SOLAR DECATHLON 2011: TEAM HAWAII MECHANICAL SYSTEMS .............................................................................. 1
CHAPTER 1 – INTRODUCTION TO SOLAR DECATHLON........................................................................... 2
1.1 Background of Solar Decathlon .................................................................................................... 2
1.2 Team Hawai‘i Objectives .............................................................................................................. 3
1.3 General Competition Rules and Criteria ....................................................................................... 4
1.3.1 Deliverables ........................................................................................................................... 5
1.3.2 On‐Site Construction ............................................................................................................. 6
1.3.3 Competition Days .................................................................................................................. 7
1.3.4 On‐Site Disassembly .............................................................................................................. 9
CHAPTER 2 – MECHANICAL SYSTEMS ................................................................................................... 10
2.1 Fire Protection System ............................................................................................................... 10
2.1.1 Fire Protection Requirements ............................................................................................. 10
2.1.2 Fire Protection Design Plans ................................................................................................ 10
2.1.3 Fire Protection Design Specifications .................................................................................. 12
2.1.4 Fire Protection Construction and Disassembly ................................................................... 13
2.2 Plumbing System ........................................................................................................................ 14
2.2.1 Plumbing Requirements ...................................................................................................... 14
2.2.2 Plumbing Design Plans ........................................................................................................ 15
2.2.3 Plumbing Design Specifications ........................................................................................... 18
2.2.4 Plumbing Construction and Disassembly ............................................................................ 18
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2.3 Heating, Ventilation, and Air Conditioning System .................................................................... 20
2.3.1 Heating, Ventilation, and Air Conditioning (HVAC) Requirements ..................................... 20
2.3.2 HVAC Design Plans .............................................................................................................. 20
2.3.3 HVAC Design Specifications ................................................................................................. 22
2.3.4 HVAC Construction and Disassembly .................................................................................. 23
2.4 Solar Thermal System ................................................................................................................. 25
2.4.1 Solar Thermal Requirements ............................................................................................... 25
2.4.2 Solar Thermal Design Plans ................................................................................................. 25
2.4.3 Solar Thermal Design Specifications ................................................................................... 27
2.4.4 Solar Thermal Construction and Disassembly ..................................................................... 27
CHAPTER 3 – RESULTS AND DISCUSSIONS ........................................................................................... 29
3.1 Summary of Team Hawai‘i’s Solar Decathlon 2011 .................................................................... 29
SECTION 2: REVIEW AND ANALYSIS OF HUMIDIFICATION DEHUMIDIFICATION DESALINATION PROCESSES WITH FOCUS ON DIRECT CONTACT CONDENSATION ............. 31
CHAPTER 4 – INTRODUCTION TO WATER DESALINATION ................................................................... 32
4.1 Background on Fresh Water Needs ............................................................................................ 32
4.1.1 The Global Need .................................................................................................................. 33
4.2 Background on Water Desalination ............................................................................................ 37
4.2.1 Thermal (Phase‐Change) Processes .................................................................................... 38
4.2.2 Membrane Processes .......................................................................................................... 42
CHAPTER 5 – THE HUMIDIFICATION DEHUMIDIFICATION THERMAL DESALINATION PROCESS ......... 45
5.1 Humidification Dehumidification (HDH) Process ....................................................................... 45
5.1.1 HDH Classifications .............................................................................................................. 46
5.1.2 Performance Parameters .................................................................................................... 49
5.2 Literature Review of HDH Systems and Components ................................................................ 51
5.2.1 Closed‐Air Open‐Water (CAOW) Systems ........................................................................... 51
5.2.2 Closed‐Water Open‐Air (CWOA) Systems ........................................................................... 53
5.2.3 Humidifier/Evaporator ........................................................................................................ 55
5.2.4 Dehumidifier/Condenser ..................................................................................................... 57
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5.2.5 Heat Exchangers .................................................................................................................. 59
CHAPTER 6 – THE POTENTIAL OF HDH WITH DIRECT CONTACT CONDENSATION ............................... 61
6.1 The Diffusion Driven Desalination (DDD) Process ...................................................................... 61
6.2 Analysis Methods and Findings .................................................................................................. 62
6.3 Summary of Analysis Methods and Findings .............................................................................. 77
CHAPTER 7 – RESULTS AND DISCUSSIONS ........................................................................................... 80
REFERENCES ................................................................................................................................ 83
APPENDIX A: SOLAR DECATHLON WATER BUDGET .......................................................... ATTACHED
APPENDIX B: MECHANICAL SPECIFICATIONS SHEETS ‐ DIVISION: 21, 22, 23, 28 ............... ATTACHED
APPENDIX C: TEAM HAWAI‘I FULL DRAWING SET ............................................................ ATTACHED
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LIST OF TABLES
SECTION 2 – HDH DESALINATION
Table 1: Disparities between rural and urban areas in water sources, 1990‐2010 [1] ..................... 36
Table 2: Top 10 desalinated water producing countries [2] ........................................................... 38
LIST OF FIGURES
SECTION 1 – SOLAR DECATHLON
Figure 1: Sheet F‐602/A1 showing the Fire Suppression Diagram with keynoting ............................ 11
Figure 2: F‐901/A1 shows an isometric view of the fire suppression system ................................... 12
Figure 3: F‐603/D1 showing fire sprinkler section detail of piping connected to rib ........................ 13
Figure 4: A1/P‐602 Domestic water supply diagram with pipe sizes and annotations ...................... 16
Figure 5: C4/P‐602 Sanitary waste and vent diagram with pipe sizing and annotations ................... 17
Figure 6: A1/P‐901 Isometric view of domestic water supply piping and tanks ............................... 19
Figure 7: A1/M‐101 showing HVAC equipment and distribution plan ............................................. 22
Figure 8: A1/M‐102 showing spill containment plan for all systems of the house ........................... 24
Figure 9: A1/M‐603 showing solar water diagram ......................................................................... 27
Figure 10: A1/M‐902 showing solar water isometrics of solar water panels and tanks .................... 28
SECTION 2 – HDH DESALINATION
Figure 11: Drinking water coverage trends by developing regions, 1990‐2010 [1] ........................... 36
Figure 12: Simple HDH diagram with solar collector ...................................................................... 46
Figure 13: CAOW cycle diagram .................................................................................................... 48
Figure 14: CWOA cycle diagram .................................................................................................... 48
Figure 15: Flow diagram for innovative diffusion driven desalination process [13] .......................... 62
Figure 16: Flow diagram for the DDD process [16] ......................................................................... 66
Figure 17: Differential control volume for the direct contact condensation tower [16] ................... 66
Figure 18: Schematic diagram of DDD experimental facility with twin condensation towers [17] .... 69
Figure 19: Flow diagram procedure for computation of the counter‐current flow condenser [17] ... 70
Figure 20: Flow diagram of Riley’s HDH system with direct contact condensation [14] ................... 71
Figure 21: Control volume used for evaporator and condenser towers, showing the interactions between the liquid, gas/vapor, and solid packing material [18] ...................................................... 72
Figure 22: Process flow diagram for solar diffusion driven desalination system [19] ....................... 75
SECTION 1:
U.S. DEPARTMENT OF ENERGY SOLAR DECATHLON 2011:
TEAM HAWAI‘I MECHANICAL ENGINEERING SYSTEMS
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CHAPTER 1 - INTRODUCTION TO SOLAR DECATHLON
1.1 BACKGROUND OF SOLAR DECATHLON
The U.S. Department of Energy Solar Decathlon is an event that tests collegiate
teams from all over the world to design and build solar-powered net-zero homes which are
aesthetically and financially competitive as well as extremely energy-efficient. Not only are
teams judged on affordability, architecture, engineering, and over-all energy balance but also
on market appeal, communications, comfort zone, hot water, appliances, and even home
entertainment. The winner of the decathlon is the team that scores the highest over-all from
the judges based on the criteria described. The 2011 Solar Decathlon is the fifth decathlon
event held biennially since the first one held in 2002. The event has since expanded to 65
teams with 10,000 students over three competitions; Solar Decathlon Europe 2012, Solar
Decathlon China 2013, and the U.S. Department of Energy Solar Decathlon 2013. All Solar
Decathlon events have been open and free to the public and have encouraged visitors to tour
the homes and learn about energy conservation of all types in various booths around the
Solar Decathlon village.
The decathlon gives students the opportunity to display their hard work through the
houses and to interact with the other teams and industry professionals. This unique
experience prepares students to enter into the clean-energy workforce and gives them an
advantage in finding jobs by contact with industry throughout the project. The Solar
Decathlon event encourages young students to consider the repercussions of their energy
usage and the need for implementation of renewable resources and sustainable energy for
homes and industry. Through the nearly 17,000 collegiate participants who have competed
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in decathlons so far, millions of spectators, ranging from family and friends of participants to
visitors and industry professionals, have been introduced to future smart homes capable of
saving money and, more importantly, energy for its occupants. Whether exposure to the
decathlon comes from word of mouth, being at a decathlon event, or through media, the
message is all the same; the youth of this generation is ready to make a change and is
showing the world how today.
1.2 TEAM HAWAI‘I OBJECTIVES
The challenge for the 2011 Solar Decathlon was to design and build a custom
modularized single family dwelling with net-zero (or better) energy usage to compete with
19 other collegiate teams from around the world in Washington D.C.. Team Hawai‘i
architects visualized an ergonomic tubular structure which the electrical and mechanical
engineering teams were tasked to design energy efficient systems within and around. The
mechanical systems were designed in conjunction with building codes and competition rules
and requirements in order to meet all the needs of the home’s occupants in the most energy
efficient way possible. These needs were determined by the Solar Decathlon judges and
demonstrate the average usage of appliances by a single family household of one to three.
Just as the shape of the house proposed by Team Hawai‘i goes outside the norm, the
mechanical equipment and techniques around the home also strayed away from the average
systems. Utilizing new concepts and materials was not only done to fit the shape of the
house but also to improve on the overall home efficiency and sustainability in the future.
The integration of aesthetics and functionality was a major challenge in this project and
pushed the engineers and architects to work very closely together, which yielded a highly
unique and strongly detailed design.
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The mechanical systems of the 2011 Solar Decathlon Team Hawai‘i house are
comprised of four sub-systems: HVAC, Plumbing, Solar Thermal, and Fire Protection. The
heating, ventilation, and air conditioning (HVAC) system utilizes a heat-pump in conjunction
with a thermal mass pillow tank filled with water and phase change material (PCM). The
plumbing system consists of PEX flexible piping for hot and cold water delivery and recycles
grey water for use in the house’s aquaponics system. The solar thermal system has two solar
panels and two hot water tanks that can provide the house with all its hot water needs. The
fire protection system also uses PEX flexible piping in combination with copper tubing for
fire suppression through six ceiling mounted sprinkler heads.
1.3 GENERAL COMPETITION RULES AND CRITERIA
The Solar Decathlon event has a strict code of rules and regulations that need to be in
place so that the decathlon can run smoothly and fairly. Each team is required to assign
positions to its key members such as Project Manager, Health and Safety Officer, Electrical
Engineer, Mechanical Engineer, and etc. These officers must conduct themselves in a
responsible fashion and encourage other team members to follow the necessary rules.
Contact with the Solar Decathlon administration is also very important to ensure the correct
interpretation of the rules and requirements. Any discrepancies, no matter how small, could
lead to penalties or even rejection from the competition. From the very beginning of design,
all regulations, even those pertaining to site operations and construction, must be taken into
account to ensure that there will not be large issues later down the road. However, as in any
construction project, there of course will be problems and changes will occur up to the time
of competition.
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For the mechanical teams the primary rules of importance are; Rule 4: Site
Operations, Rule 8: Energy, Rule 9: Liquids, and Rule 11: Contest Week. Within each Rule
there are many sub-rules, which must all be followed and/or clarified with Solar Decathlon
judges. The main contest criteria of concern for the mechanical teams are; Contest 3:
Engineering, Contest 6: Comfort Zone, Contest 7: Hot Water, Contest 8: Appliances, and
most importantly Contest 10: Energy Balance. Other contests, like Affordability, are taken
into account by the mechanical side but are not the primary focus.
1.3.1 Deliverables:
During the design process there are a number of deadlines for deliverables leading up
to the competition. These deliverables allow the competition coordinators and judges to
check over the plans of each team and ensure their cooperation with rules, regulations, and
building codes. If and when issues are found, the judges will relay these concerns to the team
and allow them time to fix and re-submit documentation. The primary set of drawings for
the house must be generated using the Autodesk Revit building information model (BIM).
The BIM shall also contain energy analysis models and a computer-animated walkthrough of
the home. The BIM will allow jury members to see a full view of each team’s project from
the small details of construction drawings, to an overview of assembly and disassembly, and
to the final artistic rendition of the home.
A project manual is also required and consists mostly of specification sheets, which
contain detailed product information on all the utilized materials and equipment. The
information found on the specification sheets are also integrated into the BIM, where all
materials and equipment are called out using keynoting according to the specification
numbers. Construction drawing sets are to be created using screen shots from the three-
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dimensional BIM. Audiovisual presentations are required for architectural, sales, and
engineering sides of the project. These presentations combine images from the 3-D house in
BIM, audio information and descriptions of the sections, and artistic visualizations in order to
create a professional message for judges and spectators at the competition. A detailed energy
analysis description is also required in the project manual, which describes the methods used
to calculate the heat gain and loss from the house, usually by some computational modeling
systems. A detailed water budget, which accounts for all water needs during the course of
the competition, is also required for the project manual.
Along with the BIM, project manual, and presentations, a web-site and a video walk
through of the home must be created. The web-site is a means for the team to communicate
with the public, especially locally, about the project and to gain support and spread the word
about the Solar Decathlon contest. The video walkthrough should be available through the
web-site and can also be played during the competition for spectators and judges.
1.3.2 On-Site Construction:
The competition begins with seven days of stand-alone assembly of the solar homes.
Most of the seven days of assembly allow for 24 hour work, and during these long days there
are many important rules and deadlines that must be met in order to be prepared for the
beginning of the contests. This construction phase is also judged and by completing quickly,
teams allow themselves more time to test and prep home systems for contest days. Some of
the rules and regulations each team should consider are described in the following.
Each team is financially responsible for any damage that is caused to the site during
construction, contests, and disassembly. All equipment, such as forklifts, is required to move
along a grass protection product provided by event organizers. Also, truck-mounted cranes
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or trailers need to stay on the gravel pathway. Ground penetration and impact on the grass
turf is of high concern for the event organizers and therefore restrictions and soil-bearing
pressure criteria must be followed for various footings around the homes. Generators are
allowed during assembly and disassembly days only and must meet National Park Services
noise regulations. All spills of any fluids from equipment and/or vehicles must be avoided
by use of secondary containment systems. During day five of assembly a water truck will
deliver a maximum of 1500 gallons to each home. A detailed water delivery plan is required
for each team to ensure safe and efficient delivery process. During assembly days no release
of water or other fluids is allowed from home into nearby storm drains. Lot conditions can
vary up to 18 vertical inches across the lot. Teams are allowed to send a representative to
scout the lot conditions during an organizer approved period and take measurements.
The solar envelope restrictions are another large consideration for the overall design
of the home including any roof mounted panels or equipment. Many other structural rules
and restrictions exists for the architectural design but are not mentioned in this report.
Overall, the main areas of concern for the mechanical teams are the turf impact of equipment
and tanks, the use of forklifts and cranes for moving and mounting equipment, and spill
containment especially during water delivery day.
1.3.3 Competition Days:
The seven days of house assembly are followed by nine days of competition during
which ten different contests occur and are graded by Solar Decathlon judges. The ten
contests are; Architecture, Market Appeal, Engineering, Communications, Affordability,
Comfort Zone, Hot Water, Appliances, Home Entertainment, and most importantly Energy
Balance. Each contest is graded on different specific criteria and results of the contests will
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be posted at different times as they are finished. The architecture, market appeal,
communications, and affordability contests are partly judged on materials already received
by judges prior to competitions days and also on the presentation and demonstration of these
items during the first few competition days. For this reason these results are announced early
into the contest days. However, the engineering, comfort zone, hot water, appliances, home
entertainment, and energy balance contests, are based on readings and measurements taken
over all nine contest days. Therefore the results of these contests are not delivered until the
day following the last day of contests. The final two contests to be judged are Engineering
and Energy Balance; the results of these two important contests will determine the overall
decathlon winners.
The specific contest criteria for the engineering contest; functionality, efficiency,
innovation, reliability, and documentation, are meant to grade the overall engineering effort
of each team. The energy balance contest is based purely on the net electrical energy, which
is the total amount energy produced minus the total amount used, of each home for the
entirety of the contest days. If a team has a net electrical energy greater than or equal to 0
kWh, then the team receives full points. Reduced points are given from 0 to -50 kWh, and
no points are given for a net electrical energy less than or equal to -50 kWh. The specific
criteria of the comfort zone, hot water, and appliances contests are explained in Chapter 2 -
Mechanical Systems under requirements for HVAC, solar thermal, and plumbing sections,
respectively.
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1.3.4 On-Site Disassembly:
The rules and regulations pertaining to the four disassembly days are very similar to
those imposed on the assembly days. One 12 hour day, followed by three 24 hour days will
be the total amount of time each team has to not only disassemble but re-pack and remove all
equipment and materials from the site. The goal for every team and the event organizers is to
try and leave the park in as good of condition as it was before the competition, in order to
show our appreciation to the park services and local community. Spill containment is a big
concern for disassembly as the water that was used by each home will need to be removed in
a similar method that it was delivered. This time, however, there is risk that the water is
contaminated, and therefore extra care must be taken to assure that no water or other fluids
spill and flow into local drainage. Again, for this reason, a detailed water removal plan must
be developed and drawn out by each team. The manner in which the homes are disassembled
is up to each team, however, since one goal of design is to demonstrate modular construction,
most teams will opt to disassemble in the same but opposite way that they assembled. Many
teams, regardless of placement in the decathlon results, will re-assemble their house for
display at the home university or another designated location.
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CHAPTER 2 – MECHANICAL SYSTEMS
2.1 FIRE PROTECTION SYSTEM
2.1.1 Fire Protection Requirements:
Fire protection is the only system not tested directly by contest officials but is a very
important requirement for safety reasons. Just as any residential home must follow fire code,
so must all solar decathlon homes. Full coverage of the interior of the home is needed
through multiple ceiling mounted sprinkler heads and extinguishers need to be placed in
areas of high fire threat, such as the kitchen. Enough water must be available at all times for
the sprinkler system to fully run for seven minutes in the event of a fire, either during
competition hours or when empty at night. No contest points are awarded directly for fire
suppression and protection but without these the homes could not compete in the decathlon
events.
2.1.2 Fire Protection Design Plans:
The fire protection system was designed according to the International Residential
Code (IRC) standards in order to meet all the requirements of a new residential home, with
both fire alarm and suppression systems. Because the house does not have a traditional
ceiling, the fire suppression system was designed to fit within the shell structure and the
sprinkler heads mounted flush with the inner FRP skin. Smoke detectors and fire
extinguishers were placed according to IRC and can be seen on sheet F-101.
In order to design the fire suppression system the sprinkler heads must be placed in
very specific areas to provide maximum coverage and to conform to IRC. The slope of the
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ceiling at the sprinkler head locations is greater than 1/3 but less than 2/3, and the heads are
sized accordingly. From the sprinkler specification sheet; the single sprinkler’s maximum
coverage needs to be 18” x18”, the minimum flow rate 19 gpm, and the minimum pressure
15 psi. According to IRC 2009 section P2904.4.2; two sprinklers run simultaneously for 7
minutes, and then the minimum water consumption is 266 gallons. Approximately 280
gallons of water are devoted to this fire suppression system and will be stored in a 300 gallon
tank in the under porch area. The sprinkler layout, piping, and tank are shown on sheet F-
102: Fire Suppression Plan, and sheet F-602: Fire Protection Diagrams (shown in Figure 1
below).
Figure 1: Sheet F‐602/A1 showing the Fire Suppression Diagram with keynoting.
The pressure needed for the fire suppression system is provided by a 3 hp centrifugal
pump. This pump was sized after performing a flow pressure simulation using a software
package developed by Thermal Engineering Corporation in Honolulu. The pump set up
along with valves and controls are drawn in Figure 1; the fire suppression diagram on F-602.
The fire sprinkler lines are PEX piping rated for fire suppression systems. These
pipes are flexible and can be routed through the curved shell structure of the house and will
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penetrate through the shell in the under floor area. A three-dimensional representation of the
system is shown in a fire suppression isometric view on sheet F-901, and can be seen in
Figure 2 below. Excess PEX piping is fitted into the shell structure to accommodate for
multiple connections and disconnections for off-site assembly and disassembly. The
sprinkler heads are recessed into ceiling to incorporate into interior design and are depicted
on sheet F-603 Fire Sprinkler Detail. The fire protection schedules, sheet F-601, list the
specific materials needed with different details depending on the material. Other comparable
UL listed products could also be used to accomplish the same needs.
Figure 2: F‐901/A1 shows an isometric view of the fire suppression system.
2.1.3 Fire Protection Design Specifications:
The fire protection system is made up of PEX and copper piping and fittings, fire
sprinklers, a fire water storage tank, a fire pump, fire alarms, and fire extinguishers. Detailed
fire equipment information can be found in the project manual specification sheets Division
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21: Fire Suppression. The fire equipment schedules, calling out all needed piping, fittings,
pumps, tanks, and sprinklers, can be found in the project plans on sheet F-601.
2.1.4 Fire Protection Construction and Disassembly:
Installation of the sprinkler heads will be done during the pre-construction stages of
the modules, and will be fitted flush to the ceiling FRP (fiber reinforced polymer) skin. The
flexible PEX piping will also be installed in each of the three individual modules containing
two sprinkler heads. These PEX lines will run from the bottom half of the shell into the
upper and are attached along one of the wooden ribs and placed below the joists that brace
the ribs together. Detailed plans of the PEX fire piping and sprinkler head placement inside
the shell are shown on sheet F-603: Fire Sprinkler Detail. Figure 3 below shows one of these
details from the drawing set; F-603/D1, which shows a cross-section detail of the sprinkler
heads and the PEX piping that runs along a rib and through joists.
Figure 3: F‐603/D1 showing fire sprinkler section detail of piping connected to rib.
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Although the FRP skin is mostly translucent the PEX lines are clear and where
attached to the ribs will not be easily seen or noticed through the ceiling shell. Extra PEX
piping will be wound up in the top and bottom shells to be connected once the shells are
joined on-site. Once the shells are connected the final quick connections, provided by the
PEX piping, can be made through the length of the belly of the house. The flexible PEX will
be used to connect to a hard copper line coming from the fire pump, which is then connected
to the plastic fire water tank, holding at all times enough water for seven minutes of fire
suppression. The system will then be primed and tested in accordance with Solar Decathlon
rules and regulations.
2.2 PLUMBING SYSTEM
2.2.1 Plumbing Requirements:
The plumbing requirements for the solar house can be determined by each team
according their needs based upon the contests that use water. All local building plumbing
code requirements must be followed in order to create a home that can deliver water for
bathing, dish washing, clothes washing, fire suppression (in case of emergency), and also for
any other water features implemented by the teams. The rules also state that a toilet shall be
installed in the bathroom but will not be connected to plumbing and therefore will not be for
use. All sanitary waste water (grey water) will come from the shower drain, bathroom and
kitchen sinks, dishwasher, and clothes washer. A detailed water budget must be made in
order for each team to determine the total amount of water that will be used during the
competition. This water budget is based upon the amount of water used for each of the
measured contests. All water brought into the home prior to competition from the decathlon
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provided water truck and then removed post competition must be accounted for in a detailed
water delivery and removal plan.
2.2.2 Plumbing Design Plans:
The plumbing system was designed following International Residential Code (IRC),
International Plumbing Code (IPC), and Uniform Plumbing Code (UPC). In order to
determine how much water would be consumed during the course of the competition, a water
budget was made. The budget details water usage from daily tasks such as showers, laundry,
dish washer, and cooking. It also must account for the water used for fire suppression (if
needed), and water needed for the thermal mass pillow tank. The maximum amount of
decathlon provided water for each team is 1500 gallons. Additional special water would be
brought in by the team for the aquaponics system to get it started. From the water budget the
water tanks were sized and configured in the under porch area, along with pumps, valves,
fittings and piping. The plumbing site plan, sheet P-101, shows the entire plumbing layout
for the house.
The domestic hot and cold water lines will be PEX piping because it can be rolled up
and stored in one module, then quickly and easily installed after module connection. All
horizontally installed PEX must be supported every 2.5 feet, in compliance with IRC
requirement from 2009 edition Table P2605.1 - Piping Support. The hot water supply PEX
piping is insulated to minimize heat loss and meet code requirements. Hot water is provided
from two lowboy solar thermal hot water storage tanks and connections are to copper piping.
Pressure for the domestic water supply is provided by a 1 hp centrifugal pump, and is
connected to a 500 gallon fresh water tank. The layout of the domestic supply plan can be
15
found on sheet P-102, and a more detailed riser diagram on sheet A1/P-602, which is also
shown in Figure 4 below.
Figure 4: A1/P‐602 Domestic water supply diagram with pipe sizes and annotations.
The sanitary waste and vent lines are assembled from PVC piping and are pre-
mounted into each module. All of the fixture sanitary drains are greater than or equal to 1-
1/4” to comply with IRC 2009 P2703.1, and drain into 2" branch lines leading to the main 2"
return line to the sanitary waste tank. The clothes washing machine drains into an 18 inch
high stand pipe to comply with IRC 2009 P2706.2 - Standpipes. The clothes washing
machine discharge goes through an air break to comply with IRC 2009 P2718.1 - Waste
Connection. The drainage fixture unit (DFU) value in the house is 7, and according to the
UPC, 2 inch gray water pipes can be used. Air admittance valves are used for low flow rate
fixtures (less than 18 gpm), and comply with IRC 2009 section P3114. These valves, along
16
with the rest of the sanitary system, are diagrammed on sheet C4/P-602 and shown in Figure
5 below. A site plan of the sanitary waste and vent system can also be found on sheet P-103.
Figure 5: C4/P‐602 Sanitary waste and vent diagram with pipe sizing and annotations.
During the competition, once grey water begins to fill the sanitary tank, it will then be
pumped out and fed into the aquaponics system to be reused and recycled; this is
demonstrated in the landscape irrigation plan on sheet L-102. The plumbing schedules, sheet
P-601, list with details all the needed materials to complete the plumbing system to code.
Any comparable UL listed products could be used instead of the ones specifically listed in
schedules. Three-dimensional isometric views of the domestic supply and sanitary return are
shown on sheets P-901 and P-902, respectively. Along with the water budget, a water
delivery and removal plan is necessary for the competition in order to allow for coordinators
to schedule water deliveries to each house. The team’s water delivery and removal plan is
described and pictured on sheet O-201.
17
2.2.3 Plumbing Design Specifications:
The plumbing design utilizes PEX and copper piping and fittings, PVC piping and
fittings, valves and vents, a supply water pump, and fresh and grey water storage tanks.
Detailed plumbing equipment information can be found in the project manual specifications
sheets Division 22: Plumbing. The plumbing equipment schedules, which outline all the
piping, fittings, valves, pumps, fixtures, and tanks used in the system, is also shown in the
project plans on sheet P-601.
2.2.4 Plumbing Construction and Disassembly:
The installation of the plumbing systems will be mostly pre-fabricated into the needed
modules. The bathroom and kitchen, with fixtures and appliances, will be completely pre-
installed in their individual modules and connections made under the floor in the belly of the
home. Wound up sections of flexible PEX piping in the belly are used for both hot and cold
water connections from the solar hot water storage tank and fresh water tank, respectively.
Cold and hot lines run to most of the appliances and fixtures; clothes washer, dishwasher and
kitchen sink interconnected, bathroom sink, shower, and refrigerator has only cold water
connection. Copper fittings and piping will also be used for connections between hot water
tanks and pumps. All the domestic water supply connections can be seen in a 3-D isometric
view in Figure 6 (on next page) from sheet A1/P-901.
The sanitary return pipes are made of standard PVC and connect to drains in the
shower, bathroom sink, kitchen sink, clothes washer, and dishwasher. The toilet, although
installed, will not be connected to supply water lines nor sanitary return pipes, and will
therefore not be available for use. Connections of the PVC sanitary return system will be
done on-site using long sections brought together in the belly of the home. A ventilation pipe
18
will be pre-installed in the module with the bathroom and will penetrate the roof structure as
shown on sheet A-561 of the drawing set. A connection will also be made from the grey
water tank to feed into the aquaponics system as the grey water fills the tank. Water tanks
will not be pre-installed due to their large size and when placed on-site are raised up on
footings to reduce the ground impact. The fresh water tank, grey (waste) water tank, fresh
water pump, and hot water tanks are all located underneath the porch area, where they can be
blocked from view. Access to this under-porch area is required to be enough to allow
workers to fit safely. Priming and testing of the water systems will be done after day five of
assembly, when the water is delivered. Detailed water delivery and removal plans are found
in the site operations section on sheet O-201 of the full drawing set.
Figure 6: A1/P‐901 Isometric view of domestic water supply piping and tanks.
19
2.3 HEATING, VENTILATION, and AIR CONDITIONING SYSTEM
2.3.1 Heating, Ventilation, and Air Conditioning (HVAC) Requirements:
The HVAC system requirements are based on the criteria of temperature and
humidity for the Comfort Zone contest. Temperature and humidity readings are taken from
various spots in the home and the thermal zone with most variation will be recorded and
time-averaged. The goal is to maintain an interior dry-bulb temperature between 71.0°F and
76.0°F, and an interior relative humidity below 60%. Each house’s thermal needs will of
course vary upon size, windows, building materials, and insulation. In order to determine the
thermal losses expected for the home design, a physical model is entered into a program.
Based on the sun path at the competition location and time, thermal exposure over a clear day
can be found and the average thermal gain of the home calculated. During the evening
thermal losses can be determined from exterior temperature and humidity estimations for the
area and by taking into account the insulation and windows used in the house.
During competition days the houses will be host to thousands of visitors, so during
this open public time temperature and humidity data is not taken. There are specific times
during each day when the comfort zone contest will occur. The times of the testing can be
utilized by the teams to optimize their cooling and heating potentials during those particular
hours. For this reason highly sophisticated HVAC systems can be used to accurately monitor
and control the temperature and humidity of different zones in the house. The HVAC system
and controls should be functional, efficient, innovative, reliable, and well documented.
2.3.2 HVAC Design Plans:
The HVAC system was designed in accordance to International Residential Code
(IRC), American Society of Heating, Refrigerating and Air-Conditioning Engineers
20
(ASHRAE), and American Society for Testing and Materials (ASTM) standards. In order to
determine the amount of heating and cooling needed to maintain the required temperature
and humidity range, according to the Solar Decathlon rules, a thermal analysis of the house
was conducted using Autodesk Ecotect and ACCA Manual J and D load calculations. The
programs were run considering the size and shape of the home and that the home would be in
Washington D.C. during the time of the competition in late September. Using the standard
weather of the location at this time it was possible to get a fairly accurate depiction of the
conditions that the house would experience and the heating and cooling loads necessary to
remain within the required ranges. From these loads the size of the heat-pump could be
found and then sizing for thermal mass, ducting, and diffusers calculated.
The HVAC system implements a water-source heat-pump drawing from a thermal
mass which acts as a geothermal source. The thermal mass contains water and phase change
material (PCM) which creates a lower and upper bound temperature range that optimizes the
performance of the heat pump. During cooling mode in the day time, heat is taken from the
interior and dumped into the thermal mass. During heating mode at night, warmer water
(requiring less heating) is now available in the thermal mass tank to be pumped through the
heat-pump. This balance helps to reduce home energy needs as well as heat loss from the
system. The thermal mass water and PCM is held in an insulated pillow/bladder tank. The
phase change materials are inside of tiny balls, which are contained in one meter long tubes
with a five centimeter diameter. Approximately 450 of these self-stacking tubes will be
placed into the pillow tank through a fill opening and is then filled with water.
HVAC air distribution uses rectangular ducting with a 1-inch layer of insulation to
prevent heat transfer between the air in ducts and the under-floor environment. Flexible hose
21
duct is used for fresh air intake and also for dehumidifier connection. The dehumidifier is
placed in parallel to the rest of the distribution system so that if heat pump is not running the
dehumidifier can still run and dehumidify the air going into the house. This method reduces
energy consumption for days when heating and cooling may not be needed. Bathroom
ventilation is provided by a fan under the lavatory, and takes air out of west bulkhead
through a flexible hose duct. Six floor diffusers distribute conditioned air into the home up
the north wall and six others, along the south wall, intake low stagnant air to be recycled
back through the heat-pump. A plan view of the home from sheet A1/M-101, seen below in
Figure 7, shows all the under-floor mechanical equipment and air distributions.
Figure 7: A1/M‐101 showing HVAC equipment and distribution plan.
2.3.3 HVAC Design Specifications:
The HVAC system is comprised of a heat pump, dehumidifier, metal ducting and
junctions, hose ducts, floor diffusers, thermal mass pillow tank, copper piping and fittings,
and a thermal mass water pump. Detailed HVAC equipment information can be found in the
project manual specification sheets Division 23: HVAC. The HVAC equipment schedules,
22
which outline all the ducting, piping, fittings, pumps, tanks, and other equipment used in the
system, is also shown in the project plans on sheet M-601.
2.3.4 HVAC Construction and Disassembly:
Pre-installation is done for the main supply and return ducts, branch ducts, and floor
diffusers into each module of the house. A bathroom air-ventilation fan is also pre-installed
in the bathroom module; however, a vent hose must be connected on-site and will exit out the
west bulkhead. All other mechanical equipment and materials are shipped separately and
installed on-site. Once the top and bottom modules are in place, cover is provided for
installers and the under-floor equipment, such as the heat-pump, pillow tank, and
dehumidifier can be installed. The connections between main supply ducts can also be made
once the modules have been joined together. Additional ducting is installed connecting the
heat-pump to supply and return air ducts, as well as to the dehumidifier and vent hose. The
vent hose will exit out the east bulkhead. Copper piping connections and fittings are then
made between the heat-pump, thermal fluid recirculating pump, and pillow tank. The PCM
tubes are placed into the pillow tank and will self-stack with some help from installers.
On water delivery day, the pillow tank can be filled with water which is pumped out
of the water tanks through a 1.5 inch rubber hose. The two water tanks are filled by the
water delivery truck prior to filling of the pillow tank. A 0.6 hp submersible pump is used to
pump the water from the water tanks into the pillow tank. This is all completed between the
two water deliveries; the first will deliver 1000 gallons and about 800 gallons of that will be
pumped into the pillow tank with the PCM tubes. The second water delivery will supply the
house with an additional 500 gallons of fresh water. During disassembly, on water removal
day, the submersible pump is used to drain the pillow tank back into the water tanks to
23
prepare for water removal and is also used to assist in draining the aquaponics tanks. The
rest of the equipment is removed as it was installed, and pre-installed equipment is kept in
the modules. Because spills are eminent during disassembly and assembly days, a spill
containment plan (sheet A1/M-102) is required for each team and can be seen below in
Figure 8.
Figure 8: A1/M‐102 showing spill containment plan for all systems of the house.
The spill containment plan shows all the systems which could contain any fluid at
some time during the competition; and therefore shows all plumbing and water tanks, HVAC
heat-pump and pillow tank, fire suppression lines and tank, solar thermal hot water tanks and
panels (not shown), and also the connections to aquaponics system tanks.
24
2.4 SOLAR THERAL SYSTEM
2.4.1 Solar Thermal Requirements:
Solar thermal needs are based upon the hot water and appliance contests criteria. The
bulk of the hot water needs will come from the hot water contest which attempts to replicate
the bathing needs of a single family home. Up to three hot water draws from the shower,
with shower head removed, can be made each day by judges and will be performed at
different times throughout the competition. Each draw must provide at least 15 gallons of
hot water within a ten minute time in order to qualify for points. Full points are given if the
average water temperature meets or exceeds 110°F and no points are received for an average
temperature lower than 100°F. Based on the number of water draws and estimating average
water usage per contest, the total hot water needs can be calculated for the competition. This
water will come from the fresh water supply delivered to each home just prior to competition
start, and must be accounted for in the water budget. From the hot water volume needs for
the most possible water draws on one day, the maximum daily hot water production value is
found and used to size a solar water heating system. The number of solar hot water panels
required and the angles they are mounted is determined based on the location and solar zone
and the daily hot water production needs.
2.4.2 Solar Thermal Design Plans:
The solar thermal water heating system was designed with IRC, ASHRAE, and
ASTM standards in mind. In order to determine the system size needed for the house the
water budget was used to calculate the maximum amount of hot water that could be drawn in
two consecutive competition days. Although the home would be built in Hawaii and is
designed for tropical climates, the HVAC and solar thermal systems need to be able to
25
perform for competition in Washington D.C. weather conditions for the end of September.
Because of this fact, the solar thermal system is over-sized for the Hawaii solar zone but is
correct for the Washington D.C. zone. When in Hawaii, one of the three panels can be
disconnected so that the system will not overheat.
Solar water heating for the house is provided by three superstructure mounted solar
thermal flat-plate collectors. Copper piping runs from the collectors, down the side of the
structure, and into the solar thermal storage tanks. The first tank is simply for storage while
the second, connected in series, is a solar thermal storage tank fitted with a backup heating
element. In the event that the collectors are unable to provide sufficient water heating, the
backup heater can make up the difference. A mixing valve is connected after the second tank
and takes hot water from solar storage and mixes it with cold water drawn from the fresh
water tank. The mixing valve is set to provide the house with water at 120 degrees
Fahrenheit in order to meet hot water requirements for dishwasher and for showers. The
storage tanks will reach temperatures upwards of 180 degrees Fahrenheit depending on sun
exposure and water usage. Blow-off valves are needed on each of the three panels and on hot
water tanks in the event that temperatures exceed safe limits. The flow of the water through
the solar thermal system can be seen in the solar water diagram on sheet M-603; also shown
in Figure 9 on next page.
26
Figure 9: A1/M‐603 showing solar water diagram.
2.4.3 Solar Thermal Design Specifications:
The solar thermal system consists of three solar thermal panels, two hot water tanks, a
solar thermal pump and controls, PEX and copper piping and fittings, three-way temperature
control mixing valve, and other valves. Detailed solar thermal equipment information can be
found in the project manual specifications sheets in Division 22: Plumbing and also Division
23: HVAC. The solar thermal equipment schedules are found in the teams full drawing set
on sheets M-601 and P-601.
2.4.4 Solar Thermal Construction and Disassembly:
Most of the construction of the solar thermal system must be done by professionals as
the copper piping has to be soldered well. The system must be able to handle temperatures
exceeding 180°F, and therefore many safety precautions are implemented to avoid
overheating. Blow-off valves are connected to each panel to alleviate pressure and steam to
27
cool the system. The solar thermal panels will be installed using a crane and will be
connected via junctions on the super-structure framing atop the home. Special care is taken
to ensure that the angles of the panels are not only correct but that they smoothly mesh with
the PV panels and super-structure louvers. A three-dimensional isometric view of the solar
water panels, copper piping, and hot water storage tanks can be found on sheet A1/M-902,
and also in Figure 10 below.
Figure 10: A1/M‐902 showing solar water isometrics of solar water panels and tanks.
Sections of copper piping, pre-soldered locally, will then be soldered and connected
between the panels and the hot water storage tanks. The storage tanks need to be placed on a
platform in order to distribute the weight evenly over the ground and reduce damage. The
mixing valve and temperature sensors are installed and connected to the controls. The pump
is installed after the first storage tank with check and ball valves, and flow monitoring
controls and sensors are connected. Once water is delivered to the water tanks, the solar
thermal system can be primed and tested. During disassembly all water must be drained
from the system prior to dismantling. The same care taken in installation will be taken in the
disassembly process.
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CHAPTER 3 – RESULTS AND DISCUSSIONS
3.1 SUMMARY OF TEAM HAWAI‘I’S SOLAR DECATHLON 2011
Combining aesthetics with functionality was the design goal of Team Hawai‘i’s Solar
Decathlon home and through the integrated efforts of architecture, mechanical and electrical
engineering students this goal was accomplished. With the strict code guidelines pertaining
to all sectors of the build, it was essential to meet these while maintaining the clean look of
the home. For the mechanical team it was very important to ensure proper design with
plumbing and HVAC ducting in order to increase efficiencies as well as to meet all code
requirements. The final design not only met code but also fit neatly in the under floor area of
the home, where components such as the heat-pump unit could still be accessed for repair.
The rest of the tanks and pumps are also efficiently and cleanly placed under the porch and
are hidden from sight. Even the copper piping running from the solar thermal panels run
under the superstructure and are not easily seen.
Keeping our mechanical equipment hidden, however, was not the main focus of the
team. Efficiency and innovative design were the driving forces that brought about many
unique systems like the internalized geothermal heat-pump application. Being the only team
implementing a very new and expensive building technology like phase change materials was
challenging but also very rewarding. Through this research it was found that there are very
high possible efficiency gains and energy savings with PCM in the thermal mass. Trying
new applications and pushing the envelope of what is normal in residential homes is the point
of the Solar Decathlon competition and Team Hawai‘i’s home design accomplished this task
on many different levels.
29
Unfortunately, the ultimate goal of building the Team Hawai‘i solar home was not
reached due to financial constraints. As the construction phase kept being pushed back
because of issues in structural design, the student based construction team from the
community college deemed that building the home under shortened deadline would not be
realistic given their experience level and limited fabrication equipment. The team leaders
decided to contract a few local companies to assist in finalizing designs and beginning the
complex fabrication of the home’s steel rib structure. However, final estimates began to
come in from the contractors and yielded numbers far above the team’s original construction
projections. Because much of the funding for building was coming from the University and
Colleges, the decision on whether to proceed with the project was ultimately up to a board
deans, the University Chancellor, and the Principle Investigator; David Rockwood of the
School of Architecture. David has been involved with the project from the beginning and he
very reluctantly agreed with the other professors and deans that the project would not be
completed on-time, nor on-budget, and therefore Team Hawai‘i would officially withdrawal
from the Solar Decathlon 2011 competition in the summer of 2011.
With hopes to compete in Solar Decathlon 2013, Team Hawai‘i’s members continued
final designs through completion and each group submitted and presented within their own
colleges and departments. Although Team Hawai‘i was unable to physically put the uniquely
efficient design to the test, the whole process was a huge learning experience for everyone
involved and it brought together colleges that wouldn’t normally work together on such a
large university wide project.
30
SECTION 2:
REVIEW AND ANALYSIS OF HUMIDIFICATION DEHUMIDIFICATION
DESALINATION PROCESSES WITH FOCUS ON DIRECT CONTACT
CONDENSATION
(Gerindtec Company’s solar powered desalination unit using MEH technology in India, September 2010)
31
CHAPTER 4 - INTRODUCTION TO WATER
DESALINATION
4.1 BACKGROUND ON FRESH WATER NEEDS
The need for fresh water is a growing concern for many people in countries all over
the world and especially those in isolated communities. The conservation and replenishing
of the world’s fresh water sources is of pivotal importance for the next generations.
However, in places where rain fall is scarce, simple conservation will not provide relief. The
use of desalination processes to create fresh water from saline water sources, such as
seawater or brackish water, is dramatically growing in certain countries, especially in gulf
areas. The primary large-scale desalination facilities in the world use the reverse osmosis
(RO) process or the multiple stage flash (MSF) distillation process. These processes are
ideal for coupling with power plants to utilize waste heat or quick electricity to aid in the
reduction of the desalination energy costs and demands.
The major need for fresh water exists in developing countries where large-scale plants
like this are few and far between. The use of small-scale decentralized solar powered
desalination systems is much more realistic for areas where water need is high, money is low,
and solar insolation is high. The humidification dehumidification (HDH) desalination
process coupled with PV energy generation and solar thermal water heating has been a focus
of study in recent years for these decentralized applications. The optimization of the many
different types of HDH desalination processes has been explored by many researchers from
all over the globe in order to validate their effectiveness. In order to optimize these current
HDH systems, various computer models have been used to analyze these systems and then
32
compare with experimental results to determine the parameters which have the greatest effect
on the performance and production rates. The effectiveness of these different models will be
explored and compared to determine which are the most suitable to obtain accurate fresh
water production rates. Based upon the several process methods the most common
optimization findings will be identified and discussed. The most viable systems and methods
will be found and verified from multiple sources. These top systems, modeling methods,
optimization parameters, and flow processes will be consolidated to present the most
productive and efficient HDH desalination process that can be further developed.
4.1.1 The Global Need:
The rain cycle is a naturally occurring process of fresh water production from saline
sources and through it rivers, lakes, and underground aquifers can be replenished.
Unfortunately there are many locations in the world where this natural fresh water generation
process does not occur on a regular basis and will sometimes not occur for years at a time.
This rain cycle, however, can be replicated through a method known as the humidification
dehumidification process of thermal desalination. This simple process was first mimicked by
the introduction of the solar still which can be dated back to the fourth century before Christ,
when sailors used it to desalinated seawater on long voyages. Since then a great deal of
advancement has been made in technology and therefore much more effective desalination
processes have been implemented for large-scale water desalting for use in industrial
applications as well as for providing nearby communities with a potable water source. In
recent history the true need for fresh water has become increasingly apparent, especially in
developing countries where population growth and drought have devastated the land and the
people. This growing need is the basis for this research and the goal is to show the potential
33
of solar powered HDH desalination processes in developing regions for use as a manageable
constant water source for the people around the area. The seemingly unquenchable global
need for fresh water is described in detail by the Progress on Drinking water and Sanitation
2012 Update; compiled by UNICEF and the World Health Organization (WHO) [1]. The
findings of this progress update are outlined in the following.
UN-Water Report for 2012 -
Every two years, UNICEF and the World Health Organization (WHO), compiles a
report describing the global status of water supply and sanitation development and also on
the progress made towards the related targets from the Millennium Development Goals
(MDG). Their primary MDG interest is Target 7c - reducing by half the proportion of people
without sustainable access to safe drinking water and basic sanitation between 1990 and 2015
[1]. This WHO/UNICEF program, known as the Joint Monitoring Program (JMP) for Water
Supply and Sanitation, collects data sets based upon information gathered from household
surveys and censuses to report on the advancement of water supply and sanitation for every
country in the world. Although accurate monitoring may not be available in all countries, the
JMP has continually produced reliable data to keep the world informed on these most
important figures. The estimates provided in the new 2012 report present the status as of the
end of 2010. This 2012 report bears very exciting news that the MDG drinking water target
was successful as of 2010, which is five years ahead of the target goal of 2015 [1]. These
improvements for developing regions can be seen in Figure 11, which also shows all
developing regions compared with the whole world. The MDG sanitation target,
unfortunately, will most likely remain unreached as of 2015 [1].
34
There are huge disparities in the numbers between rural and urban areas and the
overall percentages, which show “success” for water supply improvement goals, do not
accurately portray the truth in the many developing countries. These disparities are of great
concern and much of the 2012 JMP report focuses on this issue. Countries in sub-Saharan
Africa and Oceania are the most affected by these rural-urban disparities and are a primary
focus for efforts to drastically increase coverage as well as promote global monitoring of
drinking water quality and sanitation progress [1]. These disparities between rural and urban
areas can be seen in Table 1, on the next page. The disparities aside, there has been much
improvement world-wide with over 2 billion people receiving access to some form of
improved water source and 1.8 billion gaining access to improved sanitation facilities
between 1990 and 2010 [1]. Many of the countries that showed the most improvement were
also facing large population growth, making these gains even more impressive, although the
rapid growth can also reduce the value of some of these numbers.
Tragically, there are still over 780 million people without access to improved
drinking water sources and a staggering 2.5 billion lack improved sanitation [1]. If these
trends continue, estimates for 2015 show 605 million still lacking improved drinking water
sources and 2.4 billion without improved sanitation [1]. Since improvement in water supply
and sanitation go hand in hand, for the most part, the efforts of both are in connection but yet
the numbers seem to show great leaps for water supply and much less so for sanitation. This
may be due to discrepancies in data sets and census information; which shows the importance
of improved monitoring systems in order to know where the most need for each region exists.
For these reasons UNICEF and WHO are attempting to develop new water, sanitation and
hygiene goals, targets and indicators for beyond 2015 [1]. These new indicators and methods
35
of monitoring could potentially report not only on the availability of fresh water sources and
sanitation facilities but on the safety, quality, reliability, and sustainability of these sources
and facilities [1].
Figure 11: Drinking water coverage trends by developing regions, 1990‐2010 [1]. Table 1: Disparities between rural and urban areas in water sources, 1990‐2010 [1].
36
4.2 BACKGROUND ON WATER DESALINATION
Desalination methods can be categorized into two process types; thermal and
membrane processes. Thermal, or phase-change, processes use heat to bring a saline water
source to the point of evaporation, after which the pure water vapor is condensed and
collected to produce fresh water. Membrane processes use a semi-permeable membrane to
separate concentrates from fresh water by either applying an external pressure with use of
pumps or by using an electric current to move salt ions through an ion exchange membrane.
Both thermal and membrane process types need some source of energy to produce fresh
water and that energy generally will come from the burning of fossil-fuels; whether it be
through direct heating or through the use of electricity. In order to alleviate these energy
needs waste heat can be utilized from power plants or other sources; also renewable sources,
such as solar or geothermal, can easily be harnessed for this purpose. When renewable
sources or waste heat are used for desalination the result is much cheaper production costs,
making desalination much more viable for use in potable water production.
The history of desalination methods and processes as well as the most current
technologies are described in some detail in the following sections. The thermal processes
are outlined first; beginning with the simple solar still, moving on to the largest producing
thermal process today of multi-stage flash distillation (MSF), then multiple effect distillation
(MED), and finally the thermal and mechanical vapor compression (T/MVC). The many
different systems and configurations of the humidification dehumidification thermal process
will be described in the next chapter. After the thermal processes, the membrane processes
are described; beginning with the world’s largest producer of reverse osmosis (RO), then the
37
electrical current based process of electrodialysis reversal (EDR), a brief about nanofiltration
(NF), and finally some other ion membrane processes and their applications.
The global breakdown of the current percentages for desalinated water production is;
RO with a majority of 53%, MSF following at 25%, MED generating 8%, ED with 3%, and
the all others representing the remaining 11% [2]. These desalination methods are used all
over the world and yet nearly 75% of the total desalinated water production occurs in only 10
top countries [2]. The four largest producers; the Kingdom of Saudi Arabia (KSA), the
United Arab Emirates (UAE), the United States of America (USA), and Spain, together
represent over 50% of the global production [2]. The majority of this production comes from
the use of RO and MSF process plants. The total capacity output per day of the top 10
countries and their corresponding share of the global production are shown below in Table 2.
Table 2: Top 10 desalinated water producing countries [2].
4.2.1 Thermal (Phase-Change) Processes:
Solar Still-
The use of solar energy to naturally produce fresh water from a saline source by
means of the humidification dehumidification process can be dated back to Greek sailors in
the fourth century BC, using seawater to get drinking water on voyages. However, the first
38
published work on solar desalination was in 1551 by Arab alchemists [3]. The first solar still
was designed and built by Carlos Wilson, a Swedish engineer in Chile in 1872. During
WWII a plastic inflatable still was developed by Telkes for use by the US Navy and Air
Force in emergency life rafts [4]. The basic solar still is a very simple design in which a
single basin still is used to hold salt water and is covered by some clear covering, usually
plastic or glass, which allows sunlight to pass through. The solar rays heat the salt water to
evaporation, this water vapor can then condense on the cool glass or plastic covering. The
condensed fresh water then travels by gravity to a collection area. This process is very
simple but usually has an efficiency of below 45% due to the inherent heat losses from the
glass or plastic. This energy loss is from the latent heat of condensation transferred from the
condensing water through the glass or plastic and lost to the ambient air.
Many variations of the solar still have been made over time to reduce these losses;
one of the most effective utilizes multiple effects to take advantage of the latent heat of
condensation and reuse this energy to preheat the water through different stages [5,6].
Because of this heat recovery the set up yielded a substantial 80% increase in the gain output
ratio (GOR: the ratio of the energy consumed to the energy input) compared with a regular
single stage still [5,6]. Although this setup produced a high GOR as well as higher fresh
water production quantities these values were only achieved with a constant hot water supply
at 90°C. If the system were to actually operate at this high temperature for a long period then
the scale formation would cause issues and maintenance would be difficult. Also, the low
heat and mass transfer coefficients in this unit would require operation at these fairly high
temperatures to be productive and evaporation and condensation surfaces would need to be
made of expensive metals. For these reasons the solar still, even with multiple stages
39
providing regenerative heating, is extremely limited in production and efficiency and because
of this many other processes have been researched and developed.
Multi-Stage Flash Distillation (MSF) -
The multi-stage flash distillation process currently is used in nearly 90% of all
commercial thermal desalination plants and, as noted above, represents nearly 30% of the
world desalinated water production. MSF plants in general produce around 100,000 m3/day
of desalinated water but on the extreme side can have rates nearing 1,000,000 m3/day [7].
The reason for this is because the MSF process is highly efficient on a large capacity and
especially when in connection with a power plant for use of waste heat. The MSF process
works by allowing a saline water source to enter an evacuated chamber which suddenly drops
the pressure (flashes) to produce water vapor. This flashing process is repeated through
multiple champers with successively decreasing pressures and increasing temperatures.
Once through all the flashing stages the water vapor is condensed by using the cool source
water, thus preheating and conserving heat. The MSF process requires an external steam
supply around 100°C, which would ideally come from waste heat from a power plant. The
limiting factors for this system are determined by scaling formation at the peak temperatures.
Multiple Effect Distillation (MED) -
The process of multiple effect distillation is similar to MSF in that it utilizes multiple
chambers to increase the water vapor concentration and provide regenerative heating.
However, MED relies mainly on heating to achieve evaporation, as opposed to flashing or
drastically dropping pressure in MSF. The MED process is made up of cascading chambers
in series within which the pressure is reduced for each stage and the steam produced in each
previous stage used to heat the saline solution in the next stage. The more stages the more
40
effective these systems can be but costs limit the number of stages that is realistic. MED is
second to MSF as a commercially used process for fresh water production. The MED
process is generally operated at fairly low temperatures, usually below 70°C, which helps to
reduce the build of scale formation. The largest MED plant in the world began operation in
April 2009 and is located in Jubail, Saudi Arabia. This large-scale plant is capable of
producing above 800,000 m3/day of desalinated water [8].
Thermal or Mechanical Vapor Compression (T/MVC) -
The distillation process of vapor compression employs compressed super-heated
water vapor to heat the saline water source to the point of evaporation. The compression of
the vapor for heating can be produced by either a thermal or mechanical method. This
compressed vapor has much higher temperatures and pressures and is able to heat the original
saline feed water source very quickly. The thermal compression method takes steam from an
external source which comes from an ejector system, and makes it possible to recycle vapor
produced from the distillation process. The mechanical compression method can be
accomplished through a compression turbine and can be done at normal atmospheric
pressures or within a vacuum. When using the vacuum approach the distillation process is
more efficient but costs to generate the vacuum can be high. In both MVC and TVC the
condensation of the water vapor is done by heat exchanging condenser and because of the
high temperatures allows this regenerative heating to create more vapor. The vapor
compression method is very effective in heat regeneration but because of the high energy
demands needed to produce compressed vapor, the costs associated can be also be high.
Since VC is not as capable at producing effectively on a large-scale it is generally
used for smaller scale production. Australia used to depend on VC for nearly 18% of its
41
water production from desalination in 2002; however, since then RO process plants have
taken over and drastically reduced the number of VC process plants [8].
4.2.2 Membrane Processes:
Reverse Osmosis (RO) -
Reverse osmosis large-scale industrial plants account for nearly 80% of all membrane
process fresh water production in the world and 59% of the world production. The largest
RO plant in operation to date is the Ashkelon plant in Israel, which is capable of producing
330,000 m3/day of desalinated water [9]. The use of this process for large-scale water
production is only in competition with the MSF process. The RO process is a membrane
filtration method which can remove large ions and molecules from a solvent solution by
applying an external pressure to reverse the natural flow of the solvent. This natural flow of
the solvent from an area of low solute concentration to an area of high concentration is the
normal osmosis process. This flow across a membrane to equalize the solute concentrations
is what causes osmotic pressure. Thus, by inducing an external pressure and forcing the
reverse flow of the solvent across the membrane, the solute can remain on the pressurized
side while the pure solvent is allowed to pass through to the other side. This reversal of the
natural osmotic process flow is therefore called reverse osmosis. Standard membrane
filtration uses a straining mechanism by particle sizes and is mostly dependent on the
membrane construction, while RO uses a diffusive mechanism and is mostly dependent on
pressure and solute concentration. The pressure at which the reverse osmosis can be
productive is directly proportional to the solute concentration, and therefore this pressure and
concentration must be optimized to maximize production rates. For these reasons, RO is
42
ideal for use in drinking water purification from saline sources, such as seawater, to remove
salt ions and other concentrates from the pure water molecules.
Electrodialysis Reversal (EDR) -
Electrodialysis reversal, or EDR, is a desalination process which has been
commercially used since 1960 and, like RO, is a membrane process driven by electricity to
separate ions from the pure water molecules. Unlike RO, the EDR process implements an
electric current which is sent through the solvent solution to cause the movement of the
dissolved salt ions through the membrane. The membrane used for EDR is also different
from RO and is made of stacked layers alternating between cationic and anionic ion
exchange membranes. The direction of the ion flow through these membranes is changed by
reversing the polarity of the applied electric current. Although EDR can be used to
desalinate water for drinking purposes, the production values are generally low and better for
small-scale as opposed to large-scale RO plants.
Nanofiltration (NF) -
The method of nanofiltration is a membrane process which operates in much the same
way as reverse osmosis. The membrane developed for nanofiltration has pore sizes smaller
than those in RO and also use pressure to create flow across the membrane. The pressure
needed to create this flow is much less than that for RO and as a result the process can use
considerably less energy. The NF process is subject to fouling and scaling just as in other
desalination processes but can be more costly to the system efficiency since the filter pore
sizes are much smaller. For this reason, nanofiltration is generally used to process water with
lower total dissolved solid levels, such as surface water or groundwater. NF is being more
commercially employed in food processing for demineralization and disinfection. Although
43
NF has potential in desalination, currently the process has not shown promise as a large-scale
producer nor as efficient for small-scale applications. NF does show much potential as a
further filtration process, in conjunction with another desalination method (such as RO), to
soften and remove organic matter.
Other Desalination Processes -
Some other processes, such as the ion-exchange and the gas hydrate process, are
extremely effective at removing salt ions as well as any others from a solution. These
processes tend to be much more expensive on a large-scale and are designed more for the
removal of almost all dissolved solids. With purity levels around less than ten parts per
million (< 10 ppm), these processes far exceed the requirements for desalination for potable
water and would also remove many of the necessary nutrients found in water. Therefore,
these processes tend to be needed for applications where high purity is required such as in
hydrometallurgical, metals finishing, chemical and petrochemical, pharmaceutical, industrial
water, semiconductors, power engineering, and the nuclear industry.
44
CHAPTER 5 – THE HUMIDIFICATION
DEHUMIDIFICATION THERMAL DESALINATION
PROCESS
5.1 HUMIDIFICATION DEHUMIDIFICATION (HDH) PROCESS
The humidification dehumidification thermal process is one of the more simple
desalination methods and is based on the rain cycle. The HDH process works in much the
same way that rain is created from seawater in the natural water cycle; seawater (or saline
source) is heated by solar rays to the point of evaporation and then the water vapor is cooled
and condenses as pure water. A HDH plant simply concentrates and expedites this natural
water cycle through the use of solar thermal water heating panels, pumps, and the separation
of humidification and dehumidification into separate thermally insulated chambers. In
general, a HDH system is comprised of a humidification (evaporation) chamber, a
dehumidification (condensation) chamber, solar thermal panels, piping and pumps, and air
heaters and fans (if applicable). Many different variations of the HDH process have been
developed to maximize efficiency and production rates as well as reduce costs. The multiple
stage humidification process is a common adaptation of the general HDH system in which
multiple stages of humidification are used to maximize the water vapor content before
moving to dehumidification chamber. This allows for increases in fresh water production in
the condensation tower but the more stages used in a system the higher the costs will be. A
simple diagram of an HDH system can be seen on the next page in Figure 12.
45
Figure 12: Simple HDH diagram with solar collector.
5.1.1 HDH Classifications:
The HDH process can be classified into a multitude of configurations based upon
cycle, heating type, and energy usage method. There are two cycle configurations; the
Closed-Water Open-Air cycle (CWOA) and the Closed-Air Open-Water cycle (CAOW). As
the name would indicated, the CWOA cycle (in general), has a closed loop for the water flow
from the cool saline source through the condensation piping, where it is pre-heated collecting
the latent heat of condensation. This regenerative heating is followed by solar heating
through the panels. The heated saline water is then pumped into the humidification chamber,
where it meets air flowing in counter-current. The excess saline water not evaporated then
flows down to be added back to the saline feed and then around the loop again. The open air
flow through this cycle begins as relatively cool dry air is blown upward through the
46
humidification chamber where it meets the warm saline source and ideally reaches a relative
humidity of 100%. Once the saturated air leaves the evaporator it will enter the
dehumidification chamber where it will come into contact with the cool condensation piping
and form fresh water droplets. These droplets flow down and are collected into a fresh water
tank.
The CAOW cycle (in general) works in an opposite way; a closed air loop is first
heated by thermal collectors and flows up through the evaporator mixing with the saline feed
water and becoming humidified, then down through the condenser where it is dehumidified.
Since not all of the water vapor can condense the air retains some moisture and is sent back
through the heater and over the cycles will continue to rise in relative humidity eventually
ensuring that fully saturated air will always enter the condenser. The open water flow in this
cycle enters at the condenser where it is pre-heated through latent heat and flows down
through the evaporation chamber and is allowed to leave the cycle as the concentration of
saline in this water is now greater. For the most part, many of the systems seen in practice
try to find some way to capture the latent heat from the water that does not evaporate in the
humidification chamber and also to not waste water. Each cycle incorporates brine outflows
from the humidification chamber. Diagrams of the general CAOW and CWOA cycles can
be seen on the next page in Figures 13 and 14, respectively.
47
48
Figure 13: CAOW cycle diagram. Figure 14: CWOA cycle diagram.
There are two types of heating that can be used in these cycles; air and water heating.
Both heating methods can be powered by solar energy and integrate panels of some sort. For
CAOW cycle configurations, the heating form of choice is generally air heating; however
both heating types are commonly employed to increase performance. When water heating is
used in this cycle the excess heat from the water not evaporated in the humidifier can be
transferred to new entering saline water through heat exchangers. Heating the water only in a
closed air loop would not be productive and is not seen in the literature. For the CWOA
cycle configurations, water heating is obviously always used and air heating is not because of
the inherent losses associated with heating air in an open loop because excess heat cannot be
easily exchanged as with water. In general water heating is much more efficient than air; at
times having a heat transfer coefficient 100 times greater.
The final classification is the type of energy consumed to power equipment and to
heat the water and/or air. The type of energy used depends mainly on the location of the
system. The goal is always to utilize as many renewable sources as possible without having
to rely on fossil-fuels. In most areas solar energy is available both to power pumps, through
PV panels, and to heat water and/or air, through solar thermal panels. Geothermal energy
can be implemented when in a location where this renewable source can be found and readily
exploited without environmental impact or extreme costs. Standard forms of energy such as
electricity from the grid or from generators burning fossil-fuels are also always available, but
would do not provide reduction in energy usage nor conservation.
5.1.2 Performance Parameters:
In order to analyze the performance of these HDH systems various parameters have
been designated to accurately compare the many different configurations that have been
developed. The ones described and used in this paper are the gained output ratio (GOR), the
specific water production, the recovery ratio (RR), and the humidifier efficiency. There are
of course other efficiencies having to do directly with specific components; such as solar
thermal water panels, solar air panels, pumps, and ext. These maybe mentioned but will not
be the focus as they are unique to different systems, experimental set-ups, locations, and
other factors. The four primary performance parameters are described below.
Gained Output Ratio (GOR) -
The GOR is defined by the ratio of the latent heat of evaporation of the distillate to
the total heat input which, in the case of HDH, is absorbed by the solar collectors that are
used. The GOR is used by other desalination processes as well, such as RO and MSF, to
describe their efficiencies of water production to the amount of energy used. These large-
scale processes tend to have a GOR of around 8. It is important, however, to remember that
in general large RO or MSF plants require much larger amounts of energy, which generally
does not and cannot come from renewable sources.
49
Specific Water Production -
This parameter measures the amount of desalinated water produced per the total solar
collector area per day. This value gives an idea of the effectiveness of the system to take
advantage of the solar energy that is captured for the production of fresh water. Since much
of the costs associated with HDH systems comes from the solar collectors, the specific water
production is a not only a good indicator of energy efficiency but cost effectiveness as well.
Solar thermal air panels can account for up to 45% of the total costs for systems with air
heating [10]. Solar thermal water panels cost less but still account for around 30% of the
total costs for systems with water heating [11].
Recovery Ratio (RR) -
The recovery ratio for a system is the ratio of the amount of fresh water produced per
the saline or brackish feed water. This ratio is generally fairly low for HDH processes when
compared with large-scale production processes like RO or MSF. Although because of this
low value there is much less brine output and thus less concern for scaling occurring inside
the system. RO and MSF plants require complex brine pre-treatment processing and disposal
methods, while these are not needed for HDH systems. When the saline source water is re-
circulated the RR can be higher but this will also increase the saline concentration of the feed
and therefore increase brine blow down and then may require some pre-processing.
Humidifier Efficiency -
The efficiency of the humidifier can be evaluated using the following equation:
η = (ωout - ωin )/(ωout,sat - ωin ) ,
where ωout is the outlet absolute humidity, ωin is the inlet absolute humidity, and ωout,sat is the
outlet absolute humidity at saturation. When the efficiency of the humidifier reaches unity
50
this means that the outlet absolute humidity is at the saturation point. This is the primary
goal of the humidification chamber because when there is saturated air entering the
condensation tower it always for maximum fresh water production. In general, this
parameter is used in systems where the humidification chamber uses packing material which
is wetted by spray from the top of the chamber.
5.2 LITERATURE REVIEW OF HDH SYSTEMS and COMPONENTS
The following is a brief overview of the findings from various different
configurations of HDH systems which have been developed, built, modeled, tested, and/or
studied by others in recent desalination literature. The systems are grouped into CAOW
systems and CWOA systems, and then divided by heating type. The different designs used
for the humidification and dehumidification chambers are also described and compared in
some detail. The common heat exchanger types and methods used to provide heating and
also help reduce heat losses are explained and contrasted as well.
5.2.1 Closed-Air Open-Water (CAOW) Systems:
For systems which used essentially CAOW cycles both types of heating, water and
air, can be made effective and in some cases both were made functional. The setups that
used water heating only all were able to obtain maximum GOR and specific water production
performance values which corresponded directly to an optimal water mass flux. In some
cases this was done experimentally and others through modeling, but many were able
compare both results and find consistent relations between them. The flow rate of the saline
source through solar collectors also has a large effect on the heat transfer performance
experienced. The movement of the air through these systems was also varied; in general the
51
flow rate of the air did not have a dramatic effect on any of the performance parameters. A
GOR value of between 1 and 5 was found for most systems [12]. The high end values were
generally obtained by means of the recovery of the latent heat of condensation through pre-
heating. In one case, a new process called multiple effect humidification (MEH) was
presented which was able to achieve the largest GOR value of 5 [11]. The MEH
configuration implements a continuous temperature stratification method where vapor from
the evaporator is directly extracted at certain elevations along the chamber and injected into
the condenser at the same level [11]. This process allows for a small temperature difference
between the humidifier and dehumidifier which allows for higher heat recovery. The high
recovery of the latent heat means a lower energy demand and therefore a greater GOR value.
The MEH method also experienced higher values for specific water production and also
recovery ratio. Another method applied to this MEH process that produced larger GOR
values was the integration of thermal storage tanks. Thermal storage tanks can be used
primarily to reduce the start-up energy and time demand. By storing excess heat in tanks it
can be used at a later time when heating needs increase; for example when the suns intensity
drops due to cloud cover or time of day. Also with enough thermal storage 24-hour
operation can become feasible and more cost effective [11].
For those using a CAOW cycle with air heating only the temperature of the air was a
large factor in the absolute humidity which could be achieved through the evaporator. When
air temperatures where insufficient the low absolute humidity outlet drastically reduced the
water production from the condenser. This led to a low values for the humidifier efficiency.
Multiple stage systems were developed by some to raise the humidity values. This was
accomplished by having multiple stages of air heating and also humidifying in separate
52
chambers. The multiple humidification and heating steps produced increases in the absolute
humidity before entering the condenser, increasing total humidifier efficiencies, and boosted
fresh water production. Since the increase in production came only with additional air
heating panels, the specific water production values did not change much. Also, because of
the increased costs from multiple humidification chambers and additional solar thermal air
panels did not validate the production increases. The GOR values for most of these systems
were also low due to the much lower heat transfer coefficient associated with air heating.
Heat losses from the warm air to the incoming cool saline water source in the evaporator
were also experienced for most because this heat cannot be as easily recovered through heat
exchangers, as with water heating cycles.
For those systems where water and air heating were combined the advantages seen
were not extraordinary and costs generally outweighed the benefits. The overall findings for
systems using the CAOW cycle were that water heating is best with a maximum production
water flow rate being obtained for most. The use of the MEH process can greatly increase
the recovery of latent heat, decreasing energy demands for water heating and increasing the
GOR value. Rises in both specific water production and recovery ratio could also be seen in
the MEH systems. Overall, in order to produce higher values for all performance parameters
the primary goal is to increase the amount of heat recovery and regeneration from the water
source. This can be done through many means, but the best methods are the simplest which
also can decrease the cost per fresh water production.
5.2.2 Closed-Water Open-Air (CWOA) Systems:
For those systems seen that used the CWOA cycle all utilized water heating and none
air heating due to the inherent losses associated with heating air in an open cycle. Most of
53
the systems found that the higher the temperature of the water entering the humidifier the
greater the fresh water production. This did not always mean an increase in the specific
water production as this value is dependent on the amount of solar panels needed to provide
this heat to the water. One issue that all noticed with this CWOA cycle was that if the
recycled saline water, not evaporated in the humidifier, is not cooled enough before its
reentry into the condenser then it would be too warm to allow for maximum condensation of
fresh water from the warm humid air. To reduce the temperature of the re-feed saline water,
heat exchangers were introduced by some and found increased performance of the condenser
but by removing this heat, additional heating is required before entry to the humidifier. This
would defeat the purpose and advantage of using a closed water loop.
Unlike the CAOW cycle, both optimal air and water flow rates were found by most to
yield the best performance of the specific systems at a set water temperature. This means
that much more adjustment is necessary for this cycle in order to optimize and since water
temperatures in a real world application would vary throughout the day; it would require the
use of monitoring devices and automatic adjustment controls. The controls and monitoring
needed would dramatically increase the total system costs and would not validate the
increase in performance values. Some were able to achieve these optimal conditions and
maintain them, but this was only accomplished under ideal laboratory conditions. Through
the use of highly efficient humidifiers and optimization controls and monitoring, these
idealize laboratory systems were able to achieve higher water production values than CAOW
systems. This process, however, is very hard to maintain and not only requires the use of
advanced equipment but also constant monitoring by skilled operators. Although it is
exciting to see high production rates like these, it is unrealistic to develop a system like this
54
for a remote region where qualified operators could not be available on-site. Also, high costs
and real world conditions would drastically reduce the potential of systems such as these.
5.2.3 Humidifier/Evaporator:
Humidification chamber design is imperative to the performance of the overall
system as it is the first step of the process and without the achievement of high humidifier
efficiency then water production as well as reduction of energy usage cannot be obtained.
The primary needs for successful humidification are heat and surface area. The inlet water
and/or air temperature into the humidifier has a drastic effect of the performance; without
high enough temperatures evaporation cannot occur. The contact surface area between the
entering dry air and water must also be maximized in order to increase the effectiveness of
the evaporation process. Although there are various ways to achieve evaporation, the most
commonly used and accepted method is the integration of spray towers with a packed bed
concept. Spray nozzles at the top of the humidification tower provide direct water to air
contact and a nice distribution of the feed water throughout the chamber. In combination
with a packed tower, the spray nozzles cover the packing material with water droplets,
providing maximum contact area between the water and air.
The greatest difference between humidifiers is the type of packing material that can
be implemented to increase this contact area. Many different mediums can provide the
needed distribution of water droplets, ranging from the simple and natural to the very
complex and manufactured. Some of the packing materials seen in the literature were;
fleeces, cottons, wood materials, plants, plastics, honeycomb paper, corrugated cellulose
material, and canvas. When looking purely at surface area, the best packing comes from
manufactured grid patterns that are generally made from a plastic to reduce heat transfer
55
increase longevity. Other more natural materials would not last long, might degrade
releasing particulate into the water, and could also absorb heat. Those materials that would
absorb the water may be good for saturation but over time would degrade and require
replacement, costing time and money.
As opposed to spray nozzles, a trickle effect has been used by some to saturate a
vertical medium, or packing. A bubble method was also seen, working in the opposite way
of a spray tower, where the chamber is filled with feed water and then the air was injected at
the bottom creating small bubbles. As the bubble rise through the saline water the air inside
becomes saturated and upon reaching the surface of the water, releases and merges into
humidified air, which can then proceed to the condenser. This method depends highly on
bubble formation, size, and interaction and is highly unpredictable.
The spray nozzle tower with packing material being the optimal design choice, the
next goal is to maximize the absolute humidity of the air leaving the humidification chamber.
This humidity increase can come from varying the height of the tower, the type of spray
nozzles, the flow rate of the spray, distribution of the spray, and the density of packing
material. These features can be varied through various means and are specific to the systems
in which they reside. The MEH method takes optimization to another level, taking
evaporated vapor from the humidifier at varying heights and injecting into the condenser at
corresponding heights to ensure consistent temperature stratification between the two towers.
As mentioned earlier, this method is highly effective as it increases heat recovery which
increases the GOR and specific water production values. However, the complexity of this
design increases overall costs and maintenance needs.
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5.2.4 Dehumidifier/Condenser:
The design of the dehumidification chamber is something that varies drastically from
each system as there are many different methods to accomplish the task of condensing the
humidified air coming from the evaporator. One of the primary goals of condensation is to
create the greatest temperature differential between the warm humid air and the cooling
medium upon which the fresh water molecules can condense. For HDH systems the cooling
is generally provided by incoming feed water in order to preheat the feed water source before
further heating and entrance to the humidifier. Therefore, the cooler the original feed water
source, the better the condensation rate. The temperature of the humid air depends on the
water and/or air temperature entering the humidifier. As with the humidification tower, the
contact area between the humid air and the cooling medium is the other huge factor in the
performance of the condenser, along with the temperature differential. The most common
method used is indirect contact condensation upon heat exchangers in the form of conductive
piping through which the cool feed water can flow and preheat. Heat exchanger designs can
be enhanced using piping with connected fin arrays to maximize the contact surface area. In
these heat exchanger condenser types the kind of metal used is of great importance as heat
transfer characteristics vary greatly. Also, especially with simple piping coil designs, the
flow rate of the feed water needs to be adjusted in order to maximize heat transfer properties
and also ensure that the cooling fluid doesn’t gain too much heat inside the condenser,
reducing the needed temperature differential. These indirect contact heat exchanger type
dehumidification towers are ideal for the recovery of the latent heat of condensation, which is
captured by the cooling feed water and preheated.
57
In recent years the method of direct contact, as opposed to indirect contact methods,
has been integrated in condensation towers. The goals of this method are still the same;
increase the temperature differential and increase the contact area. However, the means by
which the condensation occurs is much different. Direct contact dehumidification towers
work and look very similar to the spray nozzle packed bed humidification tower, except for
instead of spraying heated saline water they spray cool fresh water. The cool fresh water
usually comes from the fresh water production tank after it has been cooled through an
indirect heat exchanger by the entering cool feed water; thus also accomplishing preheating
and recovering some of the latent heat of condensation. The cool fresh water is sprayed into
the condensation tower from the top and is distributed throughout the tower on the packing
material. The same plastic grid packing material as in the humidifier can be used for this as
well. Once the warm humid air from the humidifier comes into contact with the cool water
droplets and packing material the water vapor condenses. The use of this packing material
greatly increases the surface area to volume ratio and hence increases the heat and mass
transfer between the air and water in both the condensation and evaporation towers.
Although the packing material increases these values, much of latent heat of condensation is
lost to the air. The recovery of this latent heat of condensation in the condenser is more
effective through the use indirect contact condensation methods; where the humid air is
separate from the cooling fluid and heat transfer can occur across the conductive metal heat
exchanger. The use of an additional heat exchanger can recover some of this lost latent heat
and is described further in the following section.
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5.2.5 Heat Exchangers:
Heat exchangers are a pivotal part of the HDH process as they are nearly involved in
every aspect of the process. There are two types of heat exchangers; those that incorporate
direct contact between the two mediums and those that use indirect contact. The two primary
locations in the HDH process where heat exchangers are needed are in the solar panels
heating the water and/or air prior to entry to the humidifier, and in the dehumidification
chamber. Air heating is accomplished through the use of solar thermal air panels which use
the direct contact method. The heating of the saline feed water can either be achieved
through direct contact with specialized solar thermal panels made to withstand salt content,
or through an indirect contact approach. This indirect approach begins with the direct
contact heating of fresh water in regular solar thermal panels which is then sent through an
indirect contact heat exchanger with the saline feed water flowing through the other side.
The advantages to using direct heating with specialized panels is that there are less
heat losses through piping and an additional exchanger, and also less equipment and costs.
However, since salt water thermal panels need to be made of non-corrosive metals they are
much more costly and also as the salt concentration increases, the thermal conductivity of the
saline source decreases. Also, overtime even the specialized panels and piping can
experience scale build up and require cleaning as to not decrease heating efficiencies. When
the indirect method is used there are fewer issues with scaling, specialized panel costs, and
also the direct heat transfer to the fresh water is much more effective than to the salt water.
The additional heat exchanger needed to make the indirect method possible also creates
additional costs and heat losses. As can be seen, there are many trade-offs between using
indirect or direct methods for the primary water heating of the saline source. Either method
59
can be effective but most choices are made based upon the different type of systems to which
they are being adapted.
The type of heat exchanger used inside the condensation chamber depends entirely on
the method of condensation that has been chosen. This was described in some detail in the
dehumidifier/condenser section. Direct contact exchangers use spray towers and indirect
contact exchangers use piping in connection with fin arrays to produce the fresh water
condensate. As with the primary heating of the saline feed water, if the direct method is
chosen, then an additional indirect heat exchanger must be used at a later point to recovery
heat. In this case, the addition indirect heat exchanger takes warm fresh water from
production and cools it with the original cold feed water, preheating it prior to primary
heating.
60
CHAPTER 6 – THE POTENTIAL OF HDH WITH DIRECT
CONTACT CONDENSATION
6.1 THE DIFFUSION DRIVEN DESALINATION (DDD) PROCESS
As was mentioned in the review of current HDH systems, the use of direct contact
condensation has been more popular and James Klausner, along with his researchers at the
University of Florida, have done much work using this condensation method and have coined
their process as Diffusion Driven Desalination (DDD) [13]. Other than the use of the direct
contact condensation method in the dehumidification chamber, as opposed to general indirect
film condensation, there are no large differences between DDD and other HDH processes.
For ease of explanation, DDD will be used to describe any HDH process that uses direct
contact condensation and not just the ones developed at the University of Florida (UF).
Generally speaking, the DDD process operates a CAOW cycle configuration with water
heating, but can also incorporate air heating. As mentioned in the Dehumidifier/Condenser
and Heat Exchanger sections, there are two sources of water flow through the towers; the
saline feed water through the humidifier and re-circulated cooled fresh water. This means
that there are actually two separate semi-closed water loops used in DDD systems. Also as
previous described, there is a choice of direct and indirect heating of the saline feed water
source, and if the indirect method is used then there would be a third water loop for fresh
water heating. The DDD process takes all of the most effective HDH components and
methods in combination to make a highly efficient and productive HDH process. A flow
diagram of the proposed “Innovative Diffusion Driven Desalination Process” is shown in
61
Figure 15 below [13]. The primary focus of this chapter will be on DDD units like this, the
many variations developed by those at UF, and others.
Figure 15: Flow diagram for innovative diffusion driven desalination process [13].
6.2 ANALYSIS METHODS AND FINDINGS:
The optimization and analysis of the HDH process coupled with direct contact
condensation, and alike DDD systems, can lead to the increased potential for the HDH
technique to be a viable and productive method of desalination on a small-scale for
decentralized locations and island communities all over the world. Providing a renewable,
efficient, reliable, and cost effective form of fresh water production for those people that
need it most is the primary objective for small-scale desalination processes such as these.
Many different analysis techniques have been used by researchers to identify the key
enhancement operating parameters of various direct contact condensation HDH designs. The
62
majority of work performed on these systems has come from the University of Florida
research on their DDD process. Additional analysis of HDH with direct contact
condensation comes from work at the University of Hawaii at Manoa done by this author’s
predecessor and colleague Riley McGivern [14]. Riley was able to developed a simple
system which could be adaptable for small-scale renewable production in remote
communities and islands. Another collaborative work of engineers at the Beihang University
in China and the Technical University of Munich Germany presented a novel integration of
small spherical phase change material (PCM) elements as packing material in the direct
contact condenser [15]. The different optimization and analysis methods used by these
researchers, as well as an overview of their systems, are presented in the following.
To begin; the introduction of the DDD process in the Journal of Energy Resources
Technology initially presented it as a process with large-scale desalination production
potentials, capable of reducing cost values below that of RO and MSF [13]. The flow
diagram of the process introduced in this paper can be seen in Figure 15 on the previous
page. The system shown consumes waste heat from a power plant to provide the main feed
water heating and has two additional indirect heat exchangers; one water chiller for the fresh
water condensate and a regenerative heater. The water chiller uses the salt water source
drawn from a lower depth, giving cooler temperatures, to cool the exiting warm fresh water
production before it is sprayed into the direct contact condenser tower. The regenerative
heater attempts to capture the latent heat of condensation from the warm fresh water
production and transfer it to salt water drawn from the (less cool) surface water, before it
enters the primary heater. This process maybe effective given ideal location and salt water
source conditions but the use of two indirect heat exchangers, as opposed to one, could also
63
reduce the amount of heat recovered. The system shown also uses a closed-air loop driven
by a forced draft blower. The primary focus of the paper was a thermodynamic cycle
analysis in order to determine the performance bounds of their DDD process [13]. This
analysis was based on the rate of entropy generation per air flow rate in the humidification
chamber (or diffusion tower) which must be positive; and also upon the enthalpy of the brine
leaving the diffusion tower [13]. This exergy analysis was similar to many others seen in
literature from other HDH processes mentioned in the review. The conclusions yielded, as
others did, that with a higher inlet saline feed water temperature corresponding to an ideal air
to feed water mass flow ratio, there will be a minimum energy consumption rate [13]. They
also found that increasing the humidifier inlet water temperature increases the fresh water
production efficiency [13]. Based upon these results the authors were able to conclude that
the advantage to the DDD process is low exergy usage when driven by waste heat, with
satisfactory performance from inlet water temperatures as low as 50°C [13]. They went on
further to express the potential for inexpensive large-scale production.
The second major step for the UF team on their DDD process came through the
development of a detailed heat and mass transfer analysis to model the dynamic performance
of the cycle; this time based upon the flow diagram shown in Figure 16 [16]. This flow
diagram differs from the one original presented by Klausner and company in Figure 15. The
main differences being the flow of the fresh water production through the cooling heat
exchanger in connection with the flow of the saline feed water. The flow diagram also shows
an open-air loop where the air leaving the condenser is just exhausted as opposed to re-
circulated; this was done for ease of modeling of the system. The physical model developed
was based on a two-fluid film model with one-dimensional conservation equations for mass
64
and energy applied to a differential control volume, which can be seen in Figure 17 [16].
The control volume shown is just for the counter-current direct contact condenser, although
the model was created using both the humidifier and condenser. The model attempts to
describe the temperature of the water and air/vapor mixture as well as the humidity along the
heights of the towers from inlet of feed water to exit of fresh water. Three primary gradient
equations were developed for both the humidifier and condenser, however, since the direct
contact condensation is the focus, only these equations are shown in Eq. 1, 2, and 3,
respectively. Equation 1 describes the gradient of the temperature of the liquid water, TL,
along the height, z, of the condensation tower; where G is the air mass flux and L is the water
mass flux. Similarly, Equation 2 describes the gradient of the temperature of the air/vapor
mixture, Ta, along the height, z, of the condensation tower. Equation 3 describes the gradient
of the humidity ratio, ω, along the height, z, or the condensation tower; where Psat(Ta) is the
water saturation pressure corresponding to the local air temperature and is calculated using
an empirical representation of the saturation line [16].
65
Figure 16: Flow diagram for the DDD process [16].
Figure 17: Differential control volume for the direct contact condensation tower [16].
(1)
66
(2) (3)
In order to evaluate the heat and mass transfer coefficients associated with both the
evaporator and condenser processes, modified Onda’s correlations were used. Through the
use of Onda’s relations, the mathematical model can be solved using an iterative guess and
check procedure along the height of both the humidification and dehumidification towers.
The primary goal of the model was to show the dynamic performance of the system through
a parametric study. The optimal heights of both towers could be obtained based on the air to
feed water mass flow ratio. Also, the exit air and fresh water temperatures could be found
based on air mass flux, as well as the fresh water production efficiency. An energy analysis
based only on the energy required to power pumps and blowers, assuming primary heating
from power plant waste heat, was also described and the variation of the energy consumption
rate with the air to feed water mass flow ratio found. This energy analysis yielded a prime
consumption rate of 0.0022 kWh/kgfw; which can be re-written as 2.2 kWh/m3 of fresh water
[16]. This energy consumption rate would be competitive with RO, MSF, and MED, but
since the energy usage is based only upon electrical needs for pumps and blowers, it is
unrealistic to compare. This work showed the potential for improvement of the DDD system
based on a heat and mass transfer analysis.
A further adaptation of the work done in the paper described above on the DDD
system was conducted showing the correspondence of the modeling outputs with that of an
experimental setup. The focus of this work was on the experimental setup’s use of twin
condensation towers; one with co-current flow and the twin receiving the counter-current
flow [17]. A schematic diagram of the DDD experimental facility with twin condensation
towers can be seen in Figure 18. The goal of this work was to include the co-current flow
condenser tower into the model and to compare both condenser tower computational data
67
with that of the experimental findings. The addition of the co-current flow required another
differential control volume with opposite flow directions; therefore a new set of three
gradient equations were used as well. The liquid and air/vapor temperature gradients
remained unchanged, but the humidity ratio gradient was just the negative version of that for
the counter-current flow [17]. The flow diagram for the iterative computation procedure
used for the modeling of the counter-current flow through the condenser is shown in Figure
19. The procedure uses a guess and check approach with fourth order Runge-Kutta iterative
process to find all the corresponding values at the next step up in the z direction of the tower.
This procedure is very similar to that for the co-current flow (with same inputs), but for this
one the iterations will begin at the top of the packed bed and work down, instead of starting
at the bottom for the counter-current flow.
After running the model and experiments with both the co-current and counter-
current flow condensers separately, the authors found that there was good correlation
between the two for both flow patterns. However, both results showed that the effectiveness
of the co-current flow condensation tower was dramatically degraded in comparison with the
counter-current flow for the same air mass flow ratio and inlet conditions; the difference in
the effectiveness being approximately 15% [17]. This reduction in performance was
investigated through the use of high-speed cameras to capture the formation and shape of the
liquid film upon the packing material [17]. The cameras showed that the wetting of the
polyethylene packing ring structures has a high likelihood of forming liquid bridges which
can block the air flow [17]. However, as mentioned in other works, the use of this plastic
packing material is ideal for surface area maximization and works well in the evaporator and
is also cheap and easy to replace [17]. Because of the formation of these liquid bridges the
68
use of a counter-current flow is necessary to better disrupt and break these bridges, which is
why the co-current flow probably lost so much effectiveness. The authors suggested the
further investigation of these liquid bridge formations in connection with packing diameters
and wettability.
Figure 18: Schematic diagram of the DDD experimental facility with twin condensation towers [17].
69
Figure 19: Flow diagram procedure for computation of the counter‐current flow condenser [17].
A similar work to the ones just described was developed by Riley McGivern in his
HDH system with direct contact condensation [14]. When comparing the flow diagrams of
Riley’s system in Figure 20 on the next page, to that of the flow diagram used for modeling
(with only counter-current flow) by Klausner and company, they are very nearly the same
except for Riley’s use of a closed-air loop and also solar thermal energy for water heating.
However, it should be noted that Riley’s experimental set up also used an open-air loop as
did Klausner’s. Riley was also able to show the peak performance characteristics of his
system through the use of the two-fluid flow model for a packed bed through the application
of mass and energy conservation to differential control volumes for the evaporator and
condenser towers. Through this he was able to describe the changing liquid, air/vapor
70
temperature, and humidity ratio gradients along the height of the towers. Riley’s results
showed the changing exit water temperatures for the evaporator and condenser plotted versus
the varying air volume flux, while keeping the water mass flux constant [14]. Good
agreement was found between the model and the experimental results. Riley noted that the
implementation of solar thermal panels for heating would be possible based on the modeling
and experimental results [14].
Figure 20: Flow diagram of Riley’s HDH system with direct contact condensation [14].
In order to take the analysis of the DDD system to the next level, Klausner and
company turned their focus to the further development of their heat and mass transfer
analysis into a transient one. One-dimensional conservation equations were again used to
derive the necessary, now no longer steady-state, equations. Through the application of
conservation of mass and energy to the liquid phase and the air/vapor mixture side of the
control volume shown in Figure 21; two first order partial differential equations (PDEs) in
time and space are found to describe the temperature of the liquid and air/vapor mixture [18].
71
The gradient of the humidity ratio to the height, z, is found in a similar manner as the steady-
state case. An additional equation describing the differential of the temperature of the
packing material with respect to time is also generated through the conservation of energy on
the packed bed [18]. This set of four equations is used to solve a transient model from an
explicit finite difference method with a uniform grid size defined for the evaporator and
condenser mesh [18]. The set of equations used for the condenser; with the humidity ratio
gradient to height, z, and then the temperature of the liquid, the air/vapor mixture, and the
packing material with respect to time and are shown in Equations 4, 5, 6, and 7, respectively.
Closure relations are required along with the use of Onda’s correlations for the heat and mass
coefficients on the liquid and gas side are used to complete the solution. The results yielded
good correlations between the model and experimental for the water and air temperatures, but
the humidity ratio values experienced a maximum deviation around 20% [18].
Figure 21: Control volume used for evaporator and condenser towers, showing the interactions
between the liquid, gas/vapor, and solid packing material [18].
72
(4)
There are many applications for the transient modeling of the DDD process through
parametric studies to optimize operating conditions for varying water and/or air temperature
inputs [18]. Klausner, along with his team, decided to generate another paper which would
explore these applications focusing on that of coupling the DDD system with solar thermal
water heating [19]. This obvious combination has been explored in the HDH literature by
many others; however, Klausner and company were the first to publish about the transient
modeling of this specific process. With this most recent work, they have also become some
of the first to publish on the potential of the solar thermal panel integration. Although
Riley’s work did focus on the integration of the HDH cycle with direct contact condensation
with solar thermal heating, his model was used the steady-state conditions and therefore
could not input expected temperatures providing from a regular day of solar thermal heating.
In this work, “Solar diffusion driven desalination for decentralized water production”,
Klausner and corresponding author Alnaimat were able to show the expected production
values and energy consumption given the average solar thermal inputs for a clear day in
Jacksonville, Florida in the month of June [19]. They performed their analysis with a
73
specified number of solar thermal panels operating at set efficiencies. The solar array could
be varied for any system and location to provide the needed amount of thermal energy to
provide the optimal inlet feed water temperatures. This DDD process requires the use of
thermal and electrical energy, to heat the water and power pumps/blowers, respectively.
Therefore, a new electric specific energy consumption equation was also developed for this
application, which now takes into account the power needed for pumping through the solar
thermal panels and the major losses expected [19]. One of the primary findings boasted by
this work was the advantages of containing the latent heat of condensation within the system,
and not removing it through cooling as was done in the steady-state operation of their DDD
system in earlier works [19]. This idea is not novel and this recirculation and regeneration of
the latent heat of condensation has been achieved by many, including Riley and can be seen
in his system process in Figure 20. Also, it is notable, that when comparing this flow
diagram of Riley’s to the one used for the solar DDD process, shown in Figure 22, they are
very similar. The primary differences in these processes are the solar DDD’s employment of
multiple saline water tanks and the location of the fresh water cooling heat exchanger. The
location of the heat exchanger can have a drastic effect on the recovery of this latent heat and
will be discussed further in the following comparisons section.
There are many parameters which can be varied to analyze the system using this
transient model but the focus of this work was on the optimum operating mode. They
concluded that the best mode would be to use a delayed operating mode in which thermal
heat could be generated through the panels and stored prior to system startup [19]. They also
found through the parametric study that the air mass flux is a very important parameter and
this was also noticed by Riley is his work [19,14]. When using eight thermal panels for a
74
normal day in Florida, they found a maximum daily water production rate of 6.3 L/m2 of
collectors and an average specific energy consumption of 3.6 kWh/m3 of fresh water
produced [19]. From these findings Klausner and Alnaimat concluded that the solar DDD
system has high potential for small-scale fresh water production in decentralized areas [19].
Figure 22: Process flow diagram for solar diffusion driven desalination system [19].
Finally, there is one more performance analysis completed on an HDH process with
direct contact condensation which developed the novel idea of integrating phase change
materials (PCM) for the packing material. This work also performed a transient heat and
mass transfer analysis of their process using a different mathematic model than that executed
at UF by Klausner. This collaborative work between engineers at Beihang University in
China and the Technical University of Munich Germany [15] used a model that was
developed by an early work conducted in Brazil in 1999 [20] on possible fixed bed models
for pcm and sensible heat storage. In this early work by Ismail and company [20], many
75
different possible models were developed and shown; the one chosen for use by the
Germany/China team [15] was the continuous solid phase model. Through the application of
this continuous solid phase model in comparison with experimental findings they attempted
to find the effectiveness of small spherical PCM elements on the performance of the packed
bed condenser. The numerical solution of their one-dimensional model, which is made up of
a set of second-order parabolic PDEs, was done using MATLAB’s partial differential
equations solver called “pdepe” function [15]. After inputting the set of equations and
boundary conditions the “pdepe” solver is able to show the temporal and spatial evolutions of
temperature and vapor concentration fields of all the fluid and solid phases throughout the
towers [15].
The comparison of the numerical findings and the experimental was done in a
parametric analysis which investigated a number of parameters similar to those of other HDH
analysis but focused on the effects of the PCM thermal properties. The conclusions showed
that although in the initial startup of the system the PCM helped increase performance, when
steady-state operation was reached the thermal properties of the PCM actually decreased the
condenser effectiveness [15]. They also concluded, as did many others, that the air mass
flow ratio is of crucial importance on the system performance [15]. The authors proposed
that an investigation into a different packing material with high thermal conductivity, smaller
size, and lower cost than PCM could yield much better results as the PCM had poor thermal
conductivity at steady-state and very high costs [15].
76
6.3 SUMMARY OF ANALYSIS METHODS AND FINDINGS
There are many different approaches explored and presented above that all yielded
some important results for the potential of the HDH process with direct contact condensation
(or DDD process). Even though analysis methods varied drastically in complexity; from that
of a fairly simple exergy analysis to show operation bounds, to a highly involved transient
model with second-order PDEs to perform an accurate parametric study, they all provided
similar findings. Throughout these analysis methods the consistent findings were that the air
mass flux (or air mass flow ratio used by some) was the most important operating parameter.
Each system, however, was unique in what this optimum air mass flux would be to maximize
fresh water production and reduce energy consumption. Many other parameters were studied
and were optimized for each system and it is interesting to note that even though some
analyses were more complex the parametric optimizations were very similar.
The most interesting findings for this author came from looking at the differences in
the process setups and especially the many different iterations of the UF coined DDD
process, and comparing these with that of Riley McGivern’s system. Klausner and company
began with an exergy analysis and presented the DDD process as a lower cost large-scale
process with potential when coupled with power plants and using their waste heat, which
could rival RO, MSF, and MED [13]. These assertions were self-confirmed with a detailed
heat and mass transfer analysis of the steady-state operation through a parametric study and
energy analysis of a slightly varied DDD flow process (eliminating additional heat
exchangers). From this analysis Klausner presented a highly ambitions energy consumption
rate of 2.2 kWh/m3 fresh water, which as noted earlier, was only based on the electric energy
needed for pumps and blowers [16]. Klausner’s next work focused on the comparison of the
77
computer model with an experimental setup with a primary focus on the twin condensation
towers with co-current and counter-current flow. The primary findings from this work was
that the co-current flow condensation tower was ineffective and that through camera footage
the formation of liquid bridges on the packing material [17]. It can be inferred that the co-
current flow didn’t provide enough force to break these liquid bridges on the packing
material and therefore the condensation performance was drastically diminished. In the
transient analysis of the DDD process, the model showed good relation with experimental
results with temperature of the liquid and air, but the humidity ratio values were off by 20%
[18]. When comparing their set of equations with that of the ones performed in the PCM
condenser analysis with the continuous solid phase model, the equations were much simpler
and were not second-order parabolic PDEs. It can be concluded that to get good humidity
ratio or vapor concentration (as used in PCM analysis) relations, then the continuous solid
phase model should be used for any further transient investigations.
Finally, when looking at the flow diagram for the solar DDD system and comparing
with the diagram of Riley’s system, the location of the cooling heat exchanger for the fresh
water is different. In the solar DDD system; the fresh water production from the condenser is
dumped into a fresh water tank, fresh water is then drawn out by the pump and directed
through the heat exchanger where it is cooled by the entering saline feed water heading to the
saline feed water tanks. This flow process allows for the warm fresh water condensate
directly out of the condenser to mix and lose heat in the tank. The heat left in the fresh water
is transferred to the saline feed water which is also dumped into one of two tanks, again
allowing heat losses by mixing and through the tank. The little regenerative heating that
occurred at the heat exchanger is now lost and the saline feed water enters the solar collector
78
without being preheated effectively. Now, for Riley’s flow process; condensate from the
dehumidification tower is pumped directly to the heat exchanger allowing optimal heat
transfer to the saline feed water. The saline feed water is pumped directly from the saline
reservoir through the heat exchanger to be preheated right before it enters the solar seawater
heater. Although the DDD system proposed multiple “innovative” techniques, such as twin
condensers and the recovery and reuse of the latent heat of condensation, in the end these
methods were not very effective. The co-current tower was shown through experimental and
model results to highly degrade the condensation production [17]. Then, through a simple
flow process analysis, the heat recovery was shown to be less effective and when compared
with another flow diagram proved less energy efficient.
79
CHAPTER 7 – RESULTS AND DISCUSSIONS
Through this comparison and review of the many currently functional HDH process
configurations and modeling techniques the most effective systems have been identified and
analyzed in detail. Of the possible HDH cycle configurations, in general, the most effective
is the closed-air open-water cycle coupled with solar thermal water heating. The most
efficient humidification chamber design was found to use polyethylene packing material to
maximize surface area and spray nozzles to effectively cover this packed bed with the saline
feed water. This evaporation technique was found by most to be enhanced by adjusting the
air mass flux at a set water mass flux in order to provide the maximum humidity ratio at the
exit of humidifier. With a saturated air/vapor mixture entering the dehumidification
chamber, the goal now shifts to providing the greatest temperature differential between the
warm humid air and the cooling fluid, and also as with the humidifier to maximize the
surface area to volume ratio. In order to accomplish both of these goals in the condensation
tower design, the best method is direct contact condensation. Although the recovery of the
latent heat of condensation is better with indirect contact condensation heat exchangers, the
direct contact method increases the heat and mass transfer effectiveness through both
temperature differential and surface area. Therefore, the optimal condenser design will be
very similar to the evaporator and will have spray nozzles with a packed bed of polyethylene
grid rings. The spray for the condenser will use fresh water from production which has first
been cooled by entering saline feed water through an indirect heat exchanger. This heat
exchanger allows for both the recovery of some of the latent heat of condensation from the
warm condensate and also the preheating of the saline feed water. As was noted in the
comparison of the DDD processes, the placement of this heat exchanger in the flow process
80
is very important to the effectiveness of this heat recovery and regeneration. The most
effective placement is shown by Riley’s work in Figure 20.
The recovery and reuse of heat in the HDH process is of utmost importance to the
increased performance of the system. Thus the method and type of solar heating used is very
important. Both indirect and direct heat transfer methods can be used to provide the solar
thermal heating of the saline feed water source. Each method has its advantages and
disadvantages as described in detail in the heat exchanger section. In order to determine
which would be most effective, additional studies need to be performed on the efficiency of
new specialized seawater solar thermal panels and the longevity of such units analyzed for
scaling formation. There would be losses for both methods and therefore either could
potentially provide similar results over the long term.
Another important area of heat loss is in the water tanks, and one possible method to
reduce these heat losses would be the implementation of thermal storage tanks integrated
with phase change materials (PCM). The use of PCM was seen in a direct contact
condensation tower and its effectiveness at startup was productive, but during steady-state it
did not provide any increase in production. The further exploration of this PCM inside the
thermal storage tanks could increase the amount of heat retained, especially over a period of
time, such as the night. As the MEH system showed, the integration of regular thermal
storage methods allowed for the system to be run through the night and increase production
rates. Through the integration of PCM, these thermal storage tanks would be able to store
more energy at night and release it during the day time hours, potentially increasing
productivity even further.
81
Finally, additional work on the material and grid design of the packing material rings
could yield an optimal packed bed which would not experience the same liquid bridging that
occurred for the DDD processes. Both of the works that performed transient analyses for the
DDD system and the PCM system, concluded that the packing material needed to be
improved with increased thermal conductivity and an optimal grid spacing. Of these
transient analyses, the one for the PCM system using the continuous solid phase model was
more successful in producing good relation for not only the liquid and air/vapor temperatures
but also for the humidity ratio or vapor concentration. Therefore, this continuous solid phase
model, as first described by Ismail [20], would be the best choice for any further transient
analyses of the HDH process with direct contact condensation. One potential future work
could then be conducted with the use of both direct and indirect methods of saline water solar
thermal heating using the continuous solid phase model while testing polyethylene packing
grids of varying spacing.
82
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[17] Y. Li, J.F. Klausner, R. Mei, J. Knight, Direct contact condensation in packed beds. International Journal of Heat Mass Transfer, 49 (2006) 4751–4761.
[18] F. Alnaimat, J.F. Klausner, R. Mei, Transient analysis of direct contact evaporation and condensation within packed beds. International Journal of Heat Mass Transfer, 54 (2011) 3381–3393.
[19] F. Alnaimat, J.F. Klausner, Solar diffusion driven desalination for decentralized water production. Desalination, 289 (2012) 35-44.
[20] K.A.R. Ismail, R. Staginsky Jr., A parametric study on possible fixed bed models for pcm and sensible heat storage. Applied Thermal Engineering, 19 (1999) 757-78
APPENDIX A: WATER BUDGET
Function Gal Events Notes
Hot Water Draws 240 15 16 Will Draw from Fresh Water Tank
Water Vaporization 3 0.75 4 Will Draw from Fresh Water Tank
Dishwasher 10 2 5 Will Draw from Fresh Water Tank
Clothes Washer 160 20 8 Will Draw from Fresh Water Tank
Solar Thermal Tanks 80* Tank Capacity (*Will draw from Fresh Water to Provide Hot Water)
Fire Suppression Tank 266 280 Minimum 266 gallons needed for Fire Suppression
Thermal Storage Tank 770 770 Thermal Storage Water Fill
Fresh Water Tank 450 Initial Fresh Water Tank Fill
Aquaponics 50* 500**
*50 gallons Team Provided for Irrigation. **Capacity of system after
grey water recovery.
Safety Factor 50 N/A
Totals: 1499 1500
Water Required: ~1500 Gallons
CalculationsWater Use
(Gallons)
Water Storage
(Gal)
APPENDIX B: MECHANICAL SPECIFICATIONS SHEETS
DIVISION 21: FIRE SUPPRESSION
- SECTION 21 09 00: Instrumentation and control for fire-suppression systems - SECTION 21 13 00: Fire-suppression sprinkler systems - SECTION 21 24 16: Dry-chemical fire-extinguisher equipment - SECTION 21 31 13: Electric-Drive, Centrifugal fire pumps - SECTION 21 41 23: Ground suction storage tanks for fire-suppression water
DIVISION 22: PLUMBING
- SECTION 22 11 16: Domestic water piping - SECTION 22 11 23.26: Close-coupled, horizontally mounted, in-line centrifugal
domestic-water pumps - SECTION 22 12 19: Facility ground-mounted, potable-water storage tanks - SECTION 22 13 16: Sanitary waste and vent piping - SECTION 22 13 19.36: Air-admittance valves - SECTION 22 13 53: Facility septic tanks - SECTION 22 33 30.23: Residential, collector-to-tank, solar-electric domestic water
heaters - SECTION 22 41 00: Residential plumbing fixtures
DIVISION 23: HEATING, VENTILATION, AND AIR CONDITIONING
- SECTION 23 09 23: Direct-digital control system for HVAC - SECTION 23 21 13.43: Thermal mass-loop heat-pump piping - SECTION 23 21 23.13: In-line centrifugal hydronic pumps - SECTION 23 30 00: HVAC air distribution - SECTION 23 56 13.13: Heating solar flat-plate collectors - SECTION 23 71 13.23: Pressurized-water thermal storage tanks - SECTION 23 71 13.26: Phase change material for thermal mass - SECTION 23 81 46: Water-source unitary heat pumps - SECTION 23 84 16: Dehumidifiers
DIVISION 28: ELECTRONIC SAFETY AND SECURITY
- SECTION 28 31 46: Smoke detection sensors
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CENTRIFUGAL FIRE PUMPS 21 31 00 - 1
DIVISION 21: FIRE SUPPRESSION
SECTION 21 09 00
INSTRUMENTATION AND CONTROL FOR FIRE-SUPPRESSION SYSTEMS
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Jockey Pump Controller.
B. Related Requirements
1. Fire-Suppression Sprinkler Systems (Section 21 13 00).
2. Electric-Drive, Centrifugal Fire Pumps (Section 21 31 13).
3. Ground Suction Storage Tanks for Fire-Suppression Water (Section 21 41 23).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. NFPA – National Fire Protection Association.
3. UL – Underwriters Laboratories Inc.
1.01 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for Jockey Pump Controller.
1.02 QUALITY ASSURANCE
A. Certificates
1. UL certification of Jockey Pump Controller.
2. Compliance with IRC Section P2904 or NFPA 13D.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Firetrol® (or other manufacturer with similar product meeting all codes and requirements)
(www.firetrol.com).
Published
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CENTRIFUGAL FIRE PUMPS 21 31 00 - 2
2.02 CONTROLLERS
A. Firetrol® FTA500 Jockey Pump Controllers.
1. For use with Fire-Suppression system to regulate pump and control system pressure.
PART 3 – EXECUTION
3.01 INSTALLATION
A. To be installed and tested to Manufacturer’s requirements and IRC code.
END OF SECTION
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CENTRIFUGAL FIRE PUMPS 21 31 00 - 3
SECTION 21 13 00
FIRE-SUPPRESSION SPRINKLER SYSTEMS
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Fire Sprinklers.
2. Fire Sprinkler Piping.
3. Valves and Fittings.
4. Mounting Brackets.
B. Products Installed But Not Furnished Under This Section
1. Fire Pump.
2. Fire Water Storage Tank.
C. Related Requirements
1. Instrumentation and Control for Fire-Suppression Systems (Section 21 09 00).
2. Electric-Drive, Centrifugal Fire Pumps (Section 21 31 13).
3. Ground Suction Storage Tanks for Fire-Suppression Water (Section 21 41 23).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. NFPA – National Fire Protection Association.
3. UL – Underwriters Laboratories Inc.
4. ASTM – American Society for Testing and Materials
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for all products included in section.
B. Shop Drawings
1. Submit shop drawings of Fire-Suppression System.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC Section P2904 or NFPA 13D.
1.05 WARRANTY
A. Manufacturer’s Warranty
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CENTRIFUGAL FIRE PUMPS 21 31 00 - 4
1. Fire Sprinklers: Products manufactured by Tyco® Fire Suppression & Building Products (TFSBP)
are warranted solely to the original Buyer for ten (10) years against defects in material and
workmanship when paid for and properly installed and maintained under normal use and
service. This warranty will expire ten (10) years from date of shipment by TFSBP. No warranty is
given for products or components manufactured by companies not affiliated by ownership with
TFSBP or for products and components which have been subject to misuse, improper
installation, corrosion, or which have not been installed, maintained, modified or repaired in ac-
cordance with applicable Standards of the National Fire Protection Association, and/or the
standards of any authorities having jurisdiction. Materials found by TFSBP to be defective shall
be either repaired or replaced, at TFSBP’s sole option. TFSBP neither assumes, nor authorizes
any person to assume for it, any other obligation in connection with the sale of products or parts
of products. TFSBP shall not be responsible for sprinkler system design errors or inaccurate or
incomplete information supplied by Buyer or Buyer’s representatives.
2. Fire Sprinkler Piping and Accessories: Shall cover the repair or replacement of properly installed
tubing and fittings proven defective as well as incidental damages. Warranty period for PEX
tubing and subsequent system shall be 25 year non-prorated warranty against failure due to
defect in material or workmanship, beginning with the date of installation. It is the installer’s
responsibility to avoid mixing fittings manufactured by others as it will reduce the owner’s
warranty.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Sprinklers Heads: Tyco (www.tyco-fire.com).
B. Fire Sprinkler Piping: Uponor® PEX piping (www.uponor-usa.com).
C. Valves and Fittings: Uponor® PEX valves and fittings (www.uponor-usa.com).
D. Mounting Brackets: Uponor® PEX mounting (www.uponor-usa.com).
2.02 SPRINKLER HEADS
A. The TYCO RAPID RESPONSE Series LFII Residential Domed-Plate Concealed Pendent 4.9 K-Factor
Sprinklers (TY2234) are decorative, fast response, frangible bulb sprinklers designed for use in
residential occupancies such as homes, apartments, dormitories, and hotels. The Cover
Plate/Retainer Assembly conceals the sprinkler operating components above the ceiling. The domed
profile of the cover plate provides aesthetically appealing sprinkler design with lower flow rates than
can be achieved by lower profile cover plates. The separable two-piece design of the Cover Plate
and Support Cup Assemblies allows installation of the sprinklers and pressure testing of the fire
protection system prior to the installation of the ceiling or application of a finish coating.
B. The Series LFII Residential Domed- Plate Concealed Pendent Sprinklers (TY2234) are shipped with a
Dispos-able Protective Cap. The Protective Cap is temporarily removed for installation, and it must
be replaced to protect the sprinkler while the ceiling is being installed or finished. The tip of the
Protective Cap can also be used to mark the center of the ceiling hole into plaster board or ceiling
tiles by gently pushing the ceiling product against the Protective Cap. When ceiling installation is
complete, the Protective Cap must be removed and the Cover Plate Assembly installed. The
Protective Cap must be removed to ensure proper performance of the sprinklers.
2.03 FIRE SPRINKLER PIPING
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CENTRIFUGAL FIRE PUMPS 21 31 00 - 5
A. Uponor® PEX piping certified for use in Fire Protection systems
1. Cross-linked polyethylene (PEX) manufactured by the Silane method.
2. Non-barrier type.
a. Shall have a pressure and temperature rating of 160 PSI at 73°F, 100 PSI at 180°F and 80 PSI
at 200°F.
b. Tubing shall have a minimum of 6 months UV protection.
3. Manufactured in accordance with ASTM F876 and ASTM F877 and tested for compliance by an
independent third-party agency.
2.04 VALVES AND FITTINGS
A. Fittings shall be manufactured by Uponor® PEX, identified by the letters “Q” or “Z” and
Manufactured in accordance with ASTM F1807 or ASTM F2159 and/or comply with ASTM F877
system standard as identified on the fitting.
B. Valves shall be of the plastic or metal type, meeting the requirements of ASTM F877, identified as
such with the appropriate mark on the product.
2.05 MOUNTING BRACKETS
A. Mounting brackets provided by Uponor® PEX, in compliance with ASTM requirements.
PART 3 – EXECUTION
3.01 INSTALLATION
A. All Uponor® PEX products provided in this section should be installed to manufacturer’s
specifications and to IRC and NFPA code requirements.
END OF SECTION
Published
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CENTRIFUGAL FIRE PUMPS 21 31 00 - 6
SECTION 21 24 16
DRY-CHEMICAL FIRE-EXTINGUISHER EQUIPMENT
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Dry Powder Fire Extinguisher.
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. NFPA – National Fire Protection Association.
3. UL – Underwriters Laboratories Inc.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for Fire Extinguisher.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC Section P2904 or NFPA 13D.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. First Alert® (or other manufacturer with similar product meeting all codes and requirements).
2.02 FIRE EXTINGUISHERs
A. (2 ct) First Alert® Model FE3A40GR Rechargeable Heavy Duty Dry Powder Fire Extinguishers.
1. For use in case of controlled fire where one could safely use to extinguish.
PART 3 – EXECUTION
3.01 INSTALLATION
A. To be installed in locations in house where required by IRC and NFPA.
Published
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CENTRIFUGAL FIRE PUMPS 21 31 00 - 7
END OF SECTION
Published
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CENTRIFUGAL FIRE PUMPS 21 31 00 - 8
SECTION 21 31 13
ELECTRIC-DRIVE, CENTRIFUGAL FIRE PUMPS
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Electric-Drive, Centrifugal Fire Pump.
B. Related Requirements
1. Fire-Suppression Sprinkler Systems (Section 21 13 00).
2. Instrumentation and Control for Fire-Suppression Systems (Section 21 09 00).
3. Ground Suction Storage Tanks for Fire-Suppression Water (Section 21 41 23).
1.02 REFERENCES
1. Reference Standards
1. IRC – International Residential Code.
2. NFPA – National Fire Protection Association.
3. UL – Underwriters Laboratories Inc.
4. ISO – International Standards Organization.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for Fire Pump.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC Section P2904 or NFPA 13D.
1.05 WARRANTY
A. Manufacturer’s Warranty
1. Products manufactured by GRUNDFOS® PUMPS CORPORATION (Grundfos®) are warranted to
the original user only to be free of defects in material and workmanship for a period of 24
months from date of installation, but not more than 30 months from date of manufacture.
Grundfos® liability under this warranty shall be limited to repairing or replacing at Grundfos®
option, without charge, F.O.B. Grundfos® factory or authorized service station, any product of
Grundfos® manufacture. Grundfos® will not be liable for any costs of removal, installation,
transportation, or any other charges which may arise in connection with a warranty claim.
Products which are sold but not manufactured by Grundfos are subject to the warranty provided
by the manufacturer of said products and not by Grundfos® warranty. Grundfos® will not be
liable for damage or wear to products caused by abnormal operating conditions, accident,
Published
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CENTRIFUGAL FIRE PUMPS 21 31 00 - 9
abuse, misuse, unauthorized alteration or repair, or if the product was not installed in
accordance with Grundfos® printed installation and operating instructions.
2. The warranty period shall be a non-prorated period of 24 months from date of installation, not
to exceed 30 months from date of manufacture. Warranty shall cover pump, motor and add-on
modules as complete unit.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Grundfos® (or other manufacturer with similar product meeting all codes and requirements).
(www.grundfos.com)
2.02 ELECTRIC-DRIVE, CENTRIFUGAL FIRE PUMP
A. Grundfos® CR 5-8 Centrifugal Pump with standard cast iron and 304 stainless steel construction.
1. For use with Fire-Suppression System to regulate and provide water pressure to Fire Sprinkler
Heads.
2. The pumps shall have the following features:
a. The pump housing shall have a stainless steel neck ring to minimize recirculation and
increase pump efficiency.
b. The impellers shall be laser welded stainless to obtain maximum efficiency. Composite
material shall not be acceptable. The impellers shall be secured to the shaft with a neck ring
and a nut.
c. The suction and discharge flanges shall be tapped and drilled to allow gauge installation on
the pump.
d. The pumps shall have radial tungsten carbide sleeve bearings for extended life. Metal
impregnated carbon radial bearings shall not be acceptable.
e. Pump Construction:
1) Pump housing Cast Iron
2) Impellers, rotor can, rotor cladding 304 Stainless Steel
3) Shaft 316 Stainless Steel
4) Bearings Tungsten Carbide
5) Axial thrust bearing Carbon MY106
6) Shaft journals/ inner bearings Silicon Carbide
7) O-rings EPDM
8) Bearing plate 304 Stainless Steel
PART 3 - EXECUTION
3.01 INSTALLATION
A. The pump shaft shall be installed horizontally or vertically per manufacturer’s recommendations.
The system shall be vented out from a higher location form the pump. The required inlet pressure
by the pump shall be available at the pump inlet.
B. Pump location: The pump should be located in a dry, well-ventilated area which is not subject to
freezing or extreme variation in temperature. Care must be taken to ensure the pump is mounted at
least 6 inches (150 mm) clear of any obstruction or hot surfaces. The motor requires an adequate air
Published
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CENTRIFUGAL FIRE PUMPS 21 31 00 - 10
supply to prevent overheating and adequate vertical space to remove the motor for repair. For open
systems requiring suction lift the pump should be located as close to the water source as possible to
reduce piping losses.
C. Foundation: Concrete or similar foundation material should be used to provide a secure, stable
mounting base for the pump. See table of bolt hole center line dimensions for the various pump
types. Secure the pump to the foundation using all four bolts and shim pump base to assure the
pump is vertical and all four pads on the base are properly supported (uneven surfaces can result in
pump base breakage when mounting bolts are tightened). The pump can be installed vertically or
horizontally. Ensure that an adequate supply of cool air reaches the motor cooling fan. The motor
must never fall below the horizontal plane. Arrows on the pump base show the direction of flow of
liquid through the pump. To minimize possible noise from the pump, it is advisable to fit expansion
joints on either side of the pump and anti-vibration mountings between the foundation and the
pump.
Note: Care should be taken to ensure that the vent plug is located in the uppermost position.
Isolating valves should be fitted either side of the pump to avoid draining the system if the pump
needs to be cleaned, repaired or replaced.
3.02 TESTING
A. The pumps shall be factory performance and hydrostatic tested as a complete unit prior to
shipment. The testing shall be done in accordance with ISO 9906 Annex A. No test certificate is
required.
END OF SECTION
Published
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PLUMBING FIXTURES 22 40 00 - 1
SECTION 21 41 23
GROUND SUCTION STORAGE TANKS FOR FIRE-SUPPRESSION WATER
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. 300 Gallon Fire-Suppression Water Storage Tank.
B. Related Requirements
1. Fire-Suppression Sprinkler Systems (Section 21 13 00).
2. Electric-Drive, Centrifugal Fire Pumps (Section 21 31 13).
3. Instrumentation and Control for Fire-Suppression Systems (Section 21 09 00).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. NFPA – National Fire Protection Association.
3. UL – Underwriters Laboratories Inc.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for Fire-Suppression Water Storage Tank.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC Section P2904 or NFPA 13D.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Go To Tanks (or other manufacturer with similar product meeting all codes and requirements).
(www.gototanks.com/300RT-CRM.aspx)
2.02 PLASTIC STORAGE TANK
A. Go To Tanks 300RT-CRM Rectangular Utility Tank.
1. For use with Fire-Suppression system to store Fire-Suppression water.
Published
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PLUMBING FIXTURES 22 40 00 - 2
PART 3 – EXECUTION
3.01 INSTALLATION
A. To be installed on pallets to distribute weight evenly over ground surface.
END OF SECTION
END OF DIVISION 21
Published
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PLUMBING FIXTURES 22 40 00 - 3
DIVISION 22: PLUMBING
SECTION 22 11 16
DOMESTIC WATER PIPING
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Hot and Cold Water Piping.
2. Valves and Fittings.
3. Mounting brackets.
B. Related Requirements
1. Close-Coupled, Horizontally Mounted, In-Line Centrifugal Domestic-Water Pumps
(Section 22 11 23.26).
2. Facility Ground-Mounted, Potable-Water Storage Tanks (Section 22 12 19).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. IPC – International Plumbing Code.
3. UL – Underwriters Laboratories Inc.
4. UPC – Uniform Plumbing Code.
5. ASTM – American Society for Testing and Materials.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for all products included in section.
B. Shop Drawings
1. Submit shop drawings of Domestic Water Supply System.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC, IPC, and UPC.
1.05 WARRANTY
A. Manufacturer’s Warranty
1. Hot and Cold Water Piping and Accessories: Shall cover the repair or replacement of properly
installed tubing and fittings proven defective as well as incidental damages. Warranty period for
Published
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PLUMBING FIXTURES 22 40 00 - 4
PEX tubing and subsequent system shall be 25 year non-prorated warranty against failure due to
defect in material or workmanship, beginning with the date of installation. It is the installer’s
responsibility to avoid mixing fittings manufactured by others as it will reduce the owner’s
warranty.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Hot and Cold Water Piping: Uponor® PEX piping (www.uponor-usa.com).
B. Valves and Fittings: Uponor® PEX valves and fittings (www.uponor-usa.com).
C. Mounting Brackets: Uponor® PEX mounting (www.uponor-usa.com).
2.02 HOT AND COLD WATER PIPING
A. Uponor® PEX piping certified for use in Fire Protection systems
1. Cross-linked polyethylene (PEX) manufactured by the Silane method.
2. Non-barrier type.
a. Shall have a pressure and temperature rating of 160 PSI at 73°F, 100 PSI at 180°F and 80 PSI
at 200°F.
b. Tubing shall have a minimum of 6 months UV protection.
3. Manufactured in accordance with ASTM F876 and ASTM F877 and tested for compliance by an
independent third-party agency.
2.03 VALVES AND FITTINGS
A. Fittings shall be manufactured by Uponor® PEX, identified by the letters “Q” or “Z” and
Manufactured in accordance with ASTM F1807 or ASTM F2159 and/or comply with ASTM F877
system standard as identified on the fitting.
B. Valves shall be of the plastic or metal type, meeting the requirements of ASTM F877, identified as
such with the appropriate mark on the product.
2.04 MOUNTING BRACKETS
A. Mounting brackets provided by Uponor® PEX, in compliance with ASTM requirements.
PART 3 – EXECUTION
3.01 INSTALLATION
A. To be installed per Manufacturer’s requirements and IRC, IPC, UPC compliance.
END OF SECTION
Published
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PLUMBING FIXTURES 22 40 00 - 5
SECTION 22 11 23.26
CLOSE-COUPLED, HORIZONTALLY MOUNTED, IN-LINE CENTRIFUGAL DOMESTIC-WATER PUMPS
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Domestic Fresh Water Pump.
B. Related Requirements
1. Domestic Water Piping (Section 22 11 16).
2. Facility Ground-Mounted, Potable-Water Storage Tanks (Section 22 12 19).
1.02 REFERENCES
A. Abbreviations and Acronyms
1. POM: Polyoximetylen
2. NR-rubber: Natural Rubber
3. PPO: Polyphenylene Oxides
4. NBR-rubber: Nitrile-Butadiene Rubber
B. Reference Standards
1. IRC – International Residential Code.
2. IPC – International Plumbing Code.
3. UL – Underwriters Laboratories Inc.
4. UPC – Uniform Plumbing Code.
5. ASTM – American Society for Testing and Materials.
6. ISO – International Standards Organization.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for Domestic Fresh Water Pump.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC, IPC, and UPC.
1.05 WARRANTY
A. Manufacturer’s Warranty
1. Products manufactured by GRUNDFOS® PUMPS CORPORATION (Grundfos®) are warranted to
the original user only to be free of defects in material and workmanship for a period of 24
months from date of installation, but not more than 30 months from date of manufacture.
Grundfos® liability under this warranty shall be limited to repairing or replacing at Grundfos®
Published
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PLUMBING FIXTURES 22 40 00 - 6
option, without charge, F.O.B. Grundfos® factory or authorized service station, any product of
Grundfos® manufacture. Grundfos® will not be liable for any costs of removal, installation,
transportation, or any other charges which may arise in connection with a warranty claim.
Products which are sold but not manufactured by Grundfos are subject to the warranty provided
by the manufacturer of said products and not by Grundfos® warranty. Grundfos® will not be
liable for damage or wear to products caused by abnormal operating conditions, accident,
abuse, misuse, unauthorized alteration or repair, or if the product was not installed in
accordance with Grundfos® printed installation and operating instructions.
2. The warranty period shall be a non-prorated period of 24 months from date of installation, not
to exceed 30 months from date of manufacture. Warranty shall cover pump, motor and add-on
modules as complete unit.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Grundfos® (or other manufacturer with similar product meeting all codes and requirements).
(www.grundfos.com)
2.02 DOMESTIC FRESH WATER PUMP
A. Grundfos® MQ 3-45 Self-Priming Multistage Centrifugal Pump.
1. For use with Domestic Water Supply System to regulate and provide water pressure to fixtures.
2. The MQ is a complete, all-in-one unit, incorporating pump, motor, diaphragm tank, pressure and
flow sensor, controller and check valve. The controller ensures that the pump starts
automatically when water is consumed and stops automatically when the consumption ceases.
In addition, the controller protects the pump in case of faults.
B. Material Specifications as follows:
Published
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PLUMBING FIXTURES 22 40 00 - 7
PART 3 - EXECUTION
3.01 INSTALLATION
A. The pump shaft shall be installed horizontally per manufacturer’s recommendations. The terminal
box shall be located as per manufacturer’s recommendations. The system shall be vented out from
a higher location form the pump. The required inlet pressure by the pump shall be available at the
pump inlet.
B. Pump location: The pump should be located in a dry, well-ventilated area which is not subject to
freezing or extreme variation in temperature. Due to its compact design, the pump does not take up
much space and is easy to install. No space around the pump is required.
C. Self-priming pump: As it is self-priming, the MQ is able to pump water from a level below the pump.
Provided it is filled with water, the pump is able to lift water from a depth of 26 ft (8 m) in less than
5 minutes. This facilitates installation and startup of the pump and provides more reliable water
supply in installations where there is a risk of dry running and leakages in suction hose or pipes.
3.02 TESTING
A. The pumps shall be factory performance and hydrostatic tested as a complete unit prior to
shipment. The testing shall be done in accordance with ISO 9906 Annex A. No test certificate is
required
END OF SECTION
Published
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PLUMBING FIXTURES 22 40 00 - 8
SECTION 22 12 19
FACILITY GROUND-MOUNTED, POTABLE-WATER STORAGE TANKS
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. 500 Gallon Potable-Water Storage Tank.
B. Related Requirements
1. Domestic Water Piping (Section 22 11 16).
2. Facility Ground-Mounted, Potable-Water Storage Tanks (Section 22 12 19).
3. Close-Coupled, Horizontally Mounted, In-Line Centrifugal Domestic-Water Pumps
(Section 22 11 23.26).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. IPC – International Plumbing Code.
3. UL – Underwriters Laboratories Inc.
4. UPC – Uniform Plumbing Code.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for Potable-Water Storage Tank.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC, IPC, and UPC.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Go To Tanks (or other manufacturer with similar product meeting all codes and requirements).
(www.gototanks.com/500RT.aspx)
2.02 POTABLE-WATER STORAGE TANK
A. Go To Tanks 500RT-CRM Rectangular Utility Tank.
Published
Page -- 9
PLUMBING FIXTURES 22 40 00 - 9
1. For use with Domestic Water Supply System to store fresh water.
PART 3 – EXECUTION
3.01 INSTALLATION
A. To be installed on pallets to distribute weight evenly over ground surface.
END OF SECTION
Published
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PLUMBING FIXTURES 22 40 00 - 10
SECTION 22 13 16
SANITARY WASTE AND VENT PIPING
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Sanitary Piping.
2. Vent Piping.
3. Valves and Fittings.
4. Mounting Brackets.
B. Related Requirements
1. Air-Admittance Valves (Section 22 13 19.36).
2. Facility Septic Tanks (Section 22 13 53).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. IPC – International Plumbing Code.
3. UL – Underwriters Laboratories Inc.
4. UPC – Uniform Plumbing Code.
5. ASTM – American Society for Testing and Materials.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for all products included in section.
B. Shop Drawings
1. Submit shop drawings of Sanitary and Venting System.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC, IPC, and UPC.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Any providers with products meeting builder’s needs and ASTM standards, as well as compliant with
IRC, IPC, and UPC.
Published
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PLUMBING FIXTURES 22 40 00 - 11
2.02 SANITARY PIPING
A. PVC piping meeting ASTM standard.
1. For use with Sanitary and Venting System to drain water from fixtures into Sanitary-Water
Storage Tank.
2.03 VENT PIPING
A. PVC piping meeting ASTM standard.
1. For use with Sanitary and Venting System to allow air to escape through the roof of the building
and prevent drainage problems.
2.04 VALVES AND FITTINGS
A. PVC fittings and valves meeting ASTM standard.
1. For use with Sanitary and Venting System to connect piping and adjust flow conditions.
2.05 MOUNTING BRACKETS
A. PVC mounting brackets meeting ASTM standard.
2. For use with Sanitary and Venting System to hang piping.
PART 3 – EXECUTION
3.01 INSTALLATION
A. To be installed per requirements of IRC, IPC, and UPC.
END OF SECTION
Published
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PLUMBING FIXTURES 22 40 00 - 12
SECTION 22 13 19.36
AIR-ADMITTANCE VALVES
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Air-Admittance Valves.
B. Related Requirements
1. Sanitary Waste and Vent Piping (Section 22 13 16).
2. Facility Septic Tanks (Section 22 13 53).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. IPC – International Plumbing Code.
3. UL – Underwriters Laboratories Inc.
4. UPC – Uniform Plumbing Code.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for Air-Admittance Valves.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC Section P3114, IPC, and UPC.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Any providers with products meeting builder’s needs and ASTM standards, as well as compliant with
IRC, IPC, and UPC.
2.02 AIR-ADMITTANCE VALVES
A. Individual Air admittance valves (AAVs).
1. AAV’s are pressure-activated, one-way mechanical vents. For use with Sanitary and Venting
System provide venting to low flow fixtures to eliminate the need for conventional pipe venting
and roof penetrations for these fixtures. Regular Venting still required for high flow fixtures.
Published
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PLUMBING FIXTURES 22 40 00 - 13
PART 3 – EXECUTION
3.01 INSTALLATION
A. To be installed per requirements of IRC, IPC, and UPC.
END OF SECTION
Published
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PLUMBING FIXTURES 22 40 00 - 14
SECTION 22 13 53
FACILITY SEPTIC TANKS
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. 500 Gallon Sanitary-Water Storage Tank.
B. Related Requirements
1. Sanitary Waste and Vent Piping (Section 22 13 16).
2. Air-Admittance Valves (Section 22 13 19.36).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. IPC – International Plumbing Code.
3. UL – Underwriters Laboratories Inc.
4. UPC – Uniform Plumbing Code.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for Sanitary -Water Storage Tank.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC, IPC, and UPC.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Go To Tanks (or other manufacturer with similar product meeting all codes and requirements).
(www.gototanks.com/500RT.aspx)
2.02 SANITARY -WATER STORAGE TANK
A. Go To Tanks 500RT-CRM Rectangular Utility Tank.
1. For use with Sanitary and Venting System to store grey/used water.
Published
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PLUMBING FIXTURES 22 40 00 - 15
PART 3 – EXECUTION
3.01 INSTALLATION
C. To be installed on pallets to distribute weight evenly over ground surface.
END OF SECTION
Published
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PLUMBING FIXTURES 22 40 00 - 16
SECTION 22 33 30.23
RESIDENTIAL, COLLECTOR-TO-TANK, SOLAR-ELECTRIC DOMESTIC WATER HEATERS
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Solar Hot Water Storage Tank with Backup Heating.
2. Solar Hot Water Storage Tank.
3. Solar Hot Water Circulating Pump.
4. Solar Hot Water Piping, Fittings, and Valves.
B. Related Requirements
1. Domestic Water Piping (Section 22 11 16).
2. Heating Solar Flat-Plate Collectors (Section 23 56 13.13).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. IPC – International Plumbing Code.
3. UL – Underwriters Laboratories Inc.
4. UPC – Uniform Plumbing Code.
5. ASTM – American Society for Testing and Materials.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for all products included in section.
B. Shop Drawings
1. Submit shop drawings of Solar Hot Water System.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC, IPC, and UPC.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Solar Hot Water Storage Tank with Backup Heating: Rheem Marathon® Thermal Storage Tanks.
(www.marathonheaters.com)
Published
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PLUMBING FIXTURES 22 40 00 - 17
B. Solar Hot Water Storage Tank: Rheem Marathon® Thermal Storage Tanks.
(www.marathonheaters.com)
C. Solar Hot Water Circulating Pump: Grunfos® UP 15-18SU LC Circulating Pump.
(www.grundfos.com)
D. Solar Hot Water Piping, Fittings, and Valves: Any provider with code compliant products.
2.02 SOLAR HOT WATER STORAGE TANK WITH BACKUP HEATING
A. 40 Gallon Rheem Marathon® Thermal Storage Tank with Backup Heating Element.
1. For use with Solar Hot Water System to store hot water and provide backup heating when solar
thermal gains are not enough.
2.03 SOLAR HOT WATER STORAGE TANK
A. 40 Gallon Rheem Marathon® Thermal Storage Tank.
1. For use with Solar Hot Water System to store hot water.
2.04 SOLAR HOT WATER CIRCULATING PUMP
A. Grunfos® UP 15-18SU LC Circulating Pump.
1. For use with Solar Hot Water System to circulate water through Solar Thermal Collector Panels
and into storage tanks.
2.05 SOLAR HOT WATER PIPING, FITTINGS, AND VALVES
A. Copper piping with insulation per ASTM standards and IRC.
B. Copper pipe fittings meeting ASTM standards and IRC.
C. Copper pipe valves meeting ASTM standards and IRC.
PART 3 – EXECUTION
3.01 INSTALLATION
A. To be installed per Manufacturer’s requirements and IRC, IPC, UPC compliance.
END OF SECTION
Published
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PLUMBING FIXTURES 22 40 00 - 18
SECTION 22 41 00
RESIDENTIAL PLUMBING FIXTURES
PART 1 – GENERAL
1.01 SUMMARY
A. Section includes
1. Kitchen Sink, Faucet, and Strainer.
2. Bathroom Sink, Faucet, and Drain.
3. Handshower Kit, Drain, Stack Valve, and Stack Valve Trim.
4. Water Closet.
B. Related Requirements
1. Domestic Water Piping (Section 22 11 16).
2. Sanitary Waste and Vent Piping (Section 22 13 16).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. IPC – International Plumbing Code.
3. UL – Underwriters Laboratories Inc.
4. UPC – Uniform Plumbing Code.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for all products included in section.
B. Shop Drawings
1. Submit shop drawings of detail connections of plumbing to fixtures.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC, IPC, and UPC.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Kohler Kitchen & Bath
2.02 KITCHEN SINK, FAUCET, AND STRAINER
Published
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PLUMBING FIXTURES 22 40 00 - 19
A. Kohler K7507 Faucet:
(http://www.us.kohler.com/onlinecatalog/detail.jsp?from=thumb&frm=null&module=Kitchen+Sink
+Faucets&item=15108502&prod_num=7507§ion=1&category=4&resultPage=0).
B. Kohler K3331 Sink:
(http://www.us.kohler.com/onlinecatalog/detail.jsp?from=thumb&frm=null&module=Kitchen+Sinks
&item=242302&prod_num=3331§ion=1&category=5&resultPage=0-1315060530).
C. Kohler K8801 Duo Sink Strainer:
(http://www.us.kohler.com/onlinecatalog/detail.jsp?item=468302§ion=1&category=7&subcate
gory=41&retail=false).
2.03 BATHROOM SINK, FAUCET, AND DRAIN
A. Kohler k7507 Faucet:
(http://www.us.kohler.com/onlinecatalog/detail.jsp?from=thumb&frm=null&module=Kitchen+Sink
+Faucets&item=15108502&prod_num=7507§ion=1&category=4&resultPage=0).
B. Kohler Vox Vessel Lavatory:
(http://www.us.kohler.com/onlinecatalog/detail.jsp?from=thumb&frm=&module=Lavatories&item
=15184302&prod_num=14800§ion=2&category=16&resultPage=0-1420926875).
C. Kohler K-7124-A-cp Pop-up :
(http://www.us.kohler.com/onlinecatalog/detail.jsp?item=11987102&retail=false).
2.04 HANDSHOWER KIT, DRAIN, STACK VALVE, AND STACK VALVE TRIM
A. Kohler K8487 Hand shower:
(http://www.us.kohler.com/onlinecatalog/detail.jsp?from=thumb&frm=&module=Handshower+Acc
essories&item=13645102&prod_num=8487§ion=2&category=12&resultPage=0-1846098269).
B. Kohler K-9132 Drain:
(http://www.us.kohler.com/onlinecatalog/detail.jsp?item=473002&retail=false).
C. Kohler K-T14489-4-cp Trim:
(http://search.us.kohler.com/?q=Purist%AE+stacked+valve+trim&x=6&y=7).
D. Kohler Stack Valve:
(http://search.us.kohler.com/?q=MasterShower%AE+thermostatic+valve+with+integrated+volume+
control+&x=21&y=6).
2.05 WATER CLOSET
A. Kohler K-3492-0 Toilet: (http://search.us.kohler.com/?q=hatbox).
PART 3 – EXECUTION
3.01 INSTALLATION
A. To be installed per Manufacturer’s requirements and IRC, IPC, UPC compliance.
END OF SECTION
END OF DIVISION 22
Published
Page -- 20
PLUMBING FIXTURES 22 40 00 - 20
DIVISION 23: HEATING, VENTILATING,
AND AIR-CONDITIONING (HVAC)
SECTION 23 09 23
DIRECT-DIGITAL CONTROL SYSTEM FOR HVAC
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. HVAC Controller Unit.
B. Related Requirements
1. In-Line Centrifugal Hydronic Pumps (Section 23 21 23.13).
2. HVAC Air Distribution (Section 23 30 00).
3. Water-Source Unitary Heat Pumps (Section 23 81 46).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. ASHRAE – American Society of Heating, Refrigerating and Air-Conditioning Engineers.
3. UL – Underwriters Laboratories Inc.
4. AHRI – Air-Conditioning, Heating and Refrigeration Institute.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for HVAC Controller.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. AHRI certification.
3. Compliance with IRC and ASHRAE standards.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Johnson Controls® (or other manufacturer with similar product meeting all codes and
requirements). (www.johnsoncontrols.com)
Published
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PLUMBING FIXTURES 22 40 00 - 21
2.02 HVAC CONTROLLERS
A. Johnson Controls® RJ Series Controls - Premier Microprocessor.
1. For use with HVAC System to regulate Thermal Mass Pump and Heat Pump fan in order to
achieve desired indoor air conditions.
PART 3 – EXECUTION
3.01 INSTALLATION
A. To be installed and tested to Manufacturers requirements and IRC and ASHRAE standards.
END OF SECTION
Published
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PLUMBING FIXTURES 22 40 00 - 22
SECTION 23 21 13.43
THERMAL MASS-LOOP HEAT-PUMP PIPING
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Thermal Mass-Loop Heat-Pump Piping.
B. Related Requirements
1. In-Line Centrifugal Hydronic Pumps (Section 23 21 23.13).
2. HVAC Air Distribution (Section 23 30 00).
3. Water-Source Unitary Heat Pumps (Section 23 81 46).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. ASHRAE – American Society of Heating, Refrigerating and Air-Conditioning Engineers.
3. UL – Underwriters Laboratories Inc.
4. ASTM – American Society for Testing and Materials.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for Thermal Mass-Loop Heat-Pump Piping.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC and ASHRAE standards.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Any provider with products meeting system requirements and IRC.
2.02 THERMAL MASS-LOOP HEAT-PUMP PIPING
A. Copper Piping with insulation meeting ASTM standards and Heat-Pump Manufacturer’s
requirements.
1. For use with HVAC System to transport Thermal Mass fluid to and from the Heat-Pump unit.
Published
Page -- 23
PLUMBING FIXTURES 22 40 00 - 23
PART 3 – EXECUTION
3.01 INSTALLATION
A. To be installed and tested to Manufacturer’s requirements and IRC and ASHRAE standards.
B. Thermal Mass Water Piping: Piping is usually designed as ‘reverse return’ to equalize flow paths
through each unit. A short flexible pressure rated hose is used to make connection to the fixed
building piping system. This hose is typically stainless steel braid and includes a swivel fitting on one
end for easy removal and is flexible to help isolate the unit for quieter operation. Isolation valves for
servicing, y-strainers for filtering and memory-stop flow valve or a balancing valve can be provided
for consistent water flow through the unit. All unit source water connections are fittings that accept
a male pipe thread (MPT). Insert the connectors by hand, and then tighten the fitting with a wrench
to provide a leak proof joint. The open and closed loop piping system should include
pressure/temperature ports for serviceability. The proper water flow must be provided to each unit
whenever the unit operates. To assure proper flow, use pressure/temperature ports to determine
the flow rate. These ports should be located at the supply and return water connections on the unit.
The proper flow rate cannot be accurately set without measuring the water pressure drop through
the refrigerant-to-water heat exchanger. Limit hose length to 10 feet per connection. Check
carefully for water leaks.
END OF SECTION
Published
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PLUMBING FIXTURES 22 40 00 - 24
SECTION 23 21 23.13
IN-LINE CENTRIFUGAL HYDRONIC PUMPS
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Thermal Mass Booster Pump.
B. Related Requirements
1. Thermal Mass-Loop Heat-Pump Piping (Section 23 21 13.43).
2. HVAC Air Distribution (Section 23 30 00).
3. Water-Source Unitary Heat Pumps (Section 23 81 46).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. ASHRAE – American Society of Heating, Refrigerating and Air-Conditioning Engineers.
3. UL – Underwriters Laboratories Inc.
4. ISO – International Standards Organization.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for Thermal Mass Booster Pump.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC and ASHRAE standards.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Dayton® (or other manufacturer with similar product meeting all codes and requirements).
(www.grainger.com)
2.02 THERMAL MASS BOOSTER PUMP
A. Dayton® Multistage Booster Pumps.
1. For use with HVAC System to pump Thermal Mass fluid to and from the Heat-Pump unit.
Published
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PLUMBING FIXTURES 22 40 00 - 25
2. The Multistage Booster Pump increases pressure from city mains, or can pump water from
cisterns and private ponds to ensure the proper operation of filtration equipment. Each pump
stage has a 304 stainless steel radial bearing, Noryl® impeller, and Delrin® diffuser. All are rated
for continuous duty.
3. Cast-Iron housings feature cast-iron suction and discharge housings and mechanical seat with
stainless steel, Buna N, and carbon/silicon carbide parts.
PART 3 – EXECUTION
3.01 INSTALLATION
A. The pump shaft shall be installed horizontally per manufacturer’s recommendations. The system
shall be vented out from a higher location form the pump. The required inlet pressure by the pump
shall be available at the pump inlet.
B. Pump location: The pump should be located in a dry, well-ventilated area which is not subject to
freezing or extreme variation in temperature.
C. Pump Priming: Self-priming to 10 ft. when pump housing and suction housing are filled; must
maintain 1.5 gpm flow to pump for proper seal and pump housing lubrication. If liquid temperature
is above 60°F, pumps require inlet pressure of 10 psi.
D. Electronic Pump Protectors: An electronic pump protector can be used to monitor water flow and
automatically shut down the motor when flow drops below 1.0 gpm; protect pumps against damage
caused by dry run or dead head conditions. The motor will turn back on to boost system pressure
when flow goes back above that level.
3.02 TESTING
A. The pumps shall be factory performance and hydrostatic tested as a complete unit prior to
shipment. The testing shall be done in accordance with ISO 9906 Annex A. No test certificate is
required.
END OF SECTION
Published
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PLUMBING FIXTURES 22 40 00 - 26
SECTION 23 30 00
HVAC AIR DISTRIBUTION
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Metal Ducts.
2. Volume-Control Dampers.
3. Backdraft Dampers.
4. Flexible Duct Collars.
5. Flexible Hose Ducts.
6. Floor Diffusers.
7. Duct Insulation Liners.
8. Bathroom Ventilation Fan.
B. Related Requirements
1. Thermal Mass-Loop Heat-Pump Piping (Section 23 21 13.43).
2. In-Line Centrifugal Hydronic Pumps (Section 23 21 23.13).
3. Water-Source Unitary Heat Pumps (Section 23 81 46).
4. Dehumidifiers (Section 23 84 16).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. ASHRAE – American Society of Heating, Refrigerating and Air-Conditioning Engineers.
3. UL – Underwriters Laboratories Inc.
4. ASTM – American Society for Testing and Materials.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for all products included in section.
B. Shop Drawings
1. Submit shop drawings of HVAC System Diagram.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC and ASHRAE standards.
PART 2 – PRODUCTS
Published
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PLUMBING FIXTURES 22 40 00 - 27
2.01 MANUFACTURERS
A. Metal Ducts: To be manufactured by builder.
B. Volume-Control Dampers: Any provider meeting IRC and ASHRAE standards.
C. Backdraft Dampers: Any provider meeting IRC and ASHRAE standards.
D. Flexible Duct Collars: Any provider meeting IRC and ASHRAE standards.
E. Flexible Hose Ducts: Any provider meeting IRC and ASHRAE standards.
F. Floor Diffusers: Any provider meeting IRC and ASHRAE standards.
G. Duct Insulation Liners: Any provider meeting IRC and ASHRAE standards.
H. Bathroom Ventilation Fan: Panasonic®(www.panasonic.com).
2.02 METAL DUCTS
A. Ducts to be manufactured by builder to meet system requirements and IRC and ASHRAE standards.
1. Ducts to be secured by mounting brackets approved for application.
2. Ducts will be constructed of sheet metal meeting ASTM requirements.
2.03 VOLUME-CONTROL DAMPERS
A. Volume-Control Dampers will be installed into ducting for HVAC System balancing and adjustment.
2.04 BACKDRAFT DAMPERS
A. Backdraft Dampers to be installed in ducts to prevent flow of air in the wrong direction.
2.05 FLEXIBLE DUCT COLLARS
A. Flexible Duct Collars to be installed at supply and return duct connections to Heat-Pump in order to
prevent noise and vibration.
2.06 FLEXIBLE HOSE DUCTS
A. Flexible Hose Ducts will be used in place of metal ducting when applicable.
2.07 FLOOR DIFFUSERS
A. Floor Diffusers will be installed for both supply and return venting into and out of conditioned
spaces inside house.
2.08 DUCT INSULATION LINERS
A. Duct Insulation Liners will be used on both supply and return ducts with a minimum of 1 inch
thickness, complying with IRC and ASHRAE standards. Duct liners are used to insulate and prevent
heat transfer to conditioned air in ducts.
2.09 BATHROOM VENTILATION FAN
A. Panasonic® WhisperGreen-LiteTM
Ventilation Fan.
1. For use in Bathroom to provide ventilation.
Published
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PLUMBING FIXTURES 22 40 00 - 28
2. Ventilating fan shall be Low Noise ceiling mount type rated for continuous run. Fan shall be
ENERGY STAR rated and certified by the Home Ventilating Institute (HVI). Fan shall include
energy efficient compact fluorescent lighting. Evaluated by Underwriters Laboratories and
conform to both UL and cUL safety standards.
3. Motor/Blower:
a. Enclosed DC brushless motor technology rated for continuous run.
b. Power Rating shall be 120 volts and 60 Hz.
c. Fan shall be UL listed for tub/shower enclosure when used with a GFCI branch circuit wiring
and use in insulated ceiling (TYPE I.C.).
d. Motor equipped with thermal cut-off fuse control.
e. Removable with permanently lubricated plug–in motor.
4. Housing:
a. Rust proof paint, galvanized steel body.
b. Detachable 4" diameter duct adapter.
c. Built in backdraft damper.
d. Double hanger bar system allowing for ideal positioning.
5. Grille:
a. Attractive design using PP material.
b. Attaches directly to housing with torsion springs.
6. Light:
a. One 32-watt electronic ballast compact fluorescent lamps included.
b. One 4-watt, night-light included.
PART 3 – EXECUTION
3.01 INSTALLATION
A. Ductwork:
1. Ensure return air grilles will not allow line of site noise to transfer to adjacent space. Use a
sound barrier or some other material to isolate the grille from the unit. A supply grille, boot and
short piece of flex duct pointed away from the unit can greatly attenuate equipment noise.
2. Use a canvas isolation duct connector at the supply and return duct connection of the unit.
3. Internally line the discharge and return duct within the first 4-8 feet of unit with acoustic
insulation. Install an internally lined ‘L’ shaped return duct elbow at return grille. Face the elbow
away from adjacent units.
4. Always install at least one 90° elbow in the discharge duct to eliminate line of sight noise
transmission of the blower.
5. Use turning vanes at all elbows and tees to reduce turbulence.
6. Limit supply duct velocities to less than 1000 fpm
7. Design and install ductwork as stiff as possible
8. Allow 3 duct diameters both up and down stream of the unit before any fittings or transitions
are installed.
9. Use duct sealant on all duct joints.
10. Install a short (2-4’) of flex duct on all branch ducts just prior to discharge boot or diffuser to
reduce vibration and duct sound prior to delivery in the room.
11. Locate the branch duct balancing damper as far away from the diffuser as possible.
12. In ceiling plenum systems, install an internally lined ‘L’ shaped return duct elbow at unit. Face
the elbow away from adjacent units (horizontal).
Published
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PLUMBING FIXTURES 22 40 00 - 29
3.02 TESTING
B. Testing and balancing of HVAC System to be done in accordance with ASHRAE standards and meet
Manufacturer requirements of the Heat-Pump unit.
END OF SECTION
Published
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PLUMBING FIXTURES 22 40 00 - 30
SECTION 23 56 13.13
HEATING SOLAR FLAT-PLATE COLLECTORS
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Solar Hot Water Flat-Plate Collectors.
B. Related Requirements
1. Domestic Water Piping (Section 22 11 16).
2. Residential, Collector-to-Tank, Solar-Electric Domestic Water Heaters (Section 22 33 30.23).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. IPC – International Plumbing Code.
3. UL – Underwriters Laboratories Inc.
4. UPC – Uniform Plumbing Code.
5. ASTM – American Society for Testing and Materials.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for Solar Hot Water Flat-Plate Collectors.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC, ASTM, and ASHRAE standards.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. SunEarth® Inc. (or other manufacturer with similar product meeting all codes and requirements).
(www.sunearthinc.com)
2.02 SOLAR HOT WATER FLAT-PLATE COLLECTORS
A. SunEarth® Empire Series Glazed Flat Plate Solar Collectors.
Published
Page -- 31
PLUMBING FIXTURES 22 40 00 - 31
1. Three (3) Empire EP21 Panels will be installed in conjunction with Solar Hot Water System to
provide thermal energy to water as it passes through panel setup and then returns to Solar Hot
Water Storage Tanks.
PART 3 – EXECUTION
3.01 INSTALLATION
A. System shall be installed following Solar Thermal System sizing and mounting standards. Follow
Manufacturer’s requirements as well as following IRC, IPC, and UPC standards.
3.02 TESTING
A. System testing shall be performed to Manufacturer’s requirements.
END OF SECTION
Published
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PLUMBING FIXTURES 22 40 00 - 32
SECTION 23 71 13.23
PRESSURIZED-WATER THERMAL STORAGE TANKS
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Thermal Mass Pillow Tank.
2. Thermal Mass Fill Hose.
B. Related Requirements
1. Thermal Mass-Loop Heat-Pump Piping (Section 23 21 13.43).
2. In-Line Centrifugal Hydronic Pumps (Section 23 21 23.13).
3. Water-Source Unitary Heat Pumps (Section 23 81 46).
4. Phase Change Material for Thermal Mass (23 71 13.26).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. ASHRAE – American Society of Heating, Refrigerating and Air-Conditioning Engineers.
3. UL – Underwriters Laboratories Inc.
4. ASTM – American Society for Testing and Materials.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for Thermal Mass Pillow Tank and Thermal Mass Fill
Hose.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC, ASTM, ASHRAE standards.
1.05 WARRANTY
A. Manufacturer’s Warranty
1. The Original Rainwater Pillow®: Rainwater Collection Solutions, Inc., warrants that for 5 years
from the date of purchase that The Original Rainwater Pillow will be free from defects in
materials. This warranty extends to the initial purchaser of The Original Rainwater Pillow, and is
valid for the 5 years from the date of purchase. If within 5 years from the date of purchase, the
product shall prove to be defective in the materials used, it shall be repaired or replaced at
Rainwater Collection Solutions, Inc., option. The original receipt of purchase is required to
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determine warranty eligibility. No warranty implied or express is given by Rainwater Collection
Solutions, Inc., related to the installation of The Original Rainwater Pillow. This includes any
leaks that result from the connection of pipes, pumps, or other devises necessary to the
operation of The Original Rainwater Pillow. The Original Rainwater Pillow is not warranted
against: acts of God, abuse, tampering, freezing, alteration in design, overfilling, storage of
liquids (other than rainwater), and problems associated with the lack of filter maintenance. The
Original Rainwater Pillow may not be used for the transportation of liquids, and the warranty
does not extend to such uses.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Thermal Mass Pillow Tank: Rainwater Collection Solutions, Inc. (or other manufacturer with similar
product meeting all codes and requirements). (www.rainwaterpillow.com).
B. Thermal Mass Fill Hose: Abbott Rubber Company, Inc. (or other manufacture with similar product).
(www.abbottrubber.com).
2.02 THERMAL MASS PILLOW TANK
A. The Original Rainwater Pillow® Tank (1500 Gallon).
1. For use with HVAC System to store Phase Change Material along with water creating a Thermal
Mass fluid, which will be circulated through Pillow Tank.
2. The Original Rainwater Pillow is manufactured for long term water storage usage. The Pillows
are made from first grade materials and all are provided with a certificate of fitness upon
request. The Material is a reinforced polymer alloy (polyester scrim coated on both sides with a
PVC polymer). The same heavy duty industrial strength fabric commonly used by the military
and fire departments.
3. Ultra violet radiation inhibitors are incorporated in the manufacturing process of the polymers
to provide excellent ultra violet radiation resistance.
4. Fabric weight 6.5 oz sq yard. Total weight 30 oz sq yard
5. Its abrasion resistance is > 2,000 cycles. This means that an independent ASTM lab has
determined that every square inch of the Original Rainwater Pillow can withstand friction more
than 2,000 times before it begins to abrade. The breaking strength of our material is 550 lbs per
inch, which means a one-inch strip of it can hold 550 lbs. Tear 80 lbs. Adhesion 35 lbs/inch.
6. Seams are radio frequency welded, which means that we use electromagnetic energy to heat
and bond materials together under pressure, ensuring strong, leak-proof seams. Each pillow is
pressure tested before shipping. It is severe-weather tolerant, able to sustain extreme
temperatures, ranging from -30 to +160 Fahrenheit. Easily repairable with heat or cold bonding.
7. The Original Rainwater Pillow is exceedingly durable and shows excellent resistance to ruptures,
abrasions and leaks. It has also been shown to be impervious to rodents in 30 years of
experience using these pillows in crawlspaces, under decks, in yards and a wide variety of other
spaces that rodents tend to like, our manufacturer has never seen any rodent damage.
2.03 THERMAL MASS FILL HOSE
A. Abbott All Weather Water Suction Hose.
1. For use in filling up Thermal Mass Pillow Tank with needed water (1000 Gallons).
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PLUMBING FIXTURES 22 40 00 - 34
2. All weather low temperature suction and discharge hose. Lightweight and flexible. Ideal for
septic handling, construction, waste removal and industrial fluid handling.
3. Made from 100% EPDM tube reinforced with a green polyethylene helix. Abrasion resistant
cover.
PART 3 – EXECUTION
3.01 INSTALLATION
A. Pillow Tank should be placed on flat area that will be able to drain system. Supports can be used but
are not needed as the Pillow is naturally very strong. When connecting pumps and piping be sure to
make strong connections and use a leak guard.
B. Thermal Mass Fill Hose to be used to fill up Thermal Mass Pillow Tank with water. The hose will be
temporarily connected to Potable-Water Storage Tank while it is being filled, and Thermal Mass will
be filled concurrently. Once filling of Pillow Tank is complete, hose with be shut off and
disconnected from Potable-Water Storage Tank and then this will be topped off.
C. For Installation of Phase Change Material, see Section 23 71 13.26.
3.02 TESTING
A. Testing of the Thermal Mass Pillow Tank with installed Phase Change Material shall be done prior to
installation of the system to check performance of Thermal Mass.
END OF SECTION
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SECTION 23 71 13.26
PHASE CHANGE MATERIAL FOR THERMAL MASS
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Phase Change Material for Thermal Mass.
B. Related Requirements
1. Thermal Mass-Loop Heat-Pump Piping (Section 23 21 13.43).
2. In-Line Centrifugal Hydronic Pumps (Section 23 21 23.13).
3. Water-Source Unitary Heat Pumps (Section 23 81 46).
4. Pressurized-Water Thermal Storage Tanks (23 71 13.23).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. ASHRAE – American Society of Heating, Refrigerating and Air-Conditioning Engineers.
3. UL – Underwriters Laboratories Inc.
4. ASTM – American Society for Testing and Materials.
5. MSDS – Material Safety Data Sheets.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for Phase Change Material for Thermal Mass.
2. MSDS for Phase Change Material to be submitted as well.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. Compliance with IRC, ASTM, and ASHRAE standards.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. PCM Products Ltd. (or other manufacturer with similar product meeting all codes and
requirements). (www.pcmproducts.net/home.htm)
2.02 PHASE CHANGE MATERIAL FOR THERMAL MASS
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A. TubeICE® containers of PCM products.
1. For use in Thermal Mass Pillow Tank to provide a temperature range that the Thermal Mass will
stay within. This will increase productivity of Heat-Pump unit while replicating a Geothermal
Heat-Pump application.
2. These containers operate on a similar principle to the FlatICE® containers, and are supplied as
fully sealed PCM-filled HDPE tubes. The tubular design enables them to be stacked effectively in
both rectangular and cylindrical tanks with minimal void space. Once installed, a series of ridges
around the circumference of the tube mean that air or water can pass freely between the
containers allowing excellent heat exchange properties.
3. TubeICE® set at an upper and lower Phase Change Temperature shall be used to keep Thermal
Mass at most efficient operating temperatures as possible to reduce needed cooling or heating
energy from Heat-Pump unit. Approximately 300 gallons of PCM shall be used, which is about
450 TubeICE® units.
PART 3 – EXECUTION
3.01 INSTALLATION
A. TubeICE® shall be inserted into Pillow Tank prior to filling the rest of the tank with water. Once all
TubeICE® is installed the Pillow Tank can then be attached to Thermal Mass Fill Hose and filled with
approximately 1000 gallons of water.
3.02 TESTING
A. Testing of the Thermal Mass Pillow Tank with installed Phase Change Material shall be done prior to
installation of the system to check performance of Thermal Mass.
END OF SECTION
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SECTION 23 81 46
WATER-SOURCE UNITARY HEAT PUMPS
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Water-Source Heat Pump.
B. Related Requirements
1. In-Line Centrifugal Hydronic Pumps (Section 23 21 23.13).
2. HVAC Air Distribution (Section 23 30 00).
3. Direct-Digital Control System for HVAC (Section 23 09 23).
4. Thermal Mass-Loop Heat-Pump Piping (Section 23 21 13.43).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. ASHRAE – American Society of Heating, Refrigerating and Air-Conditioning Engineers.
3. UL – Underwriters Laboratories Inc.
4. AHRI – Air-Conditioning, Heating and Refrigeration Institute.
5. ISO – International Standards Organization.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for Water-Source Heat Pump.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. AHRI certification.
3. Compliance with IRC and ASHRAE standards.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Johnson Controls® (or other manufacturer with similar product meeting all codes and
requirements). (www.johnsoncontrols.com)
2.02 Water-Source Heat Pump
A. Johnson Controls® RJ Series Geothermal/Water Source Heat Pump RJS-H015-ER.
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1. For use with HVAC System to provide heating and cooling to conditioned space inside house, by
means of Thermal Mass acting as Geothermal source.
2. Equipment shall be completely assembled, piped and internally wired. Capacities and
characteristics as listed in the schedule and the specifications that follow. The reverse cycle
heating/cooling units shall be either suspended type with horizontal air inlet and discharge or
floor mounted type with horizontal air inlet and vertical upflow/down flow or rear air discharge.
Units shall be AHRI/ISO 13256-1 certified and listed by a nationally recognized safety-testing
laboratory or agency, such as ETL Testing Laboratory. Each unit shall be computer run tested at
the factory with conditioned water and operation verified to catalog data. Each unit shall be
mounted on a pallet and shipped in a corrugated box or stretch-wrapped. The units shall be
designed to operate with entering liquid temperature between 20°F and 120°F [-6.7°C and
48.9°C].
3. Refrigerant Circuit: All units shall utilize the non-ozone depleting and low global warming
potential refrigerant R410A. All units shall contain a sealed refrigerant circuit including a
hermetic motor-compressor, bidirectional thermostatic expansion valve, finned tube air-to
refrigerant heat exchanger, reversing valve, coaxial tube water-to refrigerant heat exchanger,
optional hot water generator coil, and service ports. Compressors shall be high-efficiency single
speed rotary or scroll, or dual capacity scroll type designed for heat pump duty and mounted on
vibration isolators. The compressor shall be double isolation mounted using selected durometer
grommets to provide vibration free compressor mounting. The compressor mounting bracket
shall be acoustically deadened galvanized steel to prevent vibration transmission to the cabinet.
Compressor motors shall be three-phase or single-phase PSC with overload protection. The air
coil shall be sized for low face velocity and constructed of lanced aluminum fins bonded to rifled
copper tubes in a staggered pattern not less than three rows deep for enhanced performance.
4. Blower Motor and Assembly: The blower shall be a direct drive centrifugal type with a
dynamically balanced wheel. The housing and wheel shall be designed for quiet low outlet
velocity operation. The blower housing shall be removable from the unit without disconnecting
the supply air ductwork for servicing of the blower motor. The blower motor shall be a variable-
speed ECM2 type. The ECM2 blower motor shall be soft starting, shall maintain constant CFM
over its operating static range, and shall provide 12 CFM settings. The blower motor shall be
isolated from the housing by rubber grommets. The motor shall be permanently lubricated and
have thermostatic overload protection. ECM2 motors shall be long-life ball bearing type.
PART 3 – EXECUTION
3.01 INSTALLATION
A. To be installed and tested to Manufacturers requirements and IRC and ASHRAE standards.
B. Unit Location: Locate the unit in an indoor area that allows for easy removal of the filter and access
panels. Location should have enough space for service personnel to perform maintenance or repair.
Provide sufficient room to make water, electrical and duct connection(s). If the unit is located in a
confined space, such as a closet, provisions must be made for return air to freely enter the space by
means of a louvered door, etc. Any access panel screws that would be difficult to remove after the
unit is installed should be removed prior to setting the unit. On horizontal units, allow adequate
room below the unit for a condensate drain trap and do not locate the unit above supply piping.
Care should be taken when units are located in unconditioned spaces to prevent damage from
frozen water lines and excessive heat that could damage electrical components.
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PLUMBING FIXTURES 22 40 00 - 39
C. Condensate Drain: On vertical units, the internal condensate drain assembly consists of a drain tube
which is connected to the drain pan, a 3/4 in. or 1 in. copper female adapter and a flexible
connecting hose. On vertical units, a condensate hose is inside all cabinets as a trapping loop;
therefore, an external trap is not necessary. On horizontal units, a PVC stub is provided for
condensate drain piping connection. An external trap is required (see below). If a vent is necessary,
an open stand pipe may be applied to a tee in the field-installed condensate piping. In order to work
properly, the vent must be after the trap and away from the unit.
D. Sound Performance: The RJ Series is third party sound rated in accordance with AHRI 260.
1. Recommendations for Noise Reduction for Horizontal Unit Location:
a. Specify equipment with quietest sound power ratings
b. Do not locate units above areas with a required NC 40 or less
c. Space WSHP at least 10 ft (3m) apart to avoid noise summing of multiple units in a space.
d. Maximize the height of the unit above the ceiling (horizontal).
e. Suspend unit with isolation grommets that are appropriately rated to reduce vibrations
(horizontal).
3.02 TESTING
A. The system shall follow performance standard AHRI/ASHRAE/ISO 13256-1. After performing testing
values can be compared to performance data found in Engineering Guide.
END OF SECTION
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SECTION 23 84 16
DEHUMIDIFIERS
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Dehumidifier.
A. Related Requirements
1. HVAC Air Distribution (Section 23 30 00).
2. Direct-Digital Control System for HVAC (Section 23 09 23).
3. Water-Source Unitary Heat Pumps (Section 23 81 46).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. ASHRAE – American Society of Heating, Refrigerating and Air-Conditioning Engineers.
3. UL – Underwriters Laboratories Inc.
4. AHRI – Air-Conditioning, Heating and Refrigeration Institute.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for Dehumidifier.
1.04 QUALITY ASSURANCE
A. Certificates
1. UL certification.
2. AHRI certification.
3. Compliance with IRC and ASHRAE standards.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. Therma-Stor® LLC. (or other manufacturer with similar product meeting all codes and
requirements). (www.thermastor.com).
2.02 DEHUMIDIFIER
A. Ultra-AireTM
65H Ventilating Dehumidifier.
1. For use in parallel with HVAC Air Distribution System in order to dehumidifier conditioned air
further, or to dehumidify while Heat Pump is not running.
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2. The Ultra-AireTM
65H uses a refrigeration system similar to an air conditioner’s to remove heat
and moisture from incoming air, and add heat to the air that is discharged. Hot, high pressure
refrigerant gas is routed from the compressor to the condenser coil. The refrigerant is cooled
and condensed by giving up its heat to the air that is about to be discharged from the unit. The
refrigerant liquid then passes through a strainer and capillary tubing which causes the
refrigerant pressure and temperature to drop. It next enters the evaporator coil where it
absorbs heat from the incoming air and evaporates. The evaporator operates in a flooded
condition, which means that all the evaporator tubes contain liquid refrigerant during normal
operation. A flooded evaporator should maintain nearly constant pressure and temperature
across the entire coil, from inlet to outlet. The mixture of gas and liquid refrigerant enter the
accumulator after leaving the evaporator coil. The accumulator prevents any liquid refrigerant
from reaching the compressor. The compressor evacuates the cool refrigerant gas from the
accumulator and compresses it to a high pressure and temperature.
3. Refrigerant Charging: If the refrigerant charge is lost due to service or a leak, a new charge must
be accurately weighed in. If any of the old charge is left in the system, it must be recovered
before weighing in the new charge. Refer to the unit nameplate for the correct charge weight
and refrigerant type.
4. Compressor/Capacitor Replacement: This compressor is equipped with a two terminal external
overload and a run capacitor, but no start capacitor or relay.
5. Electric Ventilation Damper: The damper will open when the ventilation is called for, allowing
fresh air into the structure through the fresh air inlet duct. The electric ventilation damper will
remain closed when the ventilation is not activated in order to prevent over-ventilating the
structure when the unit is dehumidifying or recirculating the indoor air. The electric ventilation
damper operates on 24 Vac from the control circuit. DO NOT connect high voltage to the
damper motor or damage to the motor will result. DO NOT force the blade of the damper by
hand or damage to the damper motor may result. The damper opens in one direction only. The
damper rotates very slowly, allow sufficient time for the damper to cycle. The damper will take
approximately one minute to cycle from closed to open or from open to closed.
PART 3 – EXECUTION
3.01 INSTALLATION
A. Prior to installation of the Ultra-AireTM
65H, the following checklist should be reviewed. The Ultra-
AireTM
65H can be installed in a variety of locations to meet the owner’s needs, and be integrated
with existing forced air systems or existing ductwork if desired. The location choice is contingent on
a variety of requirements not limited to: ease of service, controls access, drainage, filtration, power,
fresh-air ventilation (optional), water damage prevention, and current regulatory codes (ASHRAE,
fire, etc). Please address all of these issues before you select the location of the device.
B. Power Accessibility: Unit should be located in an area where the cord’s length (8') should easily
reach a 110-120 VAC electrical outlet with a minimum of a 15 A circuit capacity.
C. Space: Location should have enough clearance to handle the unit’s overall dimensions as well as the
necessary return/supply ductwork to the unit.
D. Support Structure and Suspension: Place the Ultra-AireTM
65H on supports to raise the base of the
unit. Do not place the Ultra-AireTM
65H directly on structural building members without vibration
absorbers or unwanted noise may result. The Ultra-AireTM
65H may be suspended with a hang kit
(4028111) or a suitable alternative from structural members, as long as the suspending assembly
supports the Ultra-AireTM
65H’s base in its entirety. Do not hang the Ultra-AireTM
65H from the
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PLUMBING FIXTURES 22 40 00 - 42
cabinet. Remember to place a drain pan under the unit if it is suspended above a finished area or
above an area where water leakage could cause damage.
E. Electrical Requirements: The Ultra-AireTM
65H plugs into a common grounded 115VAC outlet. The
device draws 5.5 Amps under normal operating conditions. If used in an area which may become
wet, a ground fault interrupter (GFI) protected circuit is recommended. Please, consult local
electrical codes for any further information. Therma-Stor® LLC offers a family of control devices for
use with the Ultra-AireTM
65H. The controls are to be located remotely from the unit and located in
the space to be conditioned. The controls are low voltage (24 volt) and should be connected to the
Ultra-AireTM
65H with low voltage wire (thermostat or other appropriate).
F. Supply Air: A short piece of flexible ducting on all Ultra-AireTM
65H duct connections is
recommended to reduce noise and vibration transmitted to rigid ductwork in the structure. Ducting
the Ultra-AireTM
65H as mentioned requires consideration of the following points. Duct Sizing: For
total duct lengths up to 25', use a minimum 8" diameter round or equivalent rectangular. For longer
lengths, use a minimum 10" diameter or equivalent. Grills or diffusers on the duct ends must not
excessively restrict airflow. Connecting to existing HVAC systems: An optional 8" check backdraft
damper is available from the factory to prevent reverse air flow through the Ultra-AireTM
65H. If the
Ultra-AireTM
65H is ducted to the supply of an air handler, the check damper should be placed in the
Ultra-AireTM
65H supply duct.
G. Noise Abatement: A length of 10 feet or more of flex ducting on the outlet of the Ultra-AireTM
65H
will reduce air noise from the fan. A length of flexible ducting on all Ultra-AireTM
65H duct
connections is recommended to reduce noise transmitted to rigid ductwork in the structure.
3.02 TESTING
A. The system should be tested to check performance standards and checked with data from
Installation Guide. Troubleshooting section can be used in the case of problems, any further issues
can be taken up with technical support.
3.03 MAINTENANCE
A. High Efficiency Air Filter: The Ultra-Aire 65H is equipped with a MERV 11 media filter. This filter
should be checked every three months. Operating the unit with a dirty filter will reduce
dehumidifier capacity and efficiency and may cause the compressor to cycle off and on
unnecessarily on the defrost control. DO NOT operate the unit without a filter or with a less
effective filter. Operating the unit without a filter or with a less effective filter may cause internal
damage to the unit and invalidate the product warranty.
END OF SECTION
END OF DIVISION 23
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DIVISION 28: ELECTRONIC SAFETY AND SECURITY
SECTION 28 31 46
SMOKE DETECTION SENSORS
PART 1 – GENERAL
1.01 SUMMARY
A. Section Includes
1. Smoke Alarms.
A. Related Requirements
1. Fire-Suppression Sprinkler Systems (Section 21 13 00).
2. Electric-Drive, Centrifugal Fire Pumps (Section 21 31 13).
3. Ground Suction Storage Tanks for Fire-Suppression Water (Section 21 41 23).
1.02 REFERENCES
A. Reference Standards
1. IRC – International Residential Code.
2. NFPA – National Fire Protection Association.
3. UL – Underwriters Laboratories Inc.
1.03 SUBMITTALS
A. Product Data
1. Submit product sheets and specifications for Smoke Alarms.
1.04 QUALITY ASSURANCE
B. Certificates
1. UL certification of Jockey Pump Controller.
2. Compliance with IRC Section P2904 or NFPA 13D.
PART 2 – PRODUCTS
2.01 MANUFACTURERS
A. First Alert® (or other manufacturer with similar product meeting all codes and
requirements) (www.firstalert.com).
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2.02 SMOKE ALARMS
A. (2 ct) First Alert® SA-9120-BCN Hardwired Smoke Alarm with Battery (9V) Backup .
1. For use in house to detect smoke and warn those inside of fire and/or smoke.
PART 3 – EXECUTION
3.01 INSTALLATION
A. To be installed and tested to Manufacturer’s requirements and IRC Fire code.
END OF SECTION
APPENDIX C: TEAM HAWAII FULL DRAWING SET
LOT NUMBER:
COPYRIGHT:
CLIENT
U.S. DEPARTMENT OF ENERGY / NREL2011 SOLAR DECATHLON
WWW.SOLARDECATHLON.GOV
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
TEAM NAME:
ADDRESS:
CONTACT:
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
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ADDRESS:
CONTACT:
ARCHITECTURE:
CONSULTANTS
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UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
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WWW.SOLARDECATHLON.GOV
TEAM NAME:
ADDRESS:
CONTACT:
ARCHITECTURE:
CONSULTANTS
ENGINEERS:
LANDSCAPING:
CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
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E-103 LIGHTING DETAILSE-104 PV ROOF PLANE-106 RAMP LIGHTING PLANE-201 ELECTRICAL EQUIPMENT ELEVATIONSE-601 PV ONE-LINE DIAGRAME-603 THREE-LINE DIAGRAME-604 PANEL SCHEDULESE-605 ELECTRICAL SCHEDULES
T-001 TELECOMMUNICATIONS SYMBOLS AND NOTEST-101 TELECOMMUNICATIONS WIRING PLANT-602 DATA WIRING DIAGRAM
O-100 ARRIVAL STAGING PLANO-101 ARRIVAL SHELL ASSEMBLY SEQUENCE PLANSO-102 SUPERSTRUCTURE ASSEMBLY SEQUENCE PLANO-103 RAMP ASSEMBLY SEQUENCE PLANO-201 WATER DELIVERY AND REMOVAL PLANO-602 TRUCK LOADING DIAGRAM
SHEET LISTSHT NO SHEET NAME
A-101 SITE PLANA-110 FIRST FLOOR PLANA-111 RAMP DECK PLANA-112 ROOF PLANA-121 FIRST FLOOR REFLECTED CEILING PLANA-211 ELEVATIONSA-212 ELEVATIONSA-213 INTERIOR ELEVATIONSA-301 BUILDING SECTIONSA-302 BUILDING SECTIONSA-313 WALL SECTIONS AT WEST AND EAST ENDA-314 WALL PLAN AT WEST AND EAST ENDA-320 FLOOR SECTIONS AND DETAILSA-321 FLOOR SECTIONS AND DETAILSA-322 ROOF SECTIONSA-401 LARGE SCALE PLANSA-501 PLAN DETAILSA-511 SECTION DETAILSA-531 WINDOW AND DOOR DETAILSA-541 WINDOW AND DOOR DETAILSA-561 ROOF DETAILSA-701 TYPICAL DETAILS
F-001 FIRE PROTECTION NOTES AND SYMBOLSF-101 FIRE DETECTION AND ALARM PLANF-102 FIRE SUPPRESSION PLANF-601 FIRE PROTECTION SCHEDULESF-602 FIRE PROTECTION DIAGRAMSF-603 FIRE SPRINKLER DETAILF-901 FIRE SUPPRESSION ISOMETRICS
P-001 PLUMBING SYMBOLS AND NOTESP-101 PLUMBING SITE PLANP-102 DOMESTIC SUPPLY PLANP-103 DOMESTIC SANITARY RETURN PLANP-601 PLUMBING SCHEDULESP-602 PLUMBING DIAGRAMSP-901 DOMESTIC SUPPLY ISOMETRICSP-902 SANITARY WASTE AND VENT ISOMETRICS
M-001 MECHANICAL SYMBOLS AND NOTESM-101 HVAC EQUIPMENT AND DISTRIBUTION PLANM-102 SPILL CONTAINMENT PLANM-103 CONTAINER LOCATIONS PLANM-104 MECHANICAL GROUND CONTACT PLANM-201 MECHANICAL ELEVATIONSM-601 MECHANICAL SCHEDULESM-602 HVAC DIAGRAMSM-603 SOLAR WATER DIAGRAMSM-901 HVAC ISOMETRICSM-902 SOLAR WATER ISOMETRICS
E-001 ELECTRICAL SYMBOLS AND NOTESE-101 ELECTRICAL DISTRIBUTION PLANE-102 LIGHTING PLAN
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G-000 COVER SHEETG-001 TABLE OF CONTENTSG-101 FINISHED SQUARE FOOTAGE COMPLIANCE PLANG-102 EGRESS PLANG-103 ADA TOUR ROUTE COMPLIANCE PLANG-201 SOLAR ENVELOPE COMPLIANCE ELEVATIONSG-202 SOLAR ENVELOPE COMPLIANCE ELEVATIONSG-602 EXTERIOR SHADING STUDIES
C-100 SITE LOCATION MAPC-101 GROUND CONTACT PLANC-104 SITE ELEVATIONSC-105 SITE ELEVATIONS
L-001 LANDSCAPE NOTES AND SYMBOLSL-101 LANDSCAPE SITE PLANL-102 LANDSCAPE IRRIGATION PLANL-201 LANDSCAPE ELEVATIONSL-601 LANDSCAPING DETAILSL-602 LANDSCAPING PLUMBING DIAGRAM
S-001 STRUCTURAL NOTES AND SYMBOLSS-100 FOUNDATION PLANS-101 FOUNDATION ELEVATIONS-102 FIRST FLOOR FRAMING PLANS-103 ROOF FRAMING PLANS-104 DECK FRAMING PLANS-105 RAMP DECK ELEVATIONSS-201 FRAMING ELEVATIONSS-301 FRAMING SECTIONSS-500 ENLARGE STRUCTURAL PLANS-501 ENLARGE STRUCTURAL SECTIONS-511 SECTION DETAILSS-521 RAMP AND DECK DETAILSS-522 RAMP AND DECK DETAILSS-523 RAMP AND DECK DETAILSS-524 RAMP AND DECK DETAILSS-525 RAMP AND DECK DETAILSS-526 RAMP AND DECK DETAILSS-527 RAMP AND DECK DETAILSS-535 FOUNDATION DETAILSS-536 FOUNDATION DETAILSS-537 FOUNDATION DETAILSS-538 FOUNDATION DETAILSS-539 FOUNDATION DETAILSS-540 FOUNDATION DETAILSS-541 FOUNDATION DETAILSS-542 FOUNDATION DETAILSS-543 FOUNDATION DETAILSS-544 FOUNDATION DETAILSS-550 SHELL FRAMING DETAILSS-645 SUPERSTRUCTURE DETAILSS-646 SUPERSTRUCTURE DETAILSS-801 TYPICAL DETAILSS-901 FRAMING ISOMETRICSS-903 MODULE DIAGRAM
MARK DATE DESCRIPTIONMARK DATE DESCRIPTION
FIRE PROTECTION NOTES1. THE FIRE SUPPRESSION SYSTEM WAS DESIGNED ACCORDING TO
INTERNATIONAL RESIDENTIAL CODE STANDARDS.2. THE SLOPE OF CEILING IS GREATER THAN 1/3 BUT LESS THAN 2/3.
FROM THE SPRINKLER SPECIFICATION SHEET, THE SINGLESPRINKLER’S MAXIMUM COVERAGE AREA IS SELECTED TO 18” X 18”,AND THEN THE MINIMUM FLOW RATE IS 19GPM AND MINIMUMPRESSURE IS 15PSI. ACCORDING TO IRC2009 SECTION P2904.4.2,TWO SPRINKLERS RUN SIMULTANEOUSLY FOR 7 MINUTES, AND THENTHE MINIMUM WATER CONSUMPTION IS 266 GALLONS. APPROXIMATELY280 GALLONS OF WATER WILL BE DEVOTED TO THIS FIRESUPPRESSION SYSTEM AND WILL BE STORED IN A 300 GALLON TANKIN THE UNDER PORCH AREA.
3. THE PRESSURE NEEDED FOR FIRE SUPPRESSION WILL BE PROVIDEDBY A 3 HP CENTRIFUGAL PUMP. THIS PUMP WAS SIZED AFTERPERFORMING A FLOW PRESSURE SIMULATION BY THERMALENGINEERING CORPORATION.
4. THE FIRE SPRINKLER LINES ARE PEX PIPING RATED FOR FIRESUPPRESSION SYSTEMS. THESE PIPES ARE FLEXIBLE ARE ABLE TOBE ROUTED THROUGH THE SHELL STRUCTURE OF THE HOUSE. THEYWILL PENETRATE THE SHELL IN THE UNDERFLOOR AREA. EXCESSPEX PIPING WILL BE FITTED INTO THE SHELL STRUCTURE TOACCOMMODATE FOR MULTIPLE CONNECTIONS AND DISCONNECTIONSFOR OFF-SITE ASSEMBLY AND DISASSEMBLY.
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
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UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
15:0
6 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
F-001
FIRE PROTECTIONNOTES AND SYMBOLS
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
DESCRIPTIONABBRV.SYMBOL
BREAK LINE
FIRE PROTECTION LEGEND
CHECK VALVE
SPRINKLER HEAD - PENDANT
SMOKE DETECTOR
CV
FLOW DIRECTION ARROW
PUMP
GATE VALVE
UNION
SD
SHP
GV
P
U
SD
MARK DATE DESCRIPTION
DV DRAIN VALVE
SD
SD
28 31 46
28 31 46
21 24 16
21 24 16
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
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UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
15:0
9 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
F-101
FIRE DETECTION ANDALARM PLAN
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
3/8" = 1'-0"A1 FIRE DETECTION AND ALARM PLAN0 4' 6'2'
REFERENCE KEYNOTES21 24 16 DRY-CHEMICAL FIRE-EXTINGUISHER
EQUIPMENT28 31 46 SMOKE DETECTION SENSORS
SHEET KEYNOTES
GENERAL SHEET NOTES
21 41 23
21 31 13
21 13 00
14
15
D1F-603
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
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UNIVERSITY OF HAWAI'I
5/3/
2011
10:
15:1
3 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
F-102
FIRE SUPPRESSIONPLAN
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
REFERENCE KEYNOTES21 13 00 FIRE-SUPPRESSION SPRINKLER SYSTEMS21 31 13 ELECTRIC-DRIVE, CENTRIFUGAL FIRE
PUMPS21 41 23 GROUND SUCTION STORAGE TANKS FOR
FIRE-SUPPRESSION WATER
SHEET KEYNOTES14 DUAL CONNECTION CONCEALED SPRINKLER
HEAD15 SINGLE CONNECTION CONCEALED
SPRINKLER HEAD
GENERAL SHEET NOTES
MARK DATE DESCRIPTION
3/8" = 1'-0"A1 FIRE SUPPRESSION PLAN0 4' 6'2'
FIRE PROTECTION EQUIPMENT SCHEDULE
DESCRIPTION MANUFACTURER
V PHHZ
MODEL
GRUNDFOS CR 5-8
MAX FLOW RATE
GPM
POWER
HP
CURRENTAMPS
RATED VOLTAGE
16012019.03FIRE WATER PUMP
DIMENSIONSINCH
33 H X 8-5/8 D
TYCO LFII TY2234FIRE SPRINKLER HEADS(6 CT) 13 [EA] __ ______ 3-5/16 D
[3/4 CONNECTION]__
FIRE PROTECTION PIPING SCHEDULE
DESCRIPTION MATERIAL LENGTH
PEX PIPE NONEFIRE SUPPRESSION SHELLBRANCH SUPPLIES
FIRE SUPPRESSION MAIN LINE AND PUMP CONNECTION
~60 FEET
~50 FEET
INSULATION
45
SIZEDIAMETER INCH
1
1-1/4
FIRE PROTECTION FITTING SCHEDULE
FAMILY MATERIAL COUNT
EPFIRE SUPPRESSION SUPPLY
EP
4
4
COPPERTYPE K
6
CONNECTION SIZESDIAMETER INCH
1-1/4 X 1 X 3/4
1-1/4 X 1-1/4
TYPE
REDUCINGTEE
COUPLING
ELBOW
EP
TEE
ELBOW
EP
1-1/4 X 1-1/4
1 X 3/4
1-1/4 X 1-1/4 X 1-1/4
2
1
FIRST ALERT FE3A40GRFIRE EXTINGUISHER __ __ ______ 4.6 D x 16.0 H__
COPPER TYPE K
FIRE PROTECTION VALVE SCHEDULE
FAMILY TYPE COUNT
CHECK VALVEFIRE SUPPRESSION SUPPLY
GATE VALVEFIRE SUPPRESSION SUPPLY
1
2
CONNECTION SIZEDIAMETER INCH
1-1/4
1-1/4
FIRE PROTECTION TANK SCHEDULE
DESCRIPTION MATERIAL VOLUMEGALLONS
MEDIUM-DENSITYPOLYETHYLENE
FIRE SUPPRESSIONWATER STORAGE TANK 300
DIMENSIONS INCH
40 W X 58 L X 29 H
NONE
FIRE SUPPRESSIONPUMP CONNECTION
FIRE SUPPRESSION SUPPLY
FIRE SUPPRESSION SUPPLY
FIRE SUPPRESSION SUPPLY
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
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UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
15:1
5 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
F-601
FIRE PROTECTIONSCHEDULES
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
21 41 23
21 31 13
14
15
22
23
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
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UNIVERSITY OF HAWAI'I
5/3/
2011
10:
15:1
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UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
F-602
FIRE PROTECTIONDIAGRAMS
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
REFERENCE KEYNOTES21 31 13 ELECTRIC-DRIVE, CENTRIFUGAL FIRE
PUMPS21 41 23 GROUND SUCTION STORAGE TANKS FOR
FIRE-SUPPRESSION WATER
SHEET KEYNOTES14 DUAL CONNECTION CONCEALED SPRINKLER
HEAD15 SINGLE CONNECTION CONCEALED
SPRINKLER HEAD22 DIAPHRAGM PRESSURE TANK23 SENSOR WIRE FOR PUMP TO DIAPHRAGM
TANK
GENERAL SHEET NOTES
NTSA1 FIRE SUPPRESSION DIAGRAM
MARK DATE DESCRIPTION
FIRST FLOOR4'-5"
F-603A1
F-603A4
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
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UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
15:2
3 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
F-603
FIRE SPRINKLERDETAIL
306
Checker
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
1/2" = 1'-0"D1 FIRE SPRINKLER SECTION DETAIL
3" = 1'-0"A1 SINGLE CONNECTION FIRE SPRINKLER DETAIL 3" = 1'-0"A4 DUAL CONNECTION FIRE SPRINKLER DETAIL
REFERENCE KEYNOTES
SHEET KEYNOTES
GENERAL SHEET NOTES1. THE PLACEMENT AND FLOW RATES OF THE
FIRE SPRINKLER HEADS WERE DETERMINEDBASED ON THE SPECIFICATIONS FROM TYCO.
2. FOR SLOPED CEILING GREATER THAN 4-INCHRISE UP TO MAXIMUM 8-INCH RISE FOR 12-INCHRUN.
3. THESE HEADS ARE CAPABLE OF MAXIMUMCOVERAGE AREA OF 18 X 18 (FEET), WITH A 19GPM MINIMUM FLOW RATE.
0 6" 1'3" 0 6" 1'3"
0 1' 2' 4'
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
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UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
15:3
8 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
F-901
FIRE SUPPRESSIONISOMETRICS
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
A1 FIRE SUPPRESSION ISOMETRIC0 4' 6'2'
DESCRIPTIONABBRV.SYMBOL
CLEANOUT
AAV
CHECK VALVE
TRAP
PLUMBING LEGEND
FIXTURE CONNECTION
FLOOR DRAIN
FIXTURE DRAIN
BV
FLOOR PENETRATION
PUMP
GATE VALVE
AIR ADMITTANCE VALVE
BALL VALVE
SHOWER
VENT ROOF
CV
CO
FXC
FXD
FLD
FLP
GV
P
SHR
TRP
VTR
PLUMBING NOTES1. PLUMBING SYSTEMS WERE DESIGNED FOLLOWING INTERNATIONAL
RESIDENTIAL CODE, INTERNATIONAL PLUMBING CODE, AND UNIFORMPLUMBING CODE.
2. DOMESTIC HOT AND COLD WATER LINES WILL BE PEX PIPING IN ORDERTO ALLOW FOR EASE OF INSTALLATION. HORIZONTAL PEX PIPES WILL BESUPPORTED FOR EVERY 2.5 FT, COMPLYING TO 2.67 FT REQUIREMENTFROM IRC2009 TABLE P2605.1 - PIPING SUPPORT. HOT WATER SUPPLYLINE WILL BE USED INSULATED PEX PIPE TO MINIMIZE THE HEAT LOSS.PRESSURE FOR THE DOMESTIC WATER SUPPLY WILL BE PROVIDED BY A1 HP CENTRIFUGAL PUMP, AND WILL BE CONNECTED TO THE 500 GALLONFRESH WATER TANK.
3. SANITARY WASTE AND VENT LINES WILL BE PVC PIPING. THE FIXTURESANITARY DRAINS ARE GREATER OR EQUAL THAN 1-1/4” TO COMPLY WITHIRC2009 P2703.1, AND WILL DRAIN INTO 2" BRANCH LINES LEADING TO THEMAIN 2" RETURN LINE TO SANITARY WASTE TANK. THE CLOTHES WASHINGMACHINE WILL DRAIN INTO AN 18 INCH HIGH STAND PIPE TO COMPLY WITHIRC2009 P2706.2 - STANDPIPES. THE CLOTHES WASHING MACHINEDISCHARGE WILL BE THROUGH AN AIR BREAK TO COMPLY WITH IRC2009P2718.1 - WASTE CONNECTION. THE DRAINAGE FIXTURE UNIT VALUE(D.F.U.) IN OUR HOUSE IS 7, AND ACCORDING TO UNIFORM PLUMBINGCODE, 2 INCH GRAY WATER PIPES CAN BE USED. AIR ADMITTANCEVALVES ARE USED FOR LOW FLOW RATE FIXTURES (LESS THAN 18GPM),AND COMPLY WITH IRC2009 SECTION P3114.
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
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UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
50:0
2 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
P-001
PLUMBING SYMBOLSAND NOTES
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
22 13 53
22 12 19
22 11 23.26
22 35 23.16
22 33 30.23
22 11 16
22 13 16
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
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UNIVERSITY OF HAWAI'I
5/3/
2011
10:
50:0
6 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
P-101
PLUMBING SITE PLAN
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
3/8" = 1'-0"A1 PLUMBING SITE PLAN
REFERENCE KEYNOTES22 11 16 DOMESTIC WATER PIPING22 11 23.26 CLOSE-COUPLED, HORIZONTALLY
MOUNTED, IN-LINE CENTRIFUGALDOMESTIC-WATER PUMPS
22 12 19 FACILITY GROUND-MOUNTED, POTABLEWATER STORAGE TANKS
22 13 16 SANITARY WASTE AND VENT PIPING22 13 53 FACILITY SEPTIC TANKS22 33 30.23 RESIDENTIAL, COLLECTOR-TO-TANK,
SOLAR-ELECTRIC DOMESTIC WATERHEATERS
22 35 23.16 CIRCULATING, STORAGE DOMESTIC WATERHEAT EXCHANGERS
SHEET KEYNOTES
GENERAL SHEET NOTES
0 4' 6'2'
1. WC WILL NOT BE CONNECTED TO WATER SUPPLYAND SANITARY LINES DURING COMPETITION.
22 12 19
22 11 23.26
22 11 16
22 33 30.23
16
17
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
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UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
50:1
1 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
P-102
DOMESTIC SUPPLYPLAN
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
3/8" = 1'-0"A1 DOMESTIC SUPPLY PLAN
REFERENCE KEYNOTES22 11 16 DOMESTIC WATER PIPING22 11 23.26 CLOSE-COUPLED, HORIZONTALLY
MOUNTED, IN-LINE CENTRIFUGALDOMESTIC-WATER PUMPS
22 12 19 FACILITY GROUND-MOUNTED, POTABLEWATER STORAGE TANKS
22 33 30.23 RESIDENTIAL, COLLECTOR-TO-TANK,SOLAR-ELECTRIC DOMESTIC WATERHEATERS
SHEET KEYNOTES16 PEX INSULATED HOT WATER LINE17 PEX COLD WATER LINE
GENERAL SHEET NOTES
0 4' 6'2'
1. WC WILL NOT BE CONNECTED TO WATER SUPPLYAND SANITARY LINES DURING COMPETITION.
22 13 53
22 11 16
22 13 19.36
22 13 19.36
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
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UNIVERSITY OF HAWAI'I
5/3/
2011
10:
50:1
5 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
P-103
DOMESTIC SANITARYRETURN PLAN
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
3/8" = 1'-0"A1 SANITARY WASTE AND VENT PLAN
REFERENCE KEYNOTES22 11 16 DOMESTIC WATER PIPING22 13 19.36 AIR-ADMITTANCE VALVES22 13 53 FACILITY SEPTIC TANKS
SHEET KEYNOTES
GENERAL SHEET NOTES
0 4' 6'2'
1. WC WILL NOT BE CONNECTED TO WATER SUPPLYAND SANITARY LINES DURING COMPETITION.
PLUMBING EQUIPMENT SCHEDULE
DESCRIPTION MANUFACTURER
V PHHZ
MODEL
GRUNDFOS MQ 3-45
MAX FLOW RATE
GPM
POWER
HP
CURRENTAMPS
RATED VOLTAGE
16012010.01FRESH WATER PUMP
DIMENSIONSINCH
12.74H X 22.44L X 8.58W
GRUNDFOS UP15-18 BUC 7SOLAR RECIRCULATING PUMP 16 1/25 1601200.74
PLUMBING PIPING SCHEDULE
DESCRIPTION MATERIAL LENGTH
PEX PIPE NONEDOMESTIC COLD WATER
PEX PIPEDOMESTIC HOT WATER
~60 FEET
~60 FEET
INSULATION
1 INCH LAYER
19
PVCSANITARY RETURN ~50 FEET NONE
PVCSANITARY VENT ~30 FEET NONE
SIZEDIAMETER INCH
3/4 & 1/2
1-1/2 & 2
1-1/2 & 2
3/4 & 1/2
PLUMBING FITTING SCHEDULE
FAMILY MATERIAL COUNT
EPDOMESTIC WATER
EPDOMESTIC WATER
4
4
PVC
DOMESTIC WATER 6
PVCSANITARY WASTE AND VENT 3
CONNECTION SIZESDIAMETER INCH
3/4 X 3/4 X 1/2
1-1/2 X 1-1/2 X 1-1/2
3/4 & 3/4
TYPE
REDUCINGTEE
COUPLING
ELBOW
TEE
DOMESTIC WATER
PVCSANITARY WASTE AND VENT 52 X 1-1/2 X 2TEE
PVCSANITARY WASTE AND VENT 32CLEANOUT
PVC/CHROMESANITARY WASTE AND VENT 41-1/2P-TRAP
EP
TEE
SANITARY WASTE AND VENT TEE
EP
2 X 2 X 2
3/4 X 1/2
3/4 X 3/4 X 3/4
2
1
BRADFORD WHITE M-1-40L6DS**SOLAR STORAGE TANKW/ BACKUP HEAING __ __ 160240 31-1/4 H X 22 D
[40 GAL]16.0
COPPER TYPE KSOLAR HOT WATER ~25 FEET 1 INCH LAYER1 & 1/2
COPPERSOLAR HOT WATER 31 X 1 X 1/2REDUCINGTEE
COPPERSOLAR HOT WATER 101 X 1COUPLING
COPPERSOLAR HOT WATER 71 X 1/2ELBOW
PLUMBING VALVE SCHEDULE
FAMILY TYPE COUNT
BALL VALVEDOMESTIC COLD WATER
CHECK VALVEDOMESTIC COLD WATER
1
1
GATE VALVEDOMESTIC COLD WATER 2
BALL VALVESOLAR HOT WATER 6
CONNECTION SIZEDIAMETER INCH
3/4
3/4
1 & 1/2
3/4
CHECK VALVESOLAR HOT WATER 21 & 1/2
DRAINSOLAR HOT WATER 21
PRESSURE RELIEFVALVE
SOLAR HOT WATER 11MIXING VALVE
SOLAR HOT WATER 11
TEMPERATURE &PRESSURE RELIEF
VALVESOLAR HOT WATER 21
AIR-ADMITTANCEVALVESANITARY VENT 21-1/2
PLUMBING TANK SCHEDULE
DESCRIPTION MATERIAL VOLUMEGALLONS
MEDIUM-DENSITYPOLYETHYLENE
FRESH WATERSTORAGE TANK
SANITARY WATERSTORAGE TANK
500
500
STEEL CASSINGW/ VITRAGLAS LINING
SOLAR HOT WATERSTORAGE TANK 40
DIMENSIONS INCH
48 W X 92 L X 29 H
MEDIUM-DENSITYPOLYETHYLENE 48 W X 92 L X 29 H
PLUMBING FIXTURES SCHEDULE
DESCRIPTION MANUFACTURER COLOR/FINISH
KOHLERKITCHEN SINK
KITCHEN SINKFAUCET
__
POLISHED CHROME
KITCHEN SINKSTRAINER
MODEL
PURIST KITCHEN FAUCET7507-CP
DUO STRAINER8801-CP
UNDERTONE KITCHEN SINK3331-NA
BATHROOM SINK WHITE
BATHROOM SINKFAUCET
VOX VESSEL LAVATORY14800-0
KOHLER
KOHLER
KOHLER
KOHLER PURIST KITCHEN FAUCET7507-CP
POLISHED CHROME
POLISHED CHROME
KOHLERBATHROOM SINKDRAIN
SHOWER POLISHED CHROME
SHOWER DRAIN
PURIST LOW FLOWHANDSHOWER
978-CP
SHOWER DRAIN9135-CP
LAVATORY DRAIN7124-A-CP
SHOWER VALVE __
WATER CLOSET
STACKED VALVE 680-KS-NA
KOHLER
KOHLER
KOHLER
KOHLER PURIST HATBOX TOILET3492-0
POLISHED CHROME
WHITE
POLISHED CHROME
DELTA-T CONTROLSHELIODYNE INC. DLTA 000-002SOLAR THERMAL
SYSTEM CONTROLLER __ __ 1601204.45
5-1/4 H X 7-3/4 L X 3-3/4 W
31-1/4 H X 22 D
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
SHEET TITLE
LOT NUMBER:
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U.S. DEPARTMENT OF ENERGY
SOLAR DECATHLON 2011
WWW.SOLARDECATHLON.GOV
TEAM NAME:
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CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
50:1
7 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
P-601
PLUMBING SCHEDULES
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
3/4"
3/4"
1/2"
1/2"
1/2"
1/2"1/2"
1/2"
1/2"3/4"
16
17
24
25
1.5"
1.5"
2"
2"
1.5"
2"
1.5"2"
2"
1.5"
26
27
22 13 19.36
22 13 19.36
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
SHEET TITLE
LOT NUMBER:
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U.S. DEPARTMENT OF ENERGY
SOLAR DECATHLON 2011
WWW.SOLARDECATHLON.GOV
TEAM NAME:
ADDRESS:
CONTACT:
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CONSULTANTS
ENGINEERS:
LANDSCAPING:
CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
50:1
8 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
P-602
PLUMBING DIAGRAMS
306
Checker
UNIVERSITY OF HAWAII (TEAM HAWAII)
NTSA1 DOMESTIC SUPPLY DIAGRAM
REFERENCE KEYNOTES22 13 19.36 AIR-ADMITTANCE VALVES
SHEET KEYNOTES16 PEX INSULATED HOT WATER LINE17 PEX COLD WATER LINE24 COLD WATER SUPPLY TO SOLAR WATER
SYSTEM25 HOT WATER SUPPLY FROM SOLAR WATER
SYSTEM26 SANITARY WATER RETURN TO SANITARY
WATER TANK27 SANITARY VENTING TO ROOF
GENERAL SHEET NOTES
NTSC4 SANITARY WASTE & VENT DIAGRAM
MARK DATE DESCRIPTION
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
SHEET TITLE
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CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
50:3
3 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
P-901
DOMESTIC SUPPLYISOMETRICS
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
A1 DOMESTIC SUPPLY ISOMETRIC
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
SHEET TITLE
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SOLAR DECATHLON 2011
WWW.SOLARDECATHLON.GOV
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CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
50:4
5 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
P-902
SANITARY WASTE ANDVENT ISOMETRICS
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
A1 SANITARY WASTE AND VENT ISOMETRIC
DESCRIPTIONABBRV.SYMBOL
BREAK LINE
BALL VALVE
PUMP
MECHANICAL LEGEND
CHECK VALVE
DUCT TRANSITION
CONDENSATE DRAIN
BDD
FLOW DIRECTION ARROW
MIXING VALVE
GATE VALVE
AIR FLOW DIRECTION ARROW
BACK DRAFT DAMPER
PRESSURE RELIEF VALVE
BV
CV
CD
DT
GV
MV
PRV
P
UNION
TEMPERATURE & PRESSURE RELIEF VALVETPRV
VCD
VOLUME CONTROL DAMPERVCD
MECHANICAL NOTES1. MECHANICAL AND HVAC SYSTEMS SHALL BE INSTALLED PER
MANUFACTURER'S SPECIFICATIONS AND INTERNATIONAL RESIDENTIALCODE.
2. THE HVAC SYSTEM IMPLEMENTS A WATER-SOURCE HEAT PUMP DRAWINGFROM A THERMAL MASS WHICH ACTS AS A GEOTHERMAL SOURCE. THETHERMAL MASS CONTAINS PHASE CHANGE MATERIAL WHICH WILL CREATEA LOWER AND UPPER BOUND TEMPERATURE RANGE THAT WILL OPTIMIZETHE PERFORMANCE OF THE HEAT PUMP. DURING COOLING MODE, HEAT WILLBE DUMPED INTO THERMAL MASS, WHILE DURING HEATING MODE COOLERWATER WILL BE PUMPED BACK INTO THERMAL MASS TANK. THIS BALANCEWILL HELP TO REDUCE ENERGY NEEDS AND REDUCE HEAT LOSS FROMSYSTEM.
3. THE THERMAL MASS WILL BE CONTAINED BY AN INSULATEDPILLOW/BLADDER TANK. THE PILLOW TANK WILL HOLD THE PHASE CHANGEMATERIAL WHICH IS CONTAINED IN LONG TUBES. APPROXIMATELY 450 OFTHESE TUBES SHALL BY PLACED INTO THE PILLOW TANK THROUGH FILLOPENING. THE TUBES WILL SELF-STACK INSIDE THE PILLOW TANK, WITHSOME ASSISTANCE. ONCE ALL PHASE CHANGE MATERIAL TUBES (TUBEICE)ARE IN PLACE, THE PILLOW TANK WILL BE FILLED WITH WATER.
4. THE PILLOW TANK WILL BE FILLED WITH WATER PUMP OUT OF THE WATERTANKS THROUGH A 1.5 INCH RUBBER HOSE. A 0.6 HP SUBMERSIBLE PUMPWILL BE USED TO PUMP THE WATER FROM THE WATER TANKS INTO THEPILLOW TANK. THIS PUMP WILL ALSO BE USED TO DRAIN THE PILLOW TANKBACK INTO THE WATER TANKS FOR WATER REMOVAL.
5. HVAC AIR DISTRIBUTION SHALL USE STANDARD RECTANGULAR DUCTINGWITH 1 INCH INSULATION LAYER. FLEXIBLE HOSE DUCT WILL BE USED FORFRESH AIR INTAKE AND ALSO FOR DEHUMIDIFIER CONNECTION. THEDEHUMIDIFIER IS PLACED IN PARALLEL TO THE REST OF THE DISTRIBUTIONSYSTEM SO THAT IF HEAT PUMP IS NOT RUNNING THE DEHUMIDIFIER COULDSTILL RUN AND DEHUMIDIFY AIR INTO HOUSE. THIS WILL REDUCE ENERGYCONSUMPTION FOR DAYS WHEN HEATING AND COOLING ARE NOT NEEDED.BATHROOM VENTILATION WILL BE PROVIDED BY A FAN UNDER THELAVATORY, AND WILL TAKE AIR OUT OF WEST BULKHEAD.
6. INSTALLATION OF MAIN SUPPLY AND RETURN DUCTS, BRANCH DUCT, ANDFLOOR DIFFUSERS WILL BE PRE-INSTALLED PER MODULE OF THE HOUSE.CONNECTIONS BETWEEN MAIN DUCTS WILL BE MADE AFTER MODULES AREPLACED TOGETHER. ALL OTHER MECHANICA EQUIPMENT WILL BE SHIPPEDSEPARATELY AND INSTALLED ONSITE.
7. SOLAR WATER HEATING WILL BE PROVIDED BY SUPERSTRUCTUREMOUNTED SOLAR THERMAL FLAT-PLATE COLLECTORS. PIPING WILL BE RUNFROM COLLECTORS INTO A SOLAR THERMAL STORAGE TANK, CONNECTEDTO A SECOND SOLAR THERMAL STORAGE TANK FITTED WITH A BACKUPHEATING ELEMENT. IN THE EVENT THAT THE COLLECTORS DON'T PROVIDESUFFICIENT WATER HEATING, THE BACKUP HEATER WILL MAKE UP THEDIFFERENCE. A MIXING VALVE WILL TAKE WATER FROM SOLAR STORAGETANKS AND MIX WITH COLD WATER FROM FRESH WATER TANK.
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
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U.S. DEPARTMENT OF ENERGY
SOLAR DECATHLON 2011
WWW.SOLARDECATHLON.GOV
TEAM NAME:
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CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
43:0
9 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
M-001
MECHANICAL SYMBOLSAND NOTES
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
23 81 46
23 84 16
23 21 13.4323 21 23.13
23 71 13.23
23 38 18
11
10
23 37 13.13
13
12
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
SHEET TITLE
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U.S. DEPARTMENT OF ENERGY
SOLAR DECATHLON 2011
WWW.SOLARDECATHLON.GOV
TEAM NAME:
ADDRESS:
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ARCHITECTURE:
CONSULTANTS
ENGINEERS:
LANDSCAPING:
CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
43:1
2 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
M-101
HVAC EQUIPMENT ANDDISTRIBUTION PLAN
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
3/8" = 1'-0"A1 HVAC PLAN
REFERENCE KEYNOTES23 21 13.43 THERMAL MASS LOOP HEAT-PUMP PIPING23 21 23.13 IN-LINE CENTRIFUGAL HYDRONIC PUMPS23 37 13.13 FLOOR DIFFUSER23 38 18 ROOM EXHAUST FAN23 71 13.23 PRESSURIZED-WATER THERMAL STORAGE
TANKS23 81 46 WATER-SOURCE UNITARY HEAT PUMPS23 84 16 DEHUMIDIFIERS
SHEET KEYNOTES10 FRESH AIR INTAKE11 BATHROOM VENTILATION EXHAUST12 AIR SUPPLY MAIN DUCT13 AIR RETURN MAIN DUCT
GENERAL SHEET NOTES
MARK DATE DESCRIPTION
0 4' 6'2'
22 12 1922 33 30.23
22 13 53
21 41 23
22 11 23.26
22 11 16
23 81 46
23 71 13.23
23 21 23.13
23 21 13.43
21 31 13
18
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
SHEET TITLE
LOT NUMBER:
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U.S. DEPARTMENT OF ENERGY
SOLAR DECATHLON 2011
WWW.SOLARDECATHLON.GOV
TEAM NAME:
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LANDSCAPING:
CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
43:2
1 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
M-102
SPILL CONTAINMENTPLAN
306
Checker
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
3/8" = 1'-0"A1 SPILL CONTAINMENT PLAN
REFERENCE KEYNOTES21 31 13 ELECTRIC-DRIVE, CENTRIFUGAL FIRE
PUMPS21 41 23 GROUND SUCTION STORAGE TANKS FOR
FIRE-SUPPRESSION WATER22 11 16 DOMESTIC WATER PIPING22 11 23.26 CLOSE-COUPLED, HORIZONTALLY
MOUNTED, IN-LINE CENTRIFUGALDOMESTIC-WATER PUMPS
22 12 19 FACILITY GROUND-MOUNTED, POTABLEWATER STORAGE TANKS
22 13 53 FACILITY SEPTIC TANKS22 33 30.23 RESIDENTIAL, COLLECTOR-TO-TANK,
SOLAR-ELECTRIC DOMESTIC WATERHEATERS
23 21 13.43 THERMAL MASS LOOP HEAT-PUMP PIPING23 21 23.13 IN-LINE CENTRIFUGAL HYDRONIC PUMPS23 71 13.23 PRESSURIZED-WATER THERMAL STORAGE
TANKS23 81 46 WATER-SOURCE UNITARY HEAT PUMPS
SHEET KEYNOTES18 AQUAPONICS TANKS
GENERAL SHEET NOTES
0 4' 6'2'
23 71 13.23
21 41 23
22 33 30.23 22 12 19
22 13 53
18
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
SHEET TITLE
LOT NUMBER:
DRAWN BY:
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CLIENT
U.S. DEPARTMENT OF ENERGY
SOLAR DECATHLON 2011
WWW.SOLARDECATHLON.GOV
TEAM NAME:
ADDRESS:
CONTACT:
ARCHITECTURE:
CONSULTANTS
ENGINEERS:
LANDSCAPING:
CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
43:2
8 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
M-103
CONTAINERLOCATIONS PLAN
306
Checker
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
3/8" = 1'-0"A1 CONTAINER LOCATIONS PLAN
REFERENCE KEYNOTES21 41 23 GROUND SUCTION STORAGE TANKS FOR
FIRE-SUPPRESSION WATER22 12 19 FACILITY GROUND-MOUNTED, POTABLE
WATER STORAGE TANKS22 13 53 FACILITY SEPTIC TANKS22 33 30.23 RESIDENTIAL, COLLECTOR-TO-TANK,
SOLAR-ELECTRIC DOMESTIC WATERHEATERS
23 71 13.23 PRESSURIZED-WATER THERMAL STORAGETANKS
SHEET KEYNOTES18 AQUAPONICS TANKS
GENERAL SHEET NOTES
0 4' 6'2'
22 13 53
22 12 19
21 41 23
22 33 30.23
E
F
G
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
SHEET TITLE
LOT NUMBER:
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U.S. DEPARTMENT OF ENERGY
SOLAR DECATHLON 2011
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TEAM NAME:
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CONTACT:
ARCHITECTURE:
CONSULTANTS
ENGINEERS:
LANDSCAPING:
CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
43:3
2 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
M-104
MECHANICAL GROUNDCONTACT PLAN
306
Checker
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
3/8" = 1'-0"A1 MECHANICAL GROUND CONTACT PLAN
REFERENCE KEYNOTES21 41 23 GROUND SUCTION STORAGE TANKS FOR
FIRE-SUPPRESSION WATER22 12 19 FACILITY GROUND-MOUNTED, POTABLE
WATER STORAGE TANKS22 13 53 FACILITY SEPTIC TANKS22 33 30.23 RESIDENTIAL, COLLECTOR-TO-TANK,
SOLAR-ELECTRIC DOMESTIC WATERHEATERS
SHEET KEYNOTESE TYPICAL WATER TANK FOOTINGF TYPICAL FIRE TANK FOOTINGG HOT WATER TANKS FOOTING
GENERAL SHEET NOTES1. ALL MECHANICAL EQUIPMENT LOCATED IN THE
UNDER-PORCH AREA WILL BE ELEVATED 3-1/2 INCHOFF THE GROUND ON STANDS.
2. THESE STANDS WILL HAVE FOOTINGS AS SHOWNWITH PRESSURES INDICATED IN MECHANICALFOOTING SCHEDULE.
MECHANICAL FOOTING SCHEDULE
FOOTING TYPE QUANTITY SIZE DIA AREA (SF) TOTAL FILLED LOAD PER TANK (LBS)
E (WATER TANKS)
F (FIRE TANK)
G (HOT WATER TANKS)
8
4
1
1'
10"
N/A
0.7854
0.5454
0.8194
4,360
2,615
454 (2 CT)
1,387.8
1,198.6
1,108.1
FOOTING PRESSURE (PSF)
0 4' 6'2'
FIRST FLOOR4'-5"
SOLAR ENVELOPE18'-0"
GRADE LEVEL0"
2 3 4 5 6 7 8 9 10 111
FIRST FLOOR4'-5"
SOLAR ENVELOPE18'-0"
GRADE LEVEL0"
D BF AE C
FIRST FLOOR4'-5"
SOLAR ENVELOPE18'-0"
GRADE LEVEL0"
DB FA EC
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
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UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
43:5
4 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
M-201
MECHANICALELEVATIONS
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
REFERENCE KEYNOTES
SHEET KEYNOTES
GENERAL SHEET NOTES
MARK DATE DESCRIPTION
1/4" = 1'-0"A1 SOUTH MECHANICAL
1/4" = 1'-0"C4 EAST MECHANICAL 1/4" = 1'-0"C1 WEST MECHANICAL ELEVATION
0 2' 4' 8' 0 2' 4' 8'
0 2' 4' 8'
WATER COOLED AIR CONDITIONING EQUIPMENT SCHEDULE
DESCRIPTION MANUFACTURER
V PHHZ
MODEL
COMPRESSOR (1 EACH)
JOHNSON CONTROLS RJSH015ER000C
FLOW RATE
GPM CFM
COOLINGEWT 86°F
CAPACITY EERBTUH BTUH/W
HEATINGEWT 68°F
CAPACITYCOP
BTUH
PSC FAN MOTOR
HP [W] FLAFACTORY CHARGE
R410A, OZ [KG] RLA LRA
RATED VOLTAGE TOTAL UNIT
FLA
MIN CIRC
AMP
MAX FUSE
HACR
1511.810.216023029.06.238 [1.08]1/6 [134] 4.05.318,50015.914,4005004.0WATER-SOURCE HEAT PUMP
HVAC EQUIPMENT SCHEDULE
DESCRIPTION MANUFACTURER
V PHHZ
MODEL
THERMA-STOR LLC ULTRA-AIRE 65H
FLOW RATE
GPM CFM
POWER
HP WATTS
CURRENTAMPS
RATED VOLTAGE
1601205.50680500DEHUMIDIFIER
DIMENSIONSINCH
21 W X 12 H X 12 D
GRUNDFOS UP15-18 BUC 7THERMAL MASS CIRCULATING PUMP 0 - 16 1/25 160120 5-1/4 H X 7-3/4 L X 3-3/4 W0.74
PANASONICWHISPERGREEN LITE
VENTILATION FANFV-08VKML3
BATHROOM VENTILATION FAN 80 14.9 160120 11.5H x 14.17W x 16.73D0.12
HVAC DUCT AND PIPING SCHEDULE
DESCRIPTION MATERIAL LENGTH
FABRICATED SHEET METAL 1 INCH LAYERRECTANGULAR METAL DUCT
COPPER TYPE K1 INCH THERMAL MASS PIPE
~100 FEET
~30 FEET
INSULATION
1 INCH LAYER
SOLAR THERMAL EQUIPMENT SCHEDULE
DESCRIPTION MANUFACTURER MODEL
HELIODYNE 26,199 (19,742)HEATING SOLARFLAT-PLATE COLLECTORS GOBI 406
DAILY INSOLATION BTU500 ZONE (400 ZONE) PANEL COATING PANEL SIZE
(INCH)
BLACK PAINT 47.56 X 81.56
JOHNSON CONTROLSRJ SERIES CONTROLS
PREMIERMICROPROCESSOR
HVAC CONTROLS 160120_________
__
__
__
__
__ __
__
__
__
__
__
RAINWATER COLLECTIONSOLUTIONS, INC
1200 GALLONPILLOW TANKTHERMAL MASS PILLOW TANK ______ 15' L X 8' W X 2' H
[FEET]____ __ __ __
PCM PRODUCTS LTD TUBEICEENAPSULATED PCMPHASE CHANGE MATERIAL __________ __ __ __ 1000 MM LENTH
50 MM DIAMETER
MECHANICAL VALVE SCHEDULE
FAMILY TYPE COUNT
VOLUME-CONTROLDAMPERHVAC AIR DISTRIBUTION
BACK DRAFTDAMPERHVAC AIR DISTRIBUTION
12
2
GATE VALVETHERMAL MASS LOOP 4
BALL VALVETHERMAL MASS LOOP 2
CONNECTION SIZEDIAMETER INCH
6
1
1
7.5
CHECK VALVETHERMAL MASS LOOP 21
CONDENSATEDRAINHVAC EQUIPMENT 21
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
SHEET TITLE
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U.S. DEPARTMENT OF ENERGY
SOLAR DECATHLON 2011
WWW.SOLARDECATHLON.GOV
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ADDRESS:
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CONSULTANTS
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LANDSCAPING:
CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
43:5
6 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
M-601
MECHANICALSCHEDULES
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
23 84 16
23 81 46
23 71 13.23
23 71 13.26
23 21 23.13
23 21 13.43
23 38 18
10
11
23 33 13.13
23 37 13.13
23 32 36
12
13
23 33 13.13
23 33 13.23
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
SHEET TITLE
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SOLAR DECATHLON 2011
WWW.SOLARDECATHLON.GOV
TEAM NAME:
ADDRESS:
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CONSULTANTS
ENGINEERS:
LANDSCAPING:
CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
43:5
7 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
M-602
HVAC DIAGRAMS
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
REFERENCE KEYNOTES23 21 13.43 THERMAL MASS LOOP HEAT-PUMP PIPING23 21 23.13 IN-LINE CENTRIFUGAL HYDRONIC PUMPS23 32 36 AIR-DISTRIBUTION FLOOR PLENUMS23 33 13.13 VOLUME-CONTROL DAMPERS23 33 13.23 BACKDRAFT DAMPERS23 37 13.13 FLOOR DIFFUSER23 38 18 ROOM EXHAUST FAN23 71 13.23 PRESSURIZED-WATER THERMAL STORAGE
TANKS23 71 13.26 PHASE CHANGE MATERIAL FOR THERMAL
STORAGE23 81 46 WATER-SOURCE UNITARY HEAT PUMPS23 84 16 DEHUMIDIFIERS
SHEET KEYNOTES10 FRESH AIR INTAKE11 BATHROOM VENTILATION EXHAUST12 AIR SUPPLY MAIN DUCT13 AIR RETURN MAIN DUCT
GENERAL SHEET NOTES
NTSA1 HVAC DIAGRAM
MARK DATE DESCRIPTION
22 33 30.23
22 35 23.16
23 56 13.13
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
SHEET TITLE
LOT NUMBER:
DRAWN BY:
CHECKED BY:
COPYRIGHT:
CLIENT
U.S. DEPARTMENT OF ENERGY
SOLAR DECATHLON 2011
WWW.SOLARDECATHLON.GOV
TEAM NAME:
ADDRESS:
CONTACT:
ARCHITECTURE:
CONSULTANTS
ENGINEERS:
LANDSCAPING:
CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
43:5
8 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
M-603
SOLAR WATERDIAGRAMS
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
REFERENCE KEYNOTES22 33 30.23 RESIDENTIAL, COLLECTOR-TO-TANK,
SOLAR-ELECTRIC DOMESTIC WATERHEATERS
22 35 23.16 CIRCULATING, STORAGE DOMESTIC WATERHEAT EXCHANGERS
23 56 13.13 HEATING SOLAR FLAT-PLATE COLLECTORS
SHEET KEYNOTES
GENERAL SHEET NOTES
NTSA1 SOLAR WATER DIAGRAM
MARK DATE DESCRIPTION
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
SHEET TITLE
LOT NUMBER:
DRAWN BY:
CHECKED BY:
COPYRIGHT:
CLIENT
U.S. DEPARTMENT OF ENERGY
SOLAR DECATHLON 2011
WWW.SOLARDECATHLON.GOV
TEAM NAME:
ADDRESS:
CONTACT:
ARCHITECTURE:
CONSULTANTS
ENGINEERS:
LANDSCAPING:
CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
44:1
4 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
M-901
HVAC ISOMETRICS
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
A1 HVAC ISOMETRIC
MARK DATE DESCRIPTION
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
SHEET TITLE
LOT NUMBER:
DRAWN BY:
CHECKED BY:
COPYRIGHT:
CLIENT
U.S. DEPARTMENT OF ENERGY
SOLAR DECATHLON 2011
WWW.SOLARDECATHLON.GOV
TEAM NAME:
ADDRESS:
CONTACT:
ARCHITECTURE:
CONSULTANTS
ENGINEERS:
LANDSCAPING:
CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
44:2
2 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
M-902
SOLAR WATERISOMETRICS
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
A1 SOLAR WATER ISOMETRIC
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
SHEET TITLE
LOT NUMBER:
DRAWN BY:
CHECKED BY:
COPYRIGHT:
CLIENT
U.S. DEPARTMENT OF ENERGY
SOLAR DECATHLON 2011
WWW.SOLARDECATHLON.GOV
TEAM NAME:
ADDRESS:
CONTACT:
ARCHITECTURE:
CONSULTANTS
ENGINEERS:
LANDSCAPING:
CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
13:4
9 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
A-561
ROOF DETAILS
306
CHECKER
UNIVERSITY OF HAWAII (TEAM HAWAII)
REFERENCE KEYNOTES
SHEET KEYNOTES
GENERAL SHEET NOTES
MARK DATE DESCRIPTION
1" = 1'-0"E1 ROOF PLUMBING VENT PENETRATION0 2' 3'1'
22 13 53
22 12 19
21 41 23
23 71 13.23
18
WATER DELIVERY AND REMOVAL SCHEDULE1. ON DAY 5 OF COMPETITION WATER WILL BE DELIVERED TO SITE. TRUCK WILL ARRIVE ON DECATHLON WAY. HOSE WILL BE
UNLOADED AND BROUGHT TO SIDE OF PORCH.2. THE PORCH ACCESS DOORS WILL BE OPENED AND THE HOSE WILL BE RUN UNDER PORCH AREA TO BE INSERTED INTO
THE FRESH WATER STORAGE TANK. PRIOR TO DELIVERY A CONNECTION BETWEEN THE FRESH WATER TANK ANDSANITARY TANK WILL BE MADE. AS THE FRESH WATER TANK IS FILLED, WATER WILL ALSO FLOW INTO THE SANITARY WATERTANK VIA THE CONNECTION. BOTH TANKS WILL BE FILLED WITH APPROXIMATELY 500 GALLONS EACH, FOR A TOTAL INITIALDELIVERY OF 1000 GALLONS.
3. AFTER INITIAL DELIVERY WATER WILL BE DISTRIBUTED FROM FRESH AND SANITARY WATER TANKS INTO THE THERMALMASS PILLOW TANK AND FIRE TANK. THIS WILL BE DONE USING A SANITARY SUBMERSIBLE PUMP AND HOSE. THIS PROCESSWILL EMPTY BOTH FRESH AND SANITARY WATER TANKS.
4. WATER TRUCK WILL RETURN FOR "TOP OFF" OF FRESH WATER TANK. THIS WILL TAKE THE REMAINING 500 GALLONS OFALLOTTED WATER DELIVERY BUDGET. AT THIS POINT THE CONNECTION BETWEEN THE SANITARY AND FRESH WATERTANKS WILL HAVE BEEN REMOVED, AND CONNECTION POINTS PLUGGED. IT WILL REMAIN THIS WAY DURING COMPETITION.
5. ON WATER REMOVAL DAY THE WATER TRUCK WILL ARRIVE ON DECATHLON WAY. HOSE WILL BE UNLOADED ANDBROUGHT TO SIDE OF PORCH.
6. PRIOR TO WATER REMOVAL WATER WILL BE DRAINED FROM THERMAL MASS PILLOW TANK AND FIRE TANK BACK INTOFRESH AND SANITARY WATER TANKS. THIS WILL BE DONE USING A SANITARY SUBMERSIBLE PUMP AND HOSE. THISPROCESS WILL FILL BOTH FRESH AND SANITARY WATER TANKS.
7. THE PORCH ACCESS DOORS WILL BE OPENED AND THE HOSE WILL BE RUN UNDER PORCH AREA TO BE INSERTED INTOTHE FRESH WATER STORAGE TANK. PRIOR TO REMOVAL THE CONNECTION BETWEEN THE FRESH WATER TANK ANDSANITARY TANK WILL BE MADE. AS THE FRESH WATER TANK IS DRAINED, WATER WILL ALSO DRAIN FROM THE SANITARYWATER TANK VIA THE CONNECTION. BOTH TANKS WILL BE DRAINED OF APPROXIMATELY 500 GALLONS EACH, FOR A TOTALINITIAL REMOVAL OF 1000 GALLONS.
8. AFTER INITIAL REMOVAL THE WATER NOW CONTAINED IN THE AQUAPONICS TANKS WILL BE DRAINED AND PUMPED BACKINTO SANITARY WATER TANK, WITH CONNECTION BETWEEN FRESH AND SANITARY TANKS STILL IN PLACE. THE WATERTRUCK WILL RETURN AFTER SERVICING OTHER HOUSES TO REMOVE APPROXIMATELY 500 GALLONS OF REMAININGWATER.
FIRST FLOOR4'-5"
GRADE LEVEL0"
1'-4
3/4
"
1 2 3 4 5 6 7
A
B
C
D
E
1 2 3 4 5 6 7
A
B
C
D
E
SHEET TITLE
LOT NUMBER:
DRAWN BY:
CHECKED BY:
COPYRIGHT:
CLIENT
U.S. DEPARTMENT OF ENERGY
SOLAR DECATHLON 2011
WWW.SOLARDECATHLON.GOV
TEAM NAME:
ADDRESS:
CONTACT:
ARCHITECTURE:
CONSULTANTS
ENGINEERS:
LANDSCAPING:
CODE CONSULTANTS:
UNIVERSITY OF HAWAI'ISCHOOL OF ARCHITECTURE
UNIVERSITY OF HAWAI'I
5/3/
2011
10:
49:5
6 AM
UNIVERSITY OF HAWAI'I AT MĀNOA2410 CAMPUS ROADHONOLULU, HI 96822
O-201
WATER DELIVERY ANDREMOVAL PLAN
306
Checker
UNIVERSITY OF HAWAII (TEAM HAWAII)
MARK DATE DESCRIPTION
1/4" = 1'-0"A1 WATER DELIVERY AND REMOVAL PLAN
REFERENCE KEYNOTES21 41 23 GROUND SUCTION STORAGE TANKS FOR
FIRE-SUPPRESSION WATER22 12 19 FACILITY GROUND-MOUNTED, POTABLE
WATER STORAGE TANKS22 13 53 FACILITY SEPTIC TANKS23 71 13.23 PRESSURIZED-WATER THERMAL STORAGE
TANKS
SHEET KEYNOTES18 AQUAPONICS TANKS
GENERAL SHEET NOTES
3/8" = 1'-0"D1 WATER DELIVERY AND REMOVAL SECTION DETAIL
0 2' 4' 8'
0 4' 6'2'