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EmpireEmpireEmpireEmpireEmpireEmpireEmpire of of of the the the the Penguins Penguins Penguins Penguins Penguins Penguins Penguins Penguins Penguins PenguinsHVAC System for Health, Safety
Procurement Path for Energy-Efficient Buildings | The Hidden Daytime Price of Electricity
Energy-Efficient Approach for Operating Rooms | Windows Can Be a Pain
APRIL 2015
J O U R N A LTHE MAGAZINE OF HVAC&R TECHNOLOGY AND APPLICATIONS ASHRAE.ORG
AA S S S S H H H H R R R R A A A A E E E E®
www.info.hotims.com/54427-22
www.info.hotims.com/54427-48
A P R I L 2 0 1 5 a sh r a e . o r g A S H R A E J O U R N A L 3
FEATURES
STANDING COLUMNS
ASHRAE® Journal (ISSN 0001-2491) MISSION STATEMENT | ASHRAE Journal reviews current HVAC&R technology of broad interest through publication of application-oriented articles. ASHRAE Journal’s editorial content ranges from back-to-basics features to reviews of emerging technologies, covering the entire spectrum of professional interest from design and construction practices to commissioning and the service life of HVAC&R environmental systems. PUBLISHED MONTHLY | Copyright 2015 by ASHRAE, 1791 Tullie Circle N.E., Atlanta, GA 30329. Periodicals postage paid at Atlanta, Georgia, and additional mailing offices. LETTERS/MANUSCRIPTS | Letters to the editor and manuscripts for publication should be sent to: Fred Turner, Editor, ASHRAE Journal, [email protected]. SUBSCRIPTIONS | $8 per single copy (includes postage and handling on mail orders). Subscriptions for members $6 per year, included with annual dues, not deductible. Nonmember $79 (includes postage in USA); $79 (includes postage for Canadian); $149 international (includes air mail). Expiration dates vary for both member and nonmember sub scriptions. Payment (U.S. funds) required with all orders. CHANGE OF ADDRESS | Requests must be received at subscription office eight weeks before effective date. Send both old and new addresses for the change. ASHRAE members may submit address changes at www.ashrae.org/address. POSTMASTER | Send form 3579 to: ASHRAE Journal, 1791 Tullie Circle N.E., Atlanta, GA 30329. Canadian Agreement Number 40037127.
ONLINE at ASHRAE.org | Feature articles are available online. Members can access articles at no cost. Nonmembers may purchase articles at www.ashrae.org/bookstore. MICROFILM | This publication is microfilmed by National Archive Publishing Company. For information on cost and issues available, contact NAPC at 800-420-NAPC or www.napubco.com. PUBLICATION DISCLAIMER | ASHRAE has compiled this publication with care, but ASHRAE has not investigated and ASHRAE expressly disclaims any duty to investigate any product, service, process, procedure, design or the like which may be described herein. The appearance of any technical data, editorial material or advertisement in this publication does not constitute endorsement, warranty or guarantee by ASHRAE of any product, service, process, procedure, design or the like. ASHRAE does not warrant that the information in this publication is free of errors and ASHRAE does not necessarily agree with any statement or opinion in this publication. The entire risk of the use of any information in this publication and its supplement is assumed by the user.
DEPARTMENTS
CONTENTS VOL. 57, NO. 4, APRIL 2015
3056
12
2015 ASHRAE TECHNOLOGY AWARDS
52 ENGINEER’S NOTEBOOK Overlooked Code
Requirements Part 2
By Stephen W. Duda, P.E.
56 BUILDING SCIENCES Windows Can Be a Pain By Joseph W. Lstiburek, Ph.D., P.Eng.
80 REFRIGERATION APPLICATIONS English, Irish and Scots By Andy Pearson, Ph.D., C.Eng.
4 Commentary
6 Industry News
10 Meetings and Shows
82 Products
84 Special Products
86 Classified Advertising
88 Advertisers Index
12 Procurement Path For Energy-Efficient Buildings
By Adam McMillen, P.E.; Paul Torcellini, Ph.D., P.E.; Sumit Ray, P.E.; Kevin Rodgers
30 Energy-Efficient Approach For Operating Rooms
By Philip Bartholomew, P.E.
64 The Hidden Daytime Price of Electricity
By Evan Berger
42 Antarctica: Empire of the Penguin By William C. Weinaug Jr., P.E.
74 Southwest One: Mixed Use Complex By Daniel Robert, Eng.; Stan Katz
Cover Photo Credit: SeaWorld
A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 54
ASHRAE Journal reviews current HVAC&R technology of broad interest through publication of applica-tions-oriented articles. Content ranges from back-to-basics features to reviews of emerging technologies.
COMMENTARY1791 Tullie Circle NEAtlanta, GA 30329-2305Phone: 404-636-8400Fax: 404-321-5478 | www.ashrae.org
PUBLISHER W. Stephen Comstock
EDITORIAL Managing Editor Sarah Foster [email protected]
Associate Editor Rebecca Matyasovski [email protected]
Associate Editor Christopher Weems [email protected]
Associate Editor Jeri Alger [email protected]
Assistant Editor Tani Palefski [email protected]
PUBLISHING SERVICESPublishing Services Manager David Soltis
Production Jayne Jackson Tracy Becker
ADVERTISINGAssociate Publisher, ASHRAE Media Advertising Greg Martin [email protected]
Advertising Production Coordinator Vanessa Johnson [email protected]
CIRCULATIONCirculation Specialist David Soltis [email protected]
ASHRAE OFFICERSPresident Thomas H. Phoenix, P.E.
President-Elect T. David Underwood, P.Eng.
Treasurer Timothy G. Wentz, P.E.
Vice Presidents Darryl K. Boyce, P.Eng.Charles E. Gulledge IIIBjarne W. Olesen, Ph.D.James K. Vallort
Secretary & Executive Vice President Jeff H. Littleton
POLICY GROUP2014 – 15 Chair Publications Committee Michael R. Brambley, Ph.D.
Washington Office [email protected]
HVAC Is for PenguinsFor years, there was a reoccurring tech-
nical session at each ASHRAE Winter and
Annual Conference entitled HVAC Is for
People. The focus was to improve under-
standing of the human factors associated
with the indoor environment.
One of the session’s regular speakers
was Dr. P. Ole Fanger, one of the giants in
the field of thermal comfort, who intro-
duced the “olf” to the study of indoor air
quality. While some thought “olf” was a
play on his name, it was actually a deriv-
ative of the Latin word olfactus, meaning
“smelled.” For the record, one “olf” is the
sensory pollution strength from an aver-
age adult working in an office or similar
non-industrial workplace, sedentary
and in thermal comfort, with a hygienic
standard equivalent of 0.7 baths per day
and whose skin has a total area of 1.8
m2 (19 ft2). In other words, the relative
strength of pollution sources that can
be perceived by humans. To Fanger, the
nose was the perfect sensor for indoor
air quality.
And before the contributions of Ole
Fanger, who was an ASHRAE Fellow and a
member of America’s National Academy
of Engineering even though he was a
researcher at the Technical University of
Denmark, there was ASHRAE’s Standard
55, Thermal Environmental Conditions for
Human Occupancy. The latest version
was published in 2013, but the stan-
dard was first issued nearly 50 years
ago benefitting over the years from the
work of many ASHRAE members includ-
ing Ralph Nevins from Kansas State
University and A. Pharo Gagge from Yale
University.
This issue of ASHRAE Journal approaches
the topic of indoor environmental
quality from another perspective—that of
the penguin. It is a reminder that engi-
neering practitioners and researchers
working to better control environments
deal with far more than air conditioning
for the everyday commercial and resi-
dential spaces in which we spend most of
our time. ASHRAE members design and
maintain a vast number of environments
for industrial processes, health-related
applications, space endeavors and yes,
worlds for penguins. According to Bjarne
Olesen, an ASHRAE Fellow and current
researcher at the Technical University of
Denmark, there’s even a comfort index
for pigs.
The Empire of the Penguin is an
immersive dark ride and penguin
exhibit. The 30,000 ft2 (2787 m2) project
is described in one of this month’s feature
articles. It won first place in ASHRAE’s
Technology Awards existing commer-
cial buildings category. Guests enter the
facility through a pre-show theater, pass
into a rock and ice themed queue, and
exit the queue through a small “ice den”
to load onto a unique trackless ride sys-
tem. The vehicles move through various
scenes, including a large theater space,
ending at an unload platform inside the
frozen penguin exhibit. The adventure
concludes in an underwater viewing area.
Animal comfort and health were the main
key performance indicators for the design
of the HVAC system with indoor air qual-
ity being the most critical.
More than just humans are dependent
on the work of ASHRAE engineers. Ask
the penguins. You can read about them
beginning on page 42.
W. Stephen Comstock, Publisher
www.info.hotims.com/54427-36
To learn more about HTHV technology, SCHEDULE A LUNCH & LEARN TODAY:www.cambridge-eng.com
With HTHV heating technology, one piece of equipment can
dramatically reduce energy costs and improve Indoor Air Quality
at the same time it is heating commercial and industrial buildings.
www.info.hotims.com/54427-14
Eiffel Tower NowGenerates OwnPower With WindTurbinesPARIS—The historic EiffelTower took a step into a sus-tainable future in March as it brought online two onsite wind turbines. The turbines are installed inside the tower’s metal scaffolding on the second level, and are painted in the same color to minimize their visual impact on the 126-year-old tower. The turbines are
installed 122 m (400 ft) from the ground in order to maximize annual electricity production potential. The turbines are expected to produce about 10,000 kWh of electricity per year. This would meet the total annual demand of the tower’s first floor, which includes res-taurants, a souvenir shop, and history exhibits. The Eiffel Tower also is install-ing rainwater collection systems to supply water for its toilets, high-efficiency LED lights, and solar panels in order to further decrease the landmark’s environ-mental footprint.
While the tower was not required to meet any envi-ronmental benchmark, the tower’s operating company,
Societe d’Exploitation de la Tour Eiffel (SETE), is attempting to reduce the tower’s environmental impact by 25% as part of the City of Paris Climate Plan.
WASHINGTON, D.C.—President Barack Obama signed an executive order in March to reduce green-house gas emissions while boosting clean energy.
“Planning for Federal Sustainability in the Next Decade” directs federal agencies to cut their green-house gas emissions from levels measured in 2008 by 40% by 2025 and increase the federal government’s use of renewables by 30%.
In addition to 21 million metric tons of emission reductions, achieving this goal could save up to $18 bil-lion in avoided energy costs between 2008 and 2025.
President DirectsFederal AgenciesTo Cut Emissions
UNIV
ERSA
L GR
EEN
ENER
GY
Eiffel Tower’s wind turbines
Haier Unveils3-D Printed AirConditionerSHANGHAI—Chineseconsumer electronics and home appliances firm Haier Group unveiled what it says is the world’s first 3-D printed fully functional air conditioner.
HAIE
R
World’s first 3-D printed air conditioner
A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 56
INDUSTRY NEWS
www.info.hotims.com/54427-37
www.info.hotims.com/54427-30
The hi-wall split-system unit wasdisplayed at the recent annual Appliance and Electronics World Expo. The unit’s cooling and heat-ing systems are fully functional, and even its LCD display is 3-D printed. The unit on display, at the time the only one available, was sold for
$6,395. Haier says that by making the unit 3-D printable, future units could easily be adjusted to suit each custom-er’s choice of color and style. The com-pany says that future units will even have 3-D printed computer boards, so users can adjust functionality. The printing process takes one day.
ORNL, Whirlpool To Develop New Energy-Efficient RefrigeratorOAK RIDGE, Tenn.—The U.S. Department of Energy’s Oak Ridge National Laboratory and Whirlpool Corp. are collaborating to design a refrigerator that could reduce energy use by up to 40% compared with cur-rent models.
The goal of the cooperative research and development agreement is to make a next-generation household refrigerator more energy efficient by using WISEMOTION, a linear com-pressor manufactured by Embraco, and other novel technologies and materials. The goal is to build a refrig-erator that consumes less than 1 kWh per day.
Researchers Develop Window Screen That Cleans the AirPALO ALTO, Calif.—Researchers at Stanford University have developed a low-cost filter that captures tiny airborne particles while remaining largely transparent. The nanotech-nology-based system, researchers say, might someday be used in window screens that would allow light and air to pass through while improving indoor air quality. The technology would function without requiring any outside energy source or costly equip-ment and ductwork. The scientists aim to capture particulate matter less than 2.5 microns in size.
ORNL
ORNL’s Pradeep Bansal examines a compressor fora new energy-efficient refrigerator.
A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 58
INDUSTRY NEWS
www.info.hotims.com/54427-17
A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 51 0
MEETINGS AND SHOWS FULL CALENDAR: WWW.ASHRAE.ORG/CALENDAR
ASHRAE JOURNAL ASHRAE Journal seeks applications ar-ticles of 3,000 or fewer words. Submis-sions are subject to peer reviews and can-not have been published previously. Sub-mit abstracts before sending articles to [email protected].
SCIENCE AND TECHNOLOGY FOR THE BUILT ENVIRONMENTASHRAE’s Science and Technology for the Built Environment seeks papers on original, com-pleted research not previously published. Papers must discuss how the research con-tributes to technology. Papers should be about 6,000 words. Abstracts and papers should be submitted on Manuscript Cen-tral at www.ashrae.org/manuscriptcentral. Contact Reinhard Radermacher, Ph.D., Editor, at [email protected].
ASHRAE CONFERENCE PAPERS For the 2016 Winter Conference in Or-lando, Fla., technical papers are due April 20, 2015. For more information, contact 678-539-1137 or [email protected].
MAYLightfair International, May 3 – 7, New York. Con-tact organizers at 404-220-2220, [email protected], or www.lightfair.com.
EE Global 2015, May 12 – 13, Washington D.C. Contact Becca Rohrer at Alliance to Save En-ergy at 202-0530-2206, [email protected], or www.eeglobalforum.org.
AIA Convention 2015, May 14 – 16, Atlanta. Con-tact the American Institute of Architects at 800-242-3837, [email protected], or www.aia.org/convention.
AIHce 2015, May 30 – June 4, Salt Lake City. Contact Lindsay Padilla at the American Industrial Hygiene Association at 703-846-0754, [email protected], or www.aihce2015.org.
JUNEASHRAE Annual Conference, June 27 – July 1,Atlanta. Contact ASHRAE at 800-527-4723 or [email protected].
JULY Solar 2015, July 28 – 30, State College, Pa. Contact 303-443-3130, [email protected], or http://solar2015.ases.org.
AUGUST NAFA Annual Convention, Aug. 27 – 29. Key West, Fla. Contact the National Air Filtration Associa-tion at 757-313-7400, [email protected], or www.nafahq.org.
SEPTEMBERACEEE National Conference on Energy Efficien-cy as a Resource, Sept. 20 – 22, Little Rock, Ark. Contact the American Council for an Energy-Effi-cient Economy at 202-507-4000 or www.aceee.org/conferences/2015/eer.
SMACNA Annual Convention, Sept. 27 – 30, Colo-rado Springs, Colo. Contact the Sheet Metal and Air Conditioning Contractors’ Association at 703-803-2980, [email protected], or www.smacna.org.
RETA Conference, Sept. 29 – Oct. 2, Milwaukee. Contact the Refrigeration Engineers and Techni-cians Association at 831-455-8783, [email protected], or www.reta.com.
World Energy Engineering Congress, Sept. 30 – Oct. 2, Orlando, Fla. Contact the Association of Energy Engineers at 770-447-5083, [email protected], or www.energycongress.com.
2015 ASHRAE Energy Modeling Conference: Tools for Designing High Performance Buildings, Sept. 30 – Oct. 2, Atlanta. Contact ASHRAE at 800-527-4723, [email protected], or www.ashrae.org/emc2015.
OCTOBERIFMA’s World Workplace, Oct. 7 – 9, Denver. Con-tact the International Facility Management Asso-ciation at 713-623-4362, [email protected], or www.ifma.org.
AHR Expo-Mexico, Oct. 20 – 22, Guadalajara, Mex-ico. Contact the International Exposition Compa-ny at 203-221-9232, [email protected], or www.ahrexpomexico.com.
CTBUH 2015, Oct. 26 – 30, New York. Contact the Council on Tall Buildings and Urban Habitat at 312-567-3487, [email protected], or www.ctbuh2015.com.
NOVEMBERAHRI Annual Meeting, Nov. 15 – 17, Bonita Springs,Fla. Contact Air-Conditioning, Heating, and Refrig-eration Institute at 703-524-8800, [email protected], or www.ahrinet.org.
Greenbuild International Conference & Expo, Nov. 18 – 20, Washington, D.C. Contact organizers at 866.815.9824, [email protected], or www.greenbuildexpo.com.
DECEMBERHARDI Annual Conference, Dec. 5–8, Orlando,Fla. Contact the Heating, Air-conditioning & Refrig-eration Distributors International at 614-345-4328, [email protected], or www.hardinet.org.
2016JULY2016 Purdue Compressor/Refrigeration and AirConditioning and High Performance Buildings Conferences and Short Courses, July 11 – 14, West Lafayette, Ind. Contact Kim Stockment at 765-494-6078, [email protected], or http://tinyurl.com/Purdue2016.
OCTOBERASPE Convention and Exposition, Oct. 27 – Nov. 4, Phoenix. Contact the American Society of Plumb-ing Engineers at 847-296-0002, [email protected], or www.aspe.org.
OUTSIDE NORTH AMERICAAPRILCIAR 2015, April 28 – 30, Madrid. Contact [email protected] or www.ciar2015.org.
MAYMostra Convegno Expocomfort Saudi, May 4 – 6,Riyadh, Saudi Arabia. Contact Reed Exhibitions at 39 02 4351701, fax 39 02 3314348, [email protected] or www.mcexpocomfort.it.
Advanced HVAC and Natural Gas Technolo-gies 2015, May 6 – 9, Riga, Latvia. Endorsed by ASHRAE. Contact Agnese Lickrastina, Riga Techni-cal University at [email protected] or www.hvacriga2015.eu.
2015 International Conference on Energy and En-vironment in Ships, May 22 – 24, Athens, Greece. Contact ASHRAE at 800-527-4723, [email protected], or www.ashrae.org/Ships2015.
JULYISHVAC-COBEE 2015, July 12 – 15, Tianjin, China. Endorsed by ASHRAE. Contact organizers at [email protected] or http://www.cobee.org.
AUGUSTIIR International Congress of Refrigeration, Aug. 16 – 22, Yokohama, Japan. Endorsed by ASHRAE. Contact 81 3 3219 3541, [email protected], or www.icr2015.org.
SEPTEMBERMostra Convegno Expocomfort Asia, Sept. 2 – 4, Singapore. Contact Reed Expositions Singapore at 65 6780 4671, fax 65 6588 3832, [email protected] or www.mcexpocomfort-asia.com.
OCTOBER8th International Cold Climate HVAC Confer-ence, Oct. 20 – 23, Dalian, China. Endorsed by ASHRAE. Contact organizers at 86 411 84709612, [email protected], or www.coldclimate2015.org.
11th International Conference on Industrial Ventilation, Oct. 26 – 28, Shanghai. Endorsed by ASHRAE. Contact 86 21 65984243, [email protected], or www.ventilation2015.org.
NOVEMBER13th Asia Pacific Conference on the Built Envi-ronment, Nov. 19 – 20, Hong Kong. Endorsed by ASHRAE. Contact organizers at [email protected] or www.ashrae-hkc.org/APC2015.html.
DECEMBERIBPSA 2015, Dec. 7 – 9, Hyderabad, India. Endorsed by ASHRAE. Contact Dr. Vishal Garg, Internation-al Building Performance Simulation Association at [email protected] or www.bs2015.in.
2016MARCH CMPX 2016, March 16 – 18, Toronto. Contact 416-444-5225, [email protected], or www.cmpxshow.com.
MAYCLIMA 2016, May. 22 – 25, Aaborg, Denmark. En-dorsed by ASHRAE. Contact www.clima2016.org.
CALLS FOR PAPERS
www.info.hotims.com/54427-33
A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 51 2
TECHNICAL FEATURE
Adam McMillen, P.E., is director of energy consulting with the Energy Center of Wisconsin’s Chicago office. Paul Torcellini, Ph.D., P.E., is the principal engineer for CommercialBuildings Research at NREL. Sumit Ray, P.E., is director, engineering and utilities, and Kevin Rodgers is university energy engineer, at the University of Chicago.
Procurement Path for Path for PathEnergy-EfficientEnergy-Efficient Buildings BuildingsEnergy-Efficient BuildingsEnergy-EfficientEnergy-Efficient BuildingsEnergy-EfficientBY ADAM MCMILLEN, P.E.; PAUL TORCELLINI, PH.D., P.E., MEMBER ASHRAE; SUMIT RAY, P.E.; AND KEVIN RODGERS, MEMBER ASHRAE
In a perfect world, a building owner building owner building tells everyone what sort of building of building of should building should building bebuilt. Talented design and contractor teams come together to design and build it.Twelve months later, the building performs building performs building to expectations, and the tenants are allhappy. Utility bills Utility bills Utility match the design energy analysis. energy analysis. energy Simple, right?
Unfortunately, design and construction schedules are
tight and decisions must be made in the need of the
moment. Even with strong energy goals, not everyone
bases decisions on the potential impact to those goals.
The details of the building often are still being worked
out after construction begins. So, how can we achieve a
building that meets the owner’s performance criteria?
Which teams understand the value proposition and
deliver the results? How do you encourage and motivate
design and construction teams?
Some owners are taking a new approach to procure
and achieve performance by using an absolute, mea-
surable energy goal set at the beginning of the project,
prior to design. In this article, we lay the framework for
an emerging approach to establish and execute tangible
energy performance goals. It is intended to simply intro-
duce some base knowledge for when design teams see
this requirement in an request for proposal (RFP) for the
first time. We will start with two new construction proj-
ects that blended a traditional design-build procure-
ment process with a more open, collaborative approach.
Future articles will dive deeper into these concepts and
the impact on measured building performance.
The University of Chicago is now midway through the
design of its 390,000 ft2 (36 232 m2) residence hall. This
project, scheduled for completion in 2016, sought an
effective way to set a new construction energy perfor-
mance-based target that they needed to hit to achieve
campus-wide energy reduction goals. The National
Renewable Energy Laboratory’s Research Support
Facility (RSF) project set out to demonstrate the inte-
gration of high performance design and procurement
practices in a replicable manner. This 360,000 ft2 (33
445 m2) Class A office building achieved both a stringent
performance-based target and net zero design upon
completion in 2010. Both projects had distinctive project
University of Chicago Campus North Residence Hall and Dining Commons.
Stu
dio
Gan
g Ar
chite
cts
A P R I L 2 0 1 5 a sh r a e . o r g A S H R A E J O U R N A L 1 3
TECHNICAL FEATURE
requirements and a common methodology to achieve
real, measurable energy performance goals.
This new contract method also provides an incentive to
build more efficiently, encourages the team to go beyond
code requirement minimums, and provides an excel-
lent return on investment with low risk. Here, the owner
drives performance-based design from the initial scoping
stage to allow design team flexibility to deliver a solution
that the market can bear. In short, the building owner:
1. Sets a firm price for the project during program
planning;
2. Specifies a whole building energy performance
requirement;
3. Aligns program metrics with the performance
criteria;
4. Assembles the request for proposal document;
5. Invites design-builders to propose solutions that
best achieve the prioritized requirements;
6. Reviews energy analysis throughout project life; and
7. Measures the energy performance after substantial
completion.
These seven steps (described below) set the framework
that allows the owner to select the best design-build
team that is responsible and accountable for designing,
building, and delivering the project that meets the con-
tractually proposed requirements. This is also achieved
within a fixed schedule and for a firm-fixed price.1 The
power of the approach is in the simple clarity of the
energy performance goal statement; it communicates
a single number that is measured at the end of the con-
tract. In this way, quality and operational efficiency can
be measured just as easily as the procurement budget
and project timeline.
1. Set a firm price for the project during program
planning. Specifying an energy target should not impact
the budget if the project enables feedback mechanisms
toward what the market can bear. The question is sim-
ply reversed: “If this is my budget and I’d like to achieve
this energy use intensity (EUI), what type of building
and systems will meet both of these goals?” The two
case studies provided in this article approached project
budget in the same manner as traditional processes. It
was established to be competitive with today’s standard
energy efficient commercial and institutional buildings.
2. Specify a whole building energy performance
requirement. Establishing a measurable performance
goal is the key difference in this approach. On typical
projects, budget and schedule is often held in strict com-
munication, while actual energy performance is often
handed-off to the facilities and maintenance group
at substantial completion. A key component of this
approach is that building energy performance remains
with the procurement team. Since the project has a
target value for energy consumption that is tracked
throughout design and construction, the project can
measure success once building operation is under way.
Establishing the target number can be flexible to
the owner’s needs. Common metrics may include EUI
(kBtu/ft2·year), absolute energy use (total kWh and
therms), or independent utility consumption targets
(electricity use in kWh/ft2 and natural gas use in therms/
ft2). Several projects have leveraged existing buildings
in their portfolio, performance of their peers, building
energy performance databases, and early conceptual
energy models (Figure 1). In the end, the goal is to provide
enough context to find a target with relevance to mul-
tiple owner needs. In contrast, many more traditional
high performance design processes establish a number
relative to some other intangible, unmeasured num-
ber (i.e., code baseline building model). This approach
lacks the direction, communication, and persistence
that the project requires. For example, stating that the
building must have a site EUI lower than 55 kBtu/ft2·year
(625 MJ/m2·year) is viewed, and executed, much more
effectively than stating 30% better than ASHRAE/IES
Standard 90.1-2010. For a goal to be met, the energy tar-
get must be an absolute and tangible number.
Site
EUI
(kBt
u/gs
f/yea
r)
FIGURE 1 Setting the energy performance target.
120
100
80
60
40
20
0
Existing Campus Residence Hall 2
Existing Campus Residence Hall 1
Conceptual Energy Model (Baseline)
Peer Institution Residence HallEnergy Star Certified Residential
Net Zero Design (Before Renewables)
Conceptual Energy Model (Aggressive)
Architecture 2030 Challenge Residence Hall
The energy goal should be tangible numbers that provide meaning to the project owner. One example scenario using several resources is provided above. The energy performance require-ment (dashed line) can be confidently established after reviewing a number of additional re-sources (blue diamonds).
Reference Project Project Energy Performance Requirement
Site E
UI (k
Btu/
ft2 ·year
)
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Aligning Program Metrics With the Energy Goal
Mission Critical
1. Attain safe work performance and safe design practices
2. LEED Platinum rating
3. Energy Star appliances, unless other system outperforms
Highly Desirable
4. 800 staff capacity (later adjusted to 822)
5. 25 kBtu/ft2 including NREL’s data center
6. Architectural integrity
7. Honor future staff needs
8. Measurable 50% plus energy savings versus ASHRAE Standard 90.1-2004
9. Support culture and amenities
10. Expandable building
11. Ergonomics
12. Flexible workspace
13. Support future technologies
14. Documentation to produce a How To manual
15. PR campaign implemented in real time for benefit of DOE/NREL and DB (design/build team)
16. Allow secure collaboration with outsiders
17. Building information modeling
18. Substantial completion by June 2010
If Possible
19. Net zero design approach
20. Most energy-efficient building in the world
21. LEED Platinum Plus rating
22. Exceed 50% savings over ASHRAE baseline
23. Visual displays of current energy efficiency
24. Support public tours
25. Achieve national and global recognition and awards
26. Support personnel turnover
The set of program metrics and performance criteria should be unique to each project. The program metrics for the National Renewable Energy Lab’s RSF facility were as follows:1
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3. Align program metrics to the performance crite-
ria. Any good engineering problem is defined by specific
dependent and independent variables. In setting three
key independent variables (budget, time, and energy
use), this new approach must then include other depen-
dent variables to be able to arrive at a solution. Both
projects presented here established tiered criteria to
allow flexibility. In NREL’s case, they established three
levels:
• Mission critical: most likely viewed as independent
variables, these are the metrics that are critical to the
success of the project. The solution must include these.
• Highly desirable: primary goals that contribute to
project success and owner satisfaction. If these are not
included, the trade-offs should be made clear.
• If possible: highly beneficial if they are included in
the solution.
This provided a framework for the goal and ultimately
the contractor committed to “which” goal they were
picking as part of their value added. A full list of NREL’s
RSF performance parameters can be found in the side-
bar “Aligning Program Metrics With the Energy Goal,”
(Page 14) and is discussed in the NREL case study.
4. Assemble the request for proposal document. The
owner must develop a clear, comprehensive RFP docu-
ment when soliciting the design-build teams for the
project. The program metrics, energy target definition,
and project goals are clarified within the framework
of their traditional RFP document. The importance of
establishing this methodology within the RFP is critical
to the project’s success. Energy performance analysis
and presentation can vary widely from one design team
to the next. By establishing a protocol for the base sup-
porting documentation, the design teams can commu-
nicate on common terms while still demonstrating their
unique value proposition for the project.
5. Invite design-builders to propose solutions that
best achieve the prioritized requirements. As seen in
the case studies, using a design competition is the most
effective approach for selecting the project team since it
allows the owner to select the team that best meets proj-
ect requirements. Using this approach the teams com-
plete project submittals and in-person interviews that
outline their proposed approach for meeting the project
goals. Each submittal is then reviewed for typical pro-
curement requirements and the energy performance
criteria. Does the team fully understand the energy
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A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 51 8
performance criteria? Do their submittals reflect the
experience needed to achieve the target? Does the stated
energy use represent a realistic solution? It is critical
that the review include an apples-to-apples compari-
son of the team’s energy models in relation to the stated
energy performance. This review can be completed by
in-house staff or an independent, third-party consultant
familiar with design and procurement practices.
6. Review the energy analysis throughout project
life. Once the winning team is selected, the design pro-
cess moves quickly into design development. Much of
the idea creation and collaboration already occurred
during the competition phase. The owner goals are
already aligned with the project team’s approach. Now
the project can immediately start to bring the solutions
to life. A primary change now is that the energy goal is
communicated as often as the budget and timeline, per-
haps more. It is reviewed and updated throughout the
entire project life, from RFP to substantial completion.
When project requirements and decisions are needed,
the owner and team now ask: 1) does it fit in the budget,
2) does it affect the construction schedule, and 3) how
does it impact our final, absolute energy performance?
Typically, only the first two are measured, now all three
will be. Does this change the answer?
7. Measure the energy performance after substantial
completion. Establishing the energy target ensures that
the building begins on a high performance path. The
RFP should also specify a predefined period when the
owner and design/construction team review the actual
building energy performance (i.e., 12 to 18 months).
While performance is likely measured during the entire
period, this stipulation provides a contractual hand-
off where the owner’s facility staff continues the high
performance of the building. This period can provide
a milestone for any incentive- or retainer-based provi-
sions stated within the contract. It also provides a great
transition point toward monitoring-based commis-
sioning or other continuous maintenance programs.
From a QAQC standpoint, it fine-tunes quality control
TECHNICAL FEATURE
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A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 52 0
throughout the process since the team knows that the
model had to represent the as-built condition. This cre-
ates an effective commissioning and checking process by
using one simple, measurable step.
Future of Performance-Based DesignInnovation arises when adversity, challenge, and great
potential co-exist. These factors present the greatest
motivation to change. When will the design and con-
struction industry innovate to go beyond ‘what we did
the last time’ and move toward grounded, tangible and
accelerated goals? The case studies here reflect many
success stories and lessons learned. The U.S. Army Corp
of Engineers in Seattle also saw great success using a
similar approach in their recent project.3 What innova-
tion can your team bring to your next project?
Case Study: University of Chicago Campus North ResidenceHall and Dining Commons
The University of Chicago is located eight miles
south of downtown Chicago in Hyde Park. The campus
includes around 160 buildings representing 15 million
square feet. One of the newest buildings will be the
Campus North Residence Hall and Dining Commons
(CNRHDC), an 800 bed, 390,000 ft2 (36 232 m2) dor-
mitory and dining hall that will open in Fall 2016. The
building is notable as being the first on campus to have
a contractual performance goal specified as a site EUI
(kBtu/ft2·year) energy target.
There were many reasons that led to the decision to
establish an energy target for the UChicago project.
A study on the long-term planning for the campus’
historic quadrangle led to important concepts such as
a focus on maintainability, comfort, and energy per-
formance. The university’s climate and energy plan is
focused on reducing campus greenhouse gases. One
consideration for the plan is new construction, which
is estimated to substantially increase the overall cam-
pus size during the next 30 years. Establishing energy
targets for new construction helps mitigate the risk
on energy use and greenhouse gas generation for the
campus. Furthermore, UChicago students will call
this building home and they are interested in more
energy-efficient buildings on campus. These dispa-
rate items culminated in the university asking the
question: “Why not set an energy target for the new
residence hall?”
The energy target selection was a multiphase process
that involved referencing the EPA Target Finder, exist-
ing UChicago campus buildings, peer universities’
building data, and developing a preliminary energy
model for the project. Analyzing similar buildings
on campus helped to establish our current baseline.
Analyzing CBECS data through EPA Target Finder
informed the university of current “best in class”
dorms. For example, a site EUI of roughly 85 kBtu/
ft2·year (965 MJ/m2·year) is needed to receive Energy
Star certification. The university also partnered with
the Energy Center of Wisconsin and local electric utility
energy efficiency program (ComEd New Construction
Service) to develop a preliminary energy model for the
building to demonstrate what energy performance was
realistically achievable.
After the energy target scoping study was performed,
the energy target for the residence hall was set at a
site EUI of 65 kBtu/ft2·year (738 MJ/m2·year). An addi-
tional wrinkle was added by allowing two parameters
to alter the energy target. First, the target can increase
or decrease linearly based on the number of occupants
and also the size of the facility. This was done to allow
the design team an increased allocation of energy use if
they were more efficient with space planning. Second,
if the design team chose to use on-site boilers instead of
campus steam, or if the design included a geothermal
system, the energy target would drop by 10 kBtu/ft2·year
(114 MJ/m2·year).
With the energy target established, the university
issued a request for qualifications to 22 architects and 10
contractors with instructions to assemble design-build
teams. Four teams were selected to complete a schematic
design and compete for final selection for the building
design. One concern was that a hard energy target would
stifle the architectural design, and result in four similar
looking buildings. Fortunately, the competition resulted
in four unique designs, all with modeled energy perfor-
mance less than 55 kBtu/ft2·year (625 MJ/m2·year). From
this process, the university selected one design-build
team and is now in the final phase of design.
ReflectionsThis process has been an engaging endeavor for the
University. The ability to cite one specific number
required for energy performance proved powerful.
For example, at one meeting, the electrical engineer
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described various methods to control the hallway
lighting while referencing the impact on the energy
target. The client made a decision to go with the
most efficient method, because they had an under-
standing of impact on the energy target and could
weigh that against other factors involved in the deci-
sion process.
The performance target ideally results in an energy
model that is more accurate compared to a traditional
energy model developed for tax deductions or green
building compliance. It represents the building as
designed, updated to reflect actual equipment selec-
tion, and is followed up with a measured outcome. As a
result, the building energy use and major end uses will
be known. This will aid
in identifying any drift in
the expected performance
and the root cause of the
degradation.
In the end, though the
design and construction
represents a multi-year
process, it pales in com-
parison to the amount of
time the building will ulti-
mately stand. The simple act of establishing a realistic
but challenging energy target will result in a tremen-
dous amount of energy and greenhouse gas savings for
the university over the next 50 plus years.
Lessons Learned• Occupant plug loads are a large component of en-
ergy use. It will be crucial to educate students and staff
on this impact and help them understand actions they
can take to reduce energy.
• Considerations need to be made on how to accom-
modate future renovations in a building that has a very
specific energy use target.
• It is crucial for the owner to inform designers what
diversity factors and schedules are to be used for the
plug loads and lighting. Everyone will then be using the
same assumptions. This can be adjusted at a later time if
required as the design solidifies.
• The energy target should be repeatedly communi-
cated to the design team. It is crucial for them to under-
stand the importance especially as new subcontractors
are brought on.
Case Study: NREL’s Research Support FacilityThe National Renewable Energy Laboratory (NREL) is
a national laboratory of the U.S. Department of Energy
(DOE). NREL has a long track record in research related to
building energy efficiency, especially in low-energy whole
building design and zero-energy buildings. NREL facilities
has embraced NREL’s mission creating world-class labora-
tories and support facilities that minimize energy use.
While NREL set energy goals for its projects, design
teams often struggled with meeting the goals within a
cost target. NREL was often left to prioritize program-
matic versus energy features in order to meet budgets.
The goal was to engage the design team and the contrac-
tor to achieve programmatic and energy goals without
exceeding fixed budgetary
ceilings.
NREL had created sev-
eral low-energy labora-
tory buildings, lessons
learned from previous
projects helped cre-
ate a procurement and
management strategy
to achieve very low
energy buildings without
increasing the construction budget.
The solution is to align all the people involved in a
project around a common goal. It was estimated that
1,000 people had some level of decision-making impact
on the delivery of the building. These people include the
owner, architect, contractor and their trade sub-con-
tractors, a subset of the occupants, and the engineers.
The key is to find a method to motivate the decision
making process and align everyone to the same goals.
NREL chose to use a performance-based design-build
strategy for the RSF project. NREL would engage a con-
tractor who would be solely responsible of the design
and delivery of the project and hold them accountable
for achieving project goals, including energy. To start,
NREL prepared a “Request for Proposal” document that
captured all project aspects and expressed them as per-
formance criteria with no prescriptive solutions.2
The heart of the proposal was a prioritized list of project
goals. Through a facilitated process, the owner team (made
up of individuals from across the organization) created
the prioritized list which contained divisions of “Mission
Critical” (items that must be completed), “Desirable,” and
National Renewable Energy Laboratory Research Support Facility.
Den
nis
Sch
roed
er /
NR
EL
TECHNICAL FEATURE
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A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 52 4
completed), “Desirable,” and “If Possible.” There were
entries about building function, sustainability, safety,
and energy to name a few. The RFP and the prioritized
list represented the voice of the owner. It was agreed
early on that this document would not conceptually
change and that when questions arose, the RFP would
be referenced. A NREL Project Manager would be
responsible for implementing the RFP without change.
It was key that the owner did not change the prioritiza-
tion during the entire building delivery process.
A short-listed group of contractors competed and
their conceptual designs were evaluated on the ability
to achieve the prioritized list in order given a constraint
of a fixed price. Conceptually, this was the wish list and
selection would be made on who provided the most
value. While the project did not start out to be a zero-
energy building (ZEB), the successful bidder showed
that they could deliver the project with the potential
to be zero-energy within the budget ceiling. As seen in
the sidebar, “Aligning Program Metrics With the Energy
Goal,” the ZEB goal was quite far down the list.
To be successful, the contractor’s team relied heavily
on strong communication and management skills to
drive the process. At the proposal stage, the contractor
engaged an energy modeler to help inform the concep-
tual design required by the proposal. This helped fold
the energy features into the architecture and the func-
tion of the building—leveraging those costs. As the proj-
ect progressed, the sub-contractors were critical to pro-
viding innovation around controlling costs. Repetition
was a key element which factored into the design. The
building was built around a standard module with pre-
cast insulated concrete panels including the windows.
The efficiency around the thermal envelope, coupled
with the daylighting enabled the use of radiant heating
and cooling in the ceiling slab—and an innovative tech-
nique of placing the tubing provided a cost point that
was achievable on the building’s budget.
The end result was a Phase 1 project (240,000 ft2 [22
297 ft2]) that uses half the energy as a traditional build-
ing producing as much energy as it consumes, includ-
ing the corporate data center located in the building
TECHNICAL FEATURE
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A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 52 6
at a cost of $259/ft2. This figure is in the lower third of
commercial office buildings built in the region during
this time period. Using a similar process, Phase 2 added
120,000 ft2 (11 148 m2) cost less per square foot, and has a
higher energy performance. A parking garage also used
the same process, except the energy goal was expressed
as energy per parking space, rather than normalized on
area and building occupancy.
Lessons Learned • In a traditional project, the owner often has to make
decisions about the projects goals during the process. In
this case, those decisions were made based on perfor-
mance criteria before the design started. The success-
ful bidder voluntarily achieved all items on the wish
list; this indicates that they could have been longer and
included more levels of energy efficiency. The benefit of
this is that owners need not determine the energy goal;
it is established by what the market can bear.
• The owner can successfully use voluntary incentives
that are prizes, that is, not tied to a deliverable. If you
do everything in the RFP, you have “acceptable” perfor-
mance; anything beyond that is “superior performance”
and can be rewarded through a voluntary program.
• The owner, independently, needs to create a set of
plug loads and plug load profiles that will govern the
project. The owner needs a strategy to achieve these loads
as well as lighting schedules. For NREL, the plug loads are
higher at night than predicted, but lower in the daytime.
Nighttime lighting loads were not accurately predicted.
• The contractor and owner need to constantly be re-
minded of the RFP requirements. Use this document as the
ultimate reference without variation. As mentioned earlier,
the owner cannot change her mind during the process.
References1. Pless, S., P. Torcellini, D. Shelton. 2011. “Using an energy perfor-
mance based design-build process to procure a large scale low-energy building.” ASHRAE Winter Conference. http://tinyurl.com/md6ts2z.
2. NREL. 2008. “NREL research support facility, request for pro-posal: solicitation No. RFJ-8-775500.” National Renewable Energy Laboratory. http://tinyurl.com/laowq9s.
3. AIA. 2013. “Federal Center South Building 1202.” The Ameri-can Institute of Architects. www.aiatopten.org/node/204.
TECHNICAL FEATURE
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TECHNICAL FEATURE
Philip Bartholomew, P.E., is a senior mechanical engineer at Miller-Remick in Cherry Hill, N.J.
BY PHILIP BARTHOLOMEW, P.E.
Hospital operating room operating room operating HVAC systems require high quantities of circulated of circulated of air tomeet ASHRAE Standard 1701 and the non-aspirating flow non-aspirating flow non-aspirating requirements flow requirements flow of the of the of oper-ating room.ating room.ating The typical HVAC system is highly ineffective, highly ineffective, highly in terms of energy of energy of use, energy use, energy atmaintaining themaintaining themaintaining desirable temperature and humidity conditions humidity conditions humidity of the of the of space. Thisarticle will demonstrate that a version of a of a of dual duct HVAC system will save consider-able amounts of operational of operational of energy compared energy compared energy to the standard system.
The typical HVAC system used in operating rooms can
be described as a single duct, VAV reheat system (Figure
1). A better description is a two position, constant volume
reheat system. The system delivers a constant 20 ach to
the operating rooms when they are occupied. A higher rate
is required if the cooling load dictates or if a special airflow
condition is required by the operation being performed.
During unoccupied periods, a constant minimum airflow
is required to maintain operating room pressurization.
The constant volume reheat aspect of this system has
historically been recognized as an energy inefficient
system. However, the high airflow requirements of the
operating room makes these inefficiencies far greater
than those that occur by oversizing the system above
what is required to meet the space cooling load.
Note that the dual duct system in Figure 2 has two sepa-
rate air tunnels and two separate banks of supply fans.
This is required to achieve the energy savings of the sys-
tem and to allow for an arrangement that locates the sup-
ply fan between the cooling coil and the final HEPA filters.
Placing the fan in this position allows the fan heat to be
added to the nearly saturated air leaving the cooling coil
and eliminates biological growth in the HEPA filters.
The dual duct system could be based on a single cus-
tom rooftop unit incorporating all components shown
in Figure 2. Alternately, the system could consist of a
separate cooling air-handling unit, a heating air-han-
dling unit and a heat recovery minimum outside venti-
lation air package. The configuration can be tailored to
suit the actual physical requirements.
The two fan arrangement of the system shown in Figure
2 is considerably different in configuration and operat-
ing characteristics than a dual duct unit with a single
blow-through fan. In the single fan system, the air path
TECHNICAL FEATURE
Energy-Efficient ApproachEnergy-Efficient ApproachEnergy-EfficientForFor Operating OperatingFor OperatingForFor OperatingFor Rooms Rooms Operating Rooms Operating Operating Rooms Operating
A P R I L 2 0 1 5 a sh r a e . o r g A S H R A E J O U R N A L 3 1
TECHNICAL FEATURE
VAV System OperationThe VAV two-position system produces about 54°F (12°C)
supply air (50°F [10°C] coil leaving temperature plus 4°F
[2°C] fan heat) 24 hours a day, all year, to be distributed to
the VAV reheat terminals. During the unoccupied periods,
when the space humidity requirements can be relaxed,
the discharge temperature can be reset to 60°F (15°C). The
quantity of supply air is generally 20 ach during occupied
periods and 10 ach during unoccupied periods.
With the VAV two-position system providing more air
to the space than required to meet the heat load, the
temperature of the space would be lower than desired.
Reheat is introduced to maintain the space temperature
setpoint. The reheat quantity would be zero if the cool-
ing capacity of the supply air at 54°F (12°C) exactly meets
the cooling requirements of the space. This is, however,
almost never the case.
The design cooling load of the typical (not robotic or
hybrid) operating room requires only about 12 ach of cool-
ing capacity to maintain a general operating room tem-
perature of 65°F (18°C). Also, this is the design heat load
with all equipment in operation at nameplate capacity.
There is some diversity, over time, of this equipment load.
An even larger factor in reducing the average heat load
from design is that the operating room is not in use for
a large portion of the occupied period and the only heat
load may be the small load of the general lighting.
When the space equipment heat load is not equal to
the cooling capacity of the supply air, all the difference
in capacity must be offset with reheat to maintain space
temperature. To meet the actual cooling load of the
space, extra cooling energy is spent to cool all the air cir-
culated and then reheat is added back into the airstream
to compensate for the overcooling of the supply air. The
sum of the overcooling and subsequent reheating is
more energy than the actual cooling load of the space.
Dual Duct System OperationAs stated earlier, the design of the two fan dual duct
system leads to the cooling capacity matching the heat
load of the spaces and requires no reheat to maintain
space temperature in most cases. Both the VAV and dual
duct systems require approximately the same amount
of fan power since both require 20 ach of circulated air
during occupied periods.
There are some savings in supply fan power of the dual
duct system since the two air tunnels operate at part
FIGURE 1 VAV air unit.
Economizer
Minimum OA
Cold Supply
55°F
Return Air
H H
C
C
C
Fans HEPA
M
M
M
M
FIGURE 2 Dual-duct air unit.
Economizer
Minimum OA
Cold Supply
55°F
Return Air
H
H C
C
C
Fans HEPAM
M
M
M
Smoke PurgeRecirculated Air
(Neutral Temperature)
72°F
Service AccessMM
MFans HEPA
M
Heat Wheel
H
Air Blender
diverges after the fan into a separate cold
deck and hot deck. The single fan system
generally requires active heating of the hot
air deck, mixing of hot and cold airstreams
at the terminal and allows air that is not
dehumidified to enter the space through
the hot deck.
A discussion of the minimum outside air
portion of the two fan dual duct system,
the function of the air-handling unit warm
deck heating coil and terminal reheat coil
will follow later after the establishment of
the energy use advantages of the system.
With the two fan dual duct system, the
cold deck produces only the amount of
cooling supply air needed to meet the load
requirements of the spaces. The remain-
der of the supply air quantity required to
meet the minimum airflow requirement
is recirculated, HEPA-filtered air from the
warm deck of the unit. Note the heating
coil in this air tunnel is not energized for
the vast majority of system operation.
CC
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capacity almost all of the time. As a
result, there will be a reduced pres-
sure drop that the fans must work
against compared to the VAV system.
The savings in the supply fan opera-
tion more than offset the additional
energy required to operate the fans
used for heat recovery. Also, within
the air-handling units there is an
almost equal amount of cooling
energy expended to overcome the
heat associated with the system fans
compared to the VAV system.
The minimum outside air system
for the dual duct system has a total
energy heat wheel and a chilled
water cooling coil to precondition
the ventilation air delivered to the
unit decks. As described later, this
is required for proper operation of
the dual duct system, but not for the
• The operating suite was con-
sidered a totally interior space with
no wall, window or roof thermal
loads.
VAV system. The savings in thermal
energy associated with this require-
ment is seen in the energy analysis
comparison.
Comparison Of Energy RequirementsThe energy analysis comparing
the two systems was performed for
a surgery suite replacement project
in western North Carolina. The suite
consisted of seven operating rooms, a
perimeter corridor, sterile supply and
storage spaces. The total floor area of
the operating rooms is 4,900 ft2 (455
m2), and the area of the other spaces
is 4,300 ft2 (390 m2). The AHU system
capacity was approximately 26,000
cfm (12 270 L/s).
For the comparison the operating
room parameters required for both
systems are as follows:
FIGURE 3 System energy use requirements at air-handling unit for 75°F average temperature.
Dual Duct System VAV Reheat
System
Distribution Cooling CapacityReheatFan EnergyCooling to Offset FanOA Conditioning
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rooms was assumed to be 65% of that time, and the sup-
ply air circulation was 20 ach to operating rooms that
were actively in use, and 10 ach when not actively in use.
• Clean up was assumed to be from 3 to 5 p.m. During
this period, the supply air circulation to the operating
rooms was 10 ach.
• The operating suite was assumed to be in unoc-
cupied mode from 5 p.m. to 6 a.m., Monday through Fri-
day and all weekend. During this period, the ventilation
air at the air-handling unit was shut off, the VAV unit
TABLE 2 Component cost difference in terms of increase for dual duct system.
Warm Deck Air-Handling Unit and Controls $120,000
Heat Recovery Package and Controls $15,000
20 ton Reduction in Air Cooled Chiller Capacity ($40,000)
Heating Hot Water Generation ($32,000)
Hot Water Distribution Piping Cost ($29,300)
Added Cost of Ductwork $20,000
Total Differential Cost $53,700
TABLE 1 Yearly energy requirements for systems.
DUAL DUCT VAV (TWO POSITION)
Cooling Energy (MMBtu) 364 898
Fan Energy (MMBtu) 443 489
Reheat Energy (MMBtu) 0 420
Humidification Energy (MMBtu)
31 57
Total (MMBtu) 838 1,864
discharge was reset to 60°F (18°C) and the circulation
rate to the operating rooms was 10 ach.
• No operating rooms had robotic or hybrid equip-
ment loads for this simulation.
Figure 3 shows a comparison of the total energy
required to operate the VAV and the dual duct systems
during a week when the average temperature was 75°F
(24°C)—85°F (29°C) daytime and 65°F (18°C) night-
time. This ambient temperature was chosen to better
demonstrate a more complete load on the heating and
• The operating suite was as-
sumed to be in occupied mode from
6 a.m. to 5 p.m., Monday through
Friday. The suite was provided full
ventilation air during this time and
the VAV and dual duct system cold
deck supply air temperature was
54°F (12°C).
• Operations were potentially
performed from 6 a.m. to 3 p.m.
The actual use of the operating
TECHNICAL FEATURE
A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 53 4
cooling utilities. At lower temperatures, the econo-
mizer cycle reduces or eliminates the refrigeration
requirements of both systems. The period of one
week was chosen to fully account for the influ-
ence of the unoccupied mode of operation of the
systems. The energy use is expressed in energy
requirements at the air-handling unit with no
accounting of the chiller plant COP and the effi-
ciency of the boiler plant. The following observa-
tions can be made:
• The cooling energy required to condition the
outside air was reduced with the heat recovery sec-
tion of the dual duct system. Although not minor,
this reduction was not responsible for the major-
ity of the savings associated with this approach.
downsized to a small degree. For the cost comparison,
this difference was not taken into account.
• The warm deck of the dual duct system was an
additional cost and consisted of a separate additional
air-handling unit.
• The minimum outside air system for the dual duct
system was a packaged system with supply and exhaust
fans, total energy wheel and cooling coil sized for 4,000
cfm (1900 L/s).
• The project required an air cooled chiller needed
for central plant back up capacity. This chiller was to be
placed on emergency electrical power.
• A steam to hot water heat exchanger and distribu-
tion pumps were required to provide heating hot water
to the VAV system reheat loads.
Also it was desirable for maintenance purposes to have
the distribution terminals next to the air-handling unit.
This helped keep the cost increase of the added duct
associated with the dual duct system minimized. The
supply duct from the VAV or dual duct terminal to the
space is the same for both systems.
Table 2 shows component costs that differ between the
dual duct and VAV systems. Component costs such as
the return air components and the supply components
downstream of the terminal are the same for both sys-
tems and are not included below. The cost difference
is stated in terms of increased cost of the dual duct
system.
The simple payback of the dual duct system for this
project is four years. Differences in the control strategy
of the VAV system and the use of more outside air can
drastically shorten the payback period. Also, differences
FIGURE 4 Dual duct terminal controls.
FT
FT
M
M
T
TT
Space Temperature Sensor
To SpaceDual Duct Terminal
Reheat (Only for High Heat External Zones and ORs That Require Warm Up)
Conditioning of outdoor air occurs in the main cooling
coil of the VAV system. The latent heat transfer of the
dual duct system’s heat wheel also reduces the amount
of winter humidification.
• The fan energy requirements for both systems is ap-
proximately equal. This is because the savings due to the
dual duct component pressure drop at part flow capacity
more than offsets the additional power requirement of
the heat recovery fans. Also, the cooling energy needed
to compensate for the fan heat is nearly equal in both
systems.
• The VAV system’s distributed cooling capacity and
required reheat energy is very large: subtracting the VAV
reheat quantity from the cooling capacity equals the
cooling capacity of the dual duct system.
The results in Figure 3 are for one week. This data
extrapolated for one year is shown in Table 1.
With estimated utility rates of $0.09/kW for electric-
ity and $9.00/mcf (thousand cubic feet) of gas, the
estimated annual energy cost for the dual duct system
is $21,100 per year and $34,500 per year for the VAV
system.
System Construction Cost Comparison and PaybackA cost comparison of the systems was performed based
on the specific needs of the project. The needs of the
project and the assumptions taken are as follows:
• The cold deck of the dual duct unit consisted of a
separate air-handling unit with approximately the same
cost as the VAV system air-handling unit. The dual duct
cold deck air-handling unit is actually less expensive
because it does not require a heating coil and can be
TT – Temperature TransmitterFT – Flow Transmitter
TECHNICAL FEATURE
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A P R I L 2 0 1 5 a sh r a e . o r g A S H R A E J O U R N A L 3 5
in construction costs to suit actual project conditions
and requirements will affect the payback period.
Dual Duct Terminal ControlThe dual duct terminal schematic is shown in Figure
4. For the surgery rooms and other flow/pressure criti-
cal areas, the control systems of a standard commercial
terminal should be replaced. The flow quantities through
the cold and warm inlets to the terminal will have a large
variation from near zero flow to full flow. To get accurate
flow over this range, it is necessary to use a flow sensor
such as a thermal dispersion element as opposed to the
terminal-supplied flow cross or flow ring sensor. This will
provide an approximate accuracy of 3% over the range
and will provide good pressure control of the room.
For temperature control, a discharge temperature sen-
sor is used because the supply air from the terminal is
delivered directly onto the patient. This approach allows
the space temperature sensor to reset the discharge con-
trol setpoint for a less drastic reaction to space condition
changes and changes in temperature setpoints. The
control of the terminal requires the cold airstream be
throttled to match the cooling setpoint of the terminal
discharge sensor. The flow quantity of the cold airstream
is measured and the warm airstream is throttled so that
the sum of the cold and warm airstreams meets the flow
requirements of the space.
An auxiliary reheat coil may be desirable for spaces
with an exterior skin load or an operating room that may
need a quick warm up of the space during the operation,
such as a cardiac operating room .
Commercial terminal controls are applicable for areas
where the strict flow control of the operating rooms is
not required.
Outside Ventilation AirBecause the blend ratio of the two airstreams into the
terminal unit will vary greatly, care must be taken that
the minimum ventilation quantity delivered to the space
is met. The method implemented in Figure 2 is to bring in
a fixed minimum quantity of outside air at the air-han-
dling unit. This quantity is proportioned to the warm
TECHNICAL FEATURE
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and cold system airstreams based on the supply airflow
of that airstream. This ensures that each airstream has
an equal percentage of ventilation air.
The recirculated air being delivered from the warm
deck is not cooled and therefore not dehumidified by
the components of that deck. The outside air must be
cooled and dehumidified before it is delivered to the
warm deck to maintain dehumidification of all air
delivered to the space. For this function, a heat recov-
ery wheel and cooling coil are used to precondition the
outside air before being delivered to both the cold and
warm decks.
Warm Deck Heating Coil OperationThe heating coil in the warm deck is not generally
required for normal operations of the unit. It is required
for the space smoke evacuation mode .
During smoke removal, the air is not returned from
the spaces and is exhausted. The unit switches over to
100% outside air to make up the exhausted air. The heat-
ing coil must bring potentially cold air up to comfort
conditions until patients in other operating rooms of the
suite can be evacuated.
In normal system operation, if a majority of the operat-
ing rooms are operated at a low temperature, the average
return air temperature combined with the cool minimum
outside ventilation air may not meet warm air tempera-
ture requirements of spaces with a higher temperature
setpoint. It may be desirable to have the minimum heat-
ing coil leaving temperature set at 72°F (22°C).
For morning warm up periods, this setpoint can be
increased to 75°F to 80°F (24°F to 27°C). Note that during
the warm up and normal system operating periods the
heating capacity is far smaller than during the potential
smoke removal operations. Two widely varying sizes of con-
trol valves (not just a two-third to one-third split) should be
considered for stable system temperature control.
Existing System Replacement/ModificationsIf an existing VAV air system that uses the present
standard of 4 ach of ventilation air (approximately
20% of supply), is in place and is at the beginning of its
TECHNICAL FEATURE
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service life, the payback of replacing the system does
not justify changing to a dual duct system. However,
some modifications can greatly affect the operational
costs associated with this system. Some suggested
modifications include:
• Apply occupancy sensors in the operating rooms so
the space has the “occupied” amount of supply air only
when the space has an active operation in process. This
can be done on a space-by-space basis for most systems
and the air-handing unit should be able to respond to
the different capacity requirements.
• Reduce the “unoccupied” airflow requirements
to those required to maintain operating room pres-
surization. During the unoccupied period, return air
from the operating room can be shut off and all system
return can be from the adjacent spaces. Take care to
ensure the fans of the system will remain stable at this
low airflow.
• Disable hot water to the reheat coils of the sys-
tem terminals during unoccupied periods. This will
eliminate the “fighting” of the cooling and heating
components of the system. The space temperature may
get cooler than desirable during unoccupied periods.
System “occupied mode” start up 30 minutes before an
operation begins will result in the reestablishment of
normal temperatures.
• Shut down or reduce the outside air ventilation
quantity during unoccupied periods.
• Reset the supply air temperature to 60°F during
unoccupied periods.
Many of these modifications address the unoccupied
operation of the system. It is important to realize that
the system operates in the unoccupied mode about
two-thirds of the time of yearly operation, and making
the changes will have a large yearly savings.
If an existing system was designed to meet older
standards requiring 100% outside air, this system is
considerably less efficient than the VAV system used
as the basis of the analysis above, even if it has a form
of sensible heat recovery. Investigation of replacing
or modifying this system in the near future should be
considered.
TECHNICAL FEATURE
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It is possible to add a recirculating warm deck
air-handling unit to an existing VAV air system and
change out the terminals from single duct reheat to
dual duct terminals. This approach is more feasible
if there is space for the warm deck air-handling
unit and the distribution terminals are in an easily
accessible location. Also, careful evaluation of the
existing VAV unit fan capacity turndown should be
investigated.
Consideration must account for the additional space
requirements of the dual duct system in a retrofit situa-
tion. Possible solutions may include stacked air handlers
or rooftop equipment.
In the evaluation of replacing the existing oper-
ating suite system, credit savings in the hospital
infrastructure capacity to the replacement system.
Considerable savings in boiler and chiller plant
capacity will be achieved and this capacity will be
available for future additions and renovations. The
operating suite needs to be supported by utilities
that are on emergency power and this may relate to
further infrastructure savings.
Also, if the central plant capacity is judged to be
marginal, replacing the operating room system may
be a better solution than increasing the capacity of the
plant.
ConclusionsIt has been demonstrated that the energy demands of
an operating room HVAC system can be mitigated by a
dual duct air system, as compared to a well-controlled
conventional VAV two-position system.
The proposed dual duct system has a higher installed
cost, but will provide a favorable payback for many
applications.
The changing of the paradigm of what is the optimum
system to be applied to the operating room is one of the
changes required to address the high energy require-
ments of the hospital.
References1. ANSI/ASHRAE/ASHE Standard 170-2008, Ventilation of Health
Care Facilities.
TECHNICAL FEATURE
A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 54 2
BUILDING AT A GLANCE
AntarcticaEmpire of the Penguin
Location: Orlando, Fla.
Owner: SeaWorld Parks and Entertainment
Principal Use: Theme park attraction
Includes: Dark ride and penguin exhibit
Employees/Occupants: 300
Gross Square Footage: 66,990
Conditioned Space Square Footage: 66,990
Substantial Completion/Occupancy: April 2013
Occupancy: 75%
William C. Weinaug Jr., P.E., is an executive vice president at exp in Maitland, Fla. He is a member of ASHRAE’s Central Florida chapter.
FIRST PLACECOMMERCIAL BUILDINGS, EXISTING
When creating a 32°F (0°C)
space in hot and humid
Orlando, the efficiency of the
systems and envelope is cru-
cial. The facility is designed to
minimize energy use while pro-
viding a habitat for penguins to
thrive.
2015 ASHRAE TECHNOLOGY AWARD CASE STUDIES
BY WILLIAM C. WEINAUG JR., P.E., MEMBER ASHRAE
AntarcticaEmpire of the Penguin
Antarctica: Empire of the of the of Penguin is an immersive darkride and penguin exhibit. The 30,000 ft2 (2787 m2)project was a renovation and addition to the existingPenguin Encounter building at building at building SeaWorld Orlando.
Guests enter the facility through facility through facility a pre-show theater, pre-show theater, pre-showpass into a rock and ice themed queue, and exit thequeue through a small “ice den” to load onto a uniquetrackless ride system. The vehicles move through vari-ous scenes, including a including a including large theater space, ending at ending at ending anunload platform inside the frozen penguin exhibit. Theadventure concludes in an underwater viewing area. viewing area. viewing
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2015 ASHRAE TECHNOLOGY TECHNOLOGY AWARD CASE STUDIES
ABOVE Ride load and initial scene.
LEFT Liquid desiccant units dehumidify the ride areas.
The design team was tasked with several engineering
challenges to make the exhibit ideal for the animals and
enjoyable for the guests:
• Maintain animal health through temperature, air
quality, filtration, and pressure relationships;
• Moisture control;
• Odor control; and
• Energy efficiency.
Animal HealthAnimal comfort and health were the main key perfor-
mance indicators for the design of the HVAC systems
with indoor air quality being the most critical. Penguins
are susceptible to aspergillus and other molds and fungi
that are common in our environment but not theirs. The
design uses high level filtration, airflow patterns, and
space pressure relationship to keep the bird’s environ-
ment healthy.
There are only a few exhibits in the world that allow
the face-to-face interaction that was incorporated
into this exhibit. Guests are first washed by clean air
as they enter the facility. Specific fresh air exchange
rates are maintained for the animal areas. All fresh
air delivered to the exhibit (either directly or through
any possible infiltration) is HEPA filtered. HEPA level
filtration along with a non-homogeneous electri-
cal field system are provided in rooftop air handling
units that recirculate the air in the space. In addi-
tion, there are specific space pressurization measures
that control where air is allowed to enter the animal
spaces.
Moisture ControlThe HVAC cooling coils required to maintain the
spaces below freezing temperatures, used a 15°F cool-
ing fluid. Constructing a proper envelope around these
spaces minimized the infiltration of potential moisture
into these cold spaces.
• Due to the large temperature and humidity level
differences across the envelope, the vapor drive is
significant. Creating a tight sealed barrier around the
low-temperature exhibit was imperative.
• Guest entry and exit points had to be controlled.
Sally port vestibules with special door controls were
incorporated into the design to allow guests to easily and
comfortably enter the exhibit while revolving doors at
the exit protect the underwater viewing area.
• Fresh air supply is pre-conditioned by an active
desiccant system. This very dry fresh air helps to lower
the humidity levels in the exhibit space.
Envelope. Early in design, a good envelope was iden-
tified as an important requirement to minimize the
sensible and latent loads and to curtail potential issues
with condensate. Detailing to minimize even the small-
est potential leak through this envelope is critical. If
moisture is allowed into the wall system, ice will form,
causing damage. Where ice doesn’t form, condensation
will form, and, over time, likely cause mold and mildew
growth.
The design team recommended the insulation/
vapor barrier envelope be built outside of the build-
ing structural frame of the cold penguin exhibits,
to provide a cocooning envelope surrounding the
cold space and eliminate the majority of the thermal
bridge issues. Where thermal bridges could not be
eliminated (as with the acrylic viewing panels and the
mechanical space where the HVAC units are located),
the dew-point temperature on the warm side had to
be controlled so that condition condensation cannot
form.
Sally Ports. The design team worked with the sto-
rytellers and show designers to ensure the integrity
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of the envelope was maintained while allowing thou-
sands of people to flow into the exhibit daily. This
included the use of sally ports and quick acting doors
to help keep the cold in the building and moisture
out.
An important part of any themed attraction is provid-
ing a comfortable flow for guests into and out of the
exhibit area. This design called for a large vehicle capa-
ble of carrying eight people into the exhibit. We identi-
fied early on that the ride area would have to be at the
same dew point as the exhibit. The design team incorpo-
rated the use of a series of sally port spaces into the guest
experience. The first sally port is camouflaged as a the-
ater space that allows guests to enter from outdoors. As
the presentation in this theater begins the outdoor sally
port closes, and the space humidity is rapidly dropped
though Cromer cycle chilled water air-handling units.
These units are sized to allow the space to reach a design
dew point by the time the interior doors open to a queue
space.
Unlike typical spaces where temperature is most
important, the queue, ride and underwater viewing
exhibit spaces required strict control of their dew
points. Strategically located self-contained liquid
desiccant air-conditioning units and Cromer cycle
chilled water units were used to effectively con-
trol the space dew point (i.e., no added energy for
reheat).
Fresh Air. The most significant load in the exhibit
space is the fresh air load. With the fresh air delivery
systems there are significant associated first cost and
operating cost considerations. Because these spaces
are very dry (i.e., very low dew point) and the outdoor
air in Orlando is very hot and humid, a tremendous
amount of work has to be done on the ventilation air
supplied.
The design team recommended the use of a heat acti-
vated desiccant system, which can easily dry the wet,
hot fresh air. Sensible, latent, and desiccant heat recov-
ery components were incorporated into this process to
recover as much energy as possible from the relief air in
the spaces. Figure 2 shows the arrangement included in
the design documents.
In Figure 2, the different components from left to right
are as follows:
• Energy Recovery Ventilator (ERV). In this first sec-
tion of the DOAS unit, the relief air passes by the fresh
air intake to pre-cool the fresh air. It is essential to get
FIGURE 1 Section through exhibit space.
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latent energy recovery since the latent cooling load is
much higher than the sensible load.
• Pre-Cooling Coil. Chilled water from the district
chilled water plant was used to cool the outdoor air
stream and raise its relative humidity prior to enter-
ing the desiccant wheel. The higher entering relative
humidity increases the desiccant dehumidification
effectiveness.
• Active Desiccant Dehumidification. An active des-
iccant wheel is next used to pull a significant amount
of moisture out of the fresh airstream. The air leaving
this section of the unit has to be very dry to keep from
freezing the 15°F (–9°C) brine cooling coil. The dryer
this air is, the less defrost will be required by the low
temperature units serving the exhibit (described later
in this narrative). The air leaving this section of the
unit is warmed by the desiccant wheel which has been
heated during the regeneration process. Note, there is
a separate side stream of outdoor air that is heated to
320°F via a gas heater to regenerate the active desic-
cant wheel.
• Cooling Coil. Chilled water from the central plant
is next used to sensibly cool the warm, but dry, fresh
airstream. This cooling could have been done by the
brine cooling coil, but it is much more efficient to use
42°F chilled water to cool the airstream prior to the
brine coil.
• Fan.
• 85% Efficient Filters.
• Brine Cooling Coil. The last cooling portion of
the unit super cools the fresh airstream to a supply
temperature to match the supply temperature of the
exhibit air-handling units.
• HEPA Filtration. High efficiency particulate filters
are required in the last section of this AHU for animal
health.
Fresh air supply is a vital component for keeping
the environment healthy, therefore we recommended
that two DOAS units be provided, each sized at the
specific air change rate required for the exhibit
spaces. Units are operated simultaneously to main-
tain the best odor control, however, if one of the units
is down for normal maintenance and/or failure, the
exhibit will still be able to function without jeopardiz-
ing animal health.
In addition to the above, specific actions to minimize
internal moisture loads had to be taken.
• Animals. Latent loads from the animals is expected
to be small.
• People Loads. Latent loads for the guests could be
large during hot, humid or rainy days. The queue areas
were designed to dry the guest prior to entering the
exhibit.
• Pools. The design required maintaining the pool
temperature at the lowest possible temperature but still
allowing optimum bird comfort and health. This helped
us to minimize water evaporation from the bodies of
water in the exhibit.
• Wash Down. The most successful approach to re-
move animal guano is through the use of high pressure
warmed water. This operation is the most significant
latent load in the space.
FIGURE 2 Dedicated outdoor air system.
ERV Pre-Cooling Coil Cooling Coil HEPA FiltrationBrine Cooling Coil
85% Efficient Filters
FanActive Desiccant Dehumidification
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causing an increase in particle size
by combining these submicron
particles. The particles both absorb
and adsorb odor. As particle sizes
increase, the HVAC filters can trap
them along with the odor. The
large recirculating air-handling
units that house these electrical
grids are located above the exhibit.
In addition to providing special
excitation technology and the high-
est level of filtration, HVAC systems
serving areas surrounding the
exhibit were fitted with titanium
dioxide catalytic filtration systems.
The design team felt employing
these two technologies would afford
us the best possible odor control
approach for the facility.
Energy EfficiencyWhen creating a 32°F (0°F) space
in hot and humid Orlando, the effi-
ciency of the envelope and the sys-
tems serving that space are crucial to
keep operating costs at a minimum.
As noted earlier, the design team’s
first task was to reduce the effect of
the outdoor conditions by ensur-
ing the coldest and driest areas (less
than 50°F [10°C]) were properly
encapsulated by a thermal panel
system with excellent insulation
and vapor barrier characteristics.
A high quality freezer panel system
was used to provide this barrier.
In addition, temperate, low dew
point zones surround the coldest
areas. Very efficient liquid desic-
cant systems with ERV (air-to-air
total energy plate heat exchangers)
perform dehumidification work in
these areas. Sally ports and revolving
doors help maintain the envelope
around the low dew point areas
while allowing thousands of guests
to enter each hour.
Light fixtures were placed outside the cold envelope to minimize heat gain in the exhibit.
Odor ControlOdor control in penguin exhibits
is often a struggle for HVAC design-
ers. Typically, animals are physically
separated from guests making con-
trol simpler. However, in this project
guests are allowed to flow freely into
and out of the exhibit through open-
ings large enough to accommodate
the ride vehicles.
Based on positive past experi-
ence, the design team recom-
mended the use of excitation
technology via a “non-homoge-
nous, in-unit electrical field” to
help control odor. Such a system
increases the rate of collisions
among the suspended particles
in the HVAC system’s airstream,
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The exhibit’s dedicated outdoor
air systems use an enthalpy energy
recovery system to reclaim as much
energy from the relief air as pos-
sible. An active desiccant wheel
ensures very dry air is supplied to
the low temperature brine cool-
ing coils, minimizing any required
reheat. The units have traditional
chilled water cooling supplied from
a very efficient district CHW loop.
The decision of the exact type of
cooling fluid to be used was crucial
to the efficiency of the systems and
the overall performance for the
building. Operating at 15°F (–9°C),
this fluid had to be special. There
were five possible methods/cooling
fluids (Figure 3) that could be used
with these air-handling units:
1. Refrigerant (either direct
expansion or liquid overfeed);
2. Ethylene glycol;
3. Propylene glycol;
4. Brine water solution; and
5. Potassium formate.
Due to the risk to the penguins’
heath if a leak occurred, the first
two options were eliminated. The
pumping energy for propylene gly-
col would be very high at 15°F (–9°C),
and the owner was concerned about
the corrosive brine system with the
fourth option. Detailed analysis
proved the potassium formate was
the most efficient cooling fluid for
this project.
The ride and queue units all use
enthalpy wheels to assist in the
dehumidification process. A heat
recovery system uses the 95°F (35°C)
condenser water return to generate
all of the hot and defrost water heat-
ing needs for the building.
Effective maintenance of a
building is necessary to achieve
designed energy savings. The
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FIGURE 3 Cooling fluid comparison.
500%
450%
400%
350%
300%
250%
200%
150%
100%
50%
0%
108%137%
256%
122% 115%
346% 361%
130%112%
426%445%
496%
142%
198%
107%
254%
gpmPressure DropPumping EnergyPipe Size
Pure Dynalene CaCl Ethylene Propylene Water HC10 Glycol Glycol (40%)
owner understood this principal and required intial
commissioning and ongoing monitoring/commis-
sioning for a period of one year after completion.
This was done to ensure the system performed as
intended. The controls programming was modified,
as needed, to optimize the systems, and we worked
with the facilities staff while they learned to operate
the building.
The greatest accomplishment of the engineering
team was the creation of a comfortable and healthy
habitat for the animals while providing an immersive
learning experience for the guests. Their experience
will foster a better appreciation of the penguins, their
environment, and its place on earth. This experi-
ence was accomplished through an integrated team
effort—from concepts through post-occupancy com-
missioning—that included the owner, the aviculturist,
the architects, ride designers, theming consultants,
structural, lighting, power, and, of course, us HVAC
engineers.
2015 ASHRAE TECHNOLOGY AWARD CASE STUDIES
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5 2 A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 5
Stephen W. Duda
COLUMN ENGINEER’S NOTEBOOK
Stephen W. Duda, P.E., is senior mechanical engineer at Ross & Baruzzini, Inc. in St. Louis.
BY STEPHEN W. DUDA, P.E., BEAP, HBDP, HFDP, FELLOW ASHRAE
In my most my most my recent Engineer’s Notebook column four months ago,1 I gave areview ofreview ofreview three of three of important safety-oriented code requirements that tend tobe overlooked in mechanical design. Reaction to that column was favorable,and I am still admittedly on admittedly on admittedly my code my code my soapbox, so I offer several more coderequirements similarly overlooked. similarly overlooked. similarly These are also critical safety- or service-related features applicable to building mechanical building mechanical building systems: code require-ments that are frequently overlooked frequently overlooked frequently by engineers, by engineers, by design-build specialists,contractors, and even code officials. These are all real examples from actualfacilities upon which I have performed property condition property condition property assessments, peerreviews I performed of designs of designs of by others, by others, by or retrofit of designs of designs of by others. by others. by
Overlooked Code Requirements
Don’t Use Corridors as an Air DuctThis is a classic blunder that I still see from time to
time; not often in large commercial or institutional con-
struction with reputable engineering and proper code
enforcement, but sometimes in light commercial con-
struction in areas with lax code enforcement. It is not
appropriate to use an egress corridor as an air plenum,
including as a path for return air.
The 2012 International Building Code2 (IBC) defines a
corridor as “an enclosed exit access component that defines
and provides a path of egress travel.” The 2012 International
Mechanical Code3 (IMC) in paragraph 601.2 states clearly
that corridors shall not serve as supply, return, exhaust,
relief or ventilation air ducts, and essentially the same clause
has appeared in previous editions and in other model codes
such as the Uniform Mechanical Code4 (UMC).
Picture an office building (Figure 1) with a corridor
down the middle, flanked by enclosed offices on both
sides of the corridor. If an air-handling unit is located
in a room adjacent to the corridor, for example, it is
unacceptable to place a return grille serving that air-
handling unit directly into the corridor wall, and use
transfer openings from each office into the corridor
proper. This has the effect of turning the corridor into a
return air “duct” in violation of this code clause.
The consequence of using this arrangement could be
dire in a fire. Were a fire to break out in, say, a trash can
in the conference room, the suction of return air by the
air-handling unit in the corridor would tend to draw
smoke from the conference room out into the corridor—
the very corridor that is needed for safe egress by build-
ing occupants. A responsible engineer should strive to
keep the corridor clear of smoke, and use of the corridor
as a return air path would actually encourage smoke to
migrate there.
To clarify, it may be proper and acceptable under some
model codes cited (e.g., IMC 601.2.1) to use the space
above a corridor ceiling as a return air path if the cor-
ridor is not required to be rated. If transfer openings are
placed from the ceiling cavity above each office to the
ceiling cavity above the corridor, and the air-handling
unit draws its return air out of the ceiling cavity (not the
corridor itself), then the integrity of the egress path is
maintained. Smoke in the trash can fire example would
then tend to be drawn into the ceiling cavity but not the
corridor itself. If the architect has designed the corridor
without a ceiling, then the return air will need to be
ducted so that the corridor is not violated.
Paragraph 601.2 goes on to grant a few exceptions or
clarifications. For example, it is acceptable to use a cor-
ridor as a source of makeup or transfer air for adjacent
toilet rooms, although I still advise using the corridor
ceiling cavity rather than the corridor itself for this
Part 2
A P R I L 2 0 1 5 a sh r a e . o r g A S H R A E J O U R N A L 5 3
The rationale behind this code requirement is that an
occupancy may have environmental air that contains
odors or contaminants that are unique to that specific
occupancy (such as a restaurant within an office com-
plex, or offices within an industrial plant) and the IMC,
therefore, wants to discourage recirculation from one
occupancy to a dissimilar one. This could potentially
be a very large retrofit cost if done incorrectly and not
caught until the building is ready to open—it is not as
simple as adding a few missed fire dampers—so make
sure this is designed correctly from the outset.
Respect the Interior Stairway EnclosureParagraph 1022.5 of the IBC forbids routing of unrelated
utilities through an interior stairway enclosure. Ductwork
and piping penetrations through interior enclosed exit
stairways are prohibited except for ductwork necessary
for independent ventilation or pressurization, sprinkler
piping, and standpipes. It is important to realize there
cannot be penetrations by unrelated ductwork, nor duc-
twork that shares service with other parts of the building,
even if protected by fire and/or smoke dampers. So it is
not permissible to deliver supply air into a stairwell off a
system serving adjacent spaces, as the code emphasizes
that interior exit stairway ventilation systems shall be
independent of other building ventilation systems.
One must avoid the temptation to route other services
through the stairway enclosure, including but not lim-
ited to domestic water, waste, hydronic reheat piping
looped all around a floor, condenser water piping from
purpose whenever possible; see Taylor5 and a subsequent
letter to the editor6 for further discussion. Obviously, you
may place return air grilles in a corridor to return that
corridor’s own supply air, and it is permissible to have a
minor imbalance of air in a corridor to maintain proper
room pressure relationships in health care or labora-
tory occupancies. Finally, this prohibition does not apply
within an individual residence or in individual tenant
office spaces of 1,000 ft2 (93 m2) or less in area.
Separate VentilationAs stated in 2012 IMC ¶403.2.1, ventilation air cannot
be recirculated from one dwelling unit* to another or
to dissimilar occupancies. This prohibits, for example,
the use of a common recirculating VAV system in a
multi-family apartment building, because it would
recirculate return air from one apartment to another. I
am not aware of any such designs and have always seen
individual air-supply systems (usually fan-coil units
or small air-handling units) on a dwelling-by-dwelling
basis in multi-family housing. However, the second half
of 403.2.1.1 is where I sometimes see violations—there
is a prohibition against recirculating air to dissimilar
occupancies. This means that a large building complex
with more than one occupancy classification cannot use
a common recirculating ventilation system across the
occupancy boundary.
For example, a large urban office complex may have
portions of the building classified as B (Business) occu-
pancy while an attached conference center may be
classified as A3 (Assembly) and a street-level retail sec-
tion may be classified as M (Mercantile). While it may
be tempting and expeditious to serve the retail section
from the same air-handling unit that serves an adjacent
business office zone, this clause in the code prohibits
recirculation of air from one occupancy to a dissimilar
one†—meaning that for all practical purposes, separate
air-handling systems are required within each formal
occupancy category. Alternatively, a system that does
not rely on recirculation, such as a dedicated outdoor
air system (DOAS) paired with hydronic or refrigerant-
based local terminal units could be applied across the
occupancy boundary.
FIGURE 1 Simplified office building incorrectly using the corridor as a return air passage.
* A dwelling unit under the IBC is an individual independent living facility that includes permanentprovisions for living, sleeping, eating, cooking and sanitation. Therefore, some hotel rooms or collegedormitory rooms may not qualify as a “dwelling unit.”† There appears to be no equivalent prohibition in the UMC.
10 ft25 ft
Conference Room
Sales
Office
Support
AHUComputer
Room
15 ft
8 ft
12 ft
30 ft8 ft.
12 ft
15 ft
Corridor
COLUMN ENGINEER’S NOTEBOOK
A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 55 4
a basement chiller to a roof-mounted cooler tower, toi-
let exhaust ductwork, and so forth. If heating and/or
air-conditioning is necessary or desired in an interior
enclosed exit stairway, the designer’s options include:
1. An independent air-handling unit located exterior
to the building (e.g., on the roof) and with supply, return,
or exhaust for the stairwell only ducted directly into the
stairway enclosure without traversing other spaces.
2. An independent ducted air-handling system inside
the building and ducted to the interior enclosed exit
stairway within a rated construction running uninter-
rupted from intake to terminus, matching the rating of
the stairwell enclosure itself.
3. A fan-coil unit, cabinet unit heater, finned-tube ra-
diator, or the like installed within the interior enclosed
exit stairway. In this case, hydronic branch piping for
connection to the terminal unit is permitted to pene-
trate the stairwell enclosure with proper sealing and fire
safing of the penetration.
Access & Aisles Around EquipmentMechanical engineers sometimes complain that archi-
tects squeeze too much space out of air-handling unit rooms
or mechanical equipment rooms, as an excuse for not
providing sufficient aisles or service clearance. Electrical
engineers have done an admirable job of demanding
adequate service clearance around electrical gear by point-
ing out that it is required by their code.7 Now we mechani-
cal engineers have the same ability to say to the architect:
“Look, here it is in the code. We’d love to help you make the
mechanical room smaller but we can’t. The code requires
these clearances and we have no choice in the matter.”
The 2012 IMC in Section 306 now requires that any
room containing an appliance must be provided with an
unobstructed passageway measuring not less than 36 in.
(914 mm) wide and 80 in. (2 m) high from the door to the
equipment; and a level working space at least 30 in. deep
and 30 in. wide (762 mm by 762 mm) must be provided
in front of the control side for servicing. This means it
is no longer acceptable to arrange an equipment room
such that piping or ductwork must be crawled under or
climbed over in order to reach a chiller, air-handling unit,
or other piece of equipment. Mechanical engineers and
designers should insist on adequate mechanical room
service space and annotate the service aisles clearly on the
drawings, so the contractor knows and understands your
intent to keep those aisles clear.
Keep in mind fire safety as well. The rationale for the
code requirement of a clear access aisle is not only to
allow a service technician reasonable ability to service the
mechanical equipment. It is also intended to allow, once
the service technician has reached the equipment and
begun work, a clear path of egress out of the room in the
event a fire or other emergency occurs. It is not difficult
to imagine a fire started accidentally by an electrical fault
or a spark from a welder’s torch during servicing, and
it would be unacceptable if the service technician were
forced to crawl under ducts, climb over pipes, or shimmy
through very narrow passages in order to reach safety.
For roof-mounted or other elevated equipment requiring
a climb greater than 16 ft (4.87 m) above adjacent grade,
the same section requires a permanent ladder or stair (not
a portable ladder) to access roof-mounted equipment.
Review of Overlooked Code Requirements, Part 1It is worthwhile to reiterate the three frequently over-
looked code requirements from the December 2014
Engineer’s Notebook column, to have all of the items
handy in one location for use as a checklist:
1. Guardrails are required where equipment that re-
quires service is located within 10 ft (3 m) of a roof edge
or other platform is located more than 30 in. (762 mm)
above the adjacent floor, roof or grade below.
2. For piping carrying fluids at 140ºF (60ºC) or greater,
all piping surfaces including but not limited to pipe,
flanges, fittings, valves of every kind, strainers, unions,
and other appurtenances should be insulated to avoid
potential for personnel injury via contact with a hot
surface. For Standard 90.1 compliance, this requirement
takes affect at or above 105ºF (41ºC) in most instances.
3. If an air inlet or outlet is less than 7 ft (2.1 m) above
the floor, its maximum allowable blade spacing is one-
half in. (12.7 mm).
References1. Duda, S. 2014. “Overlooked code requirements.” ASHRAE
Journal 56 (12).2. ICC. 2012. International Building Code. Chicago: International
Code Council, Inc.3. ICC. 2012. International Mechanical Code. Chicago: International
Code Council, Inc.4. IAPMO/ANSI/UMC-1-2012, Uniform Mechanical Code. Ontario, Calif.:
International Association of Plumbing and Mechanical Officials, Inc.5. Taylor, S. 2014. “Restroom exhaust systems.” ASHRAE Journal 56 (2).6. Darwich, A. 2014. Letter to the Editor. ASHRAE Journal 56 (4).7. NFPA 70-2014. National Electrical Code. Quincy, Mass.: Na-
tional Fire Protection Association.
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A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 55 6
COLUMN BUILDING SCIENCES
Joseph W. Lstiburek
BY JOSEPH W. LSTIBUREK, PH.D., P.ENG., FELLOW ASHRAE
Joseph W. Lstiburek, Ph.D., P.Eng., is a principal of Building Science Corporation in Westford, Mass. Visit www.buildingscience.com.
Continuous Insulation and Punched Openings
Sometimes we make easy things easy things easy hard. And sometimes we make hard things easy. Withcontinuous insulation and punched openings both things are true.
The physics is easy. A wall A wall A has to control water, air, vapor and heat. A window A window A has window has window tocontrol water, air, vapor and heat. Both have a water control layer, an air control layer,a vapor control layer and a thermal control layer. All you have to do is connect the watercontrol layers to each other, the air control layers to each other, the vapor control layersto each other and the thermal control layers to each other. Oh, yeah, one other point.You don’t want the windows to be sucked out of the of the of wall when it is really blowing. really blowing. really
Now it gets interesting. Where is the wall water control
layer? With continuous insulation it can be the continu-
ous insulation layer itself—or it can be behind it. It is
pretty dumb to put a separate water control layer—spe-
cifically a film or thin membrane—over the exterior of
the continuous insulation layer because it is impossible
to install the additional layer in a practical manner—one
that prevents it from getting sucked off and one that has
constructible details.†
Now, I don’t have a problem with water control layer
films when they are used correctly. Historically, they
have an awesome track record. Tar paper, impregnated
felt, coated paper, and polyolefin films go back a long
way. The best performance from a wind load perspective
and a durability perspective comes from installing such
films behind the continuous insulation layer and over
structural sheathing. That way the film is supported on
both sides—it is sandwiched typically between OSB/ply-
wood/gypsum structural sheathing on one side and the
continuous insulation layer on the other. Neither suck-
ing nor blowing cause it to flex. Of course, you can turn
the structural sheathing itself into a water control layer
and air control layer and not need the film layer at all.‡
I think the winning technologies are to make the struc-
tural sheathing itself the water and air control layer—
and to install continuous insulation over the structural
sheathing (Figure 1). Back in the day we called this the
“perfect wall” (see ASHRAE Journal, May 2007). Or make
the continuous insulation itself the water and air control
layer and include or exclude the structural sheathing
based on—wait for it—structural considerations (Figure 2).
Note that this is an “opinion” so everyone relax. You get
to have your own opinions, too.
So, according to me, there are two locations for the
water and air control layer—behind the continuous
Windows Can Be Can Be Can A Pain A Pain A *
* A “Straube-ism”... after Professor John Straube. He is a master punster. I stole this line from him to make this column work.† The only folks that recommend the practice are the folks that sell water control layer films (aka housewraps, water-resistant barrier films and coated papers). The only reason I can come up with as to why is that they don’t want the rest of us to figure out that you don’t need their products if you turn the continuous insulation layer itself into the water control layer.‡ Not good if you are in the water control layer film business—but pretty good if you are in the liquid-applied over structural sheathing water control and air control layer business or if you make structural sheathing that is itself the water control and air control layer. Of course, both of these groups hate the continuous insulation people who argue that the continuous insulation can do both on its own. Ah, the marketplace is getting interesting and the squabbles are getting ugly. Each group is trying to screw over the other groups to either hold on to market share or capture market share.
A P R I L 2 0 1 5 a sh r a e . o r g A S H R A E J O U R N A L 5 7
COLUMN BUILDING SCIENCES
insulation or the exterior face of
the continuous insulation. Now
for the “pain” part—the windows.
Are they going to be “innies” or
“outies”? Who talks like this?
Welcome to my world.
Are the windows going to be
“inset” or are they going to be
outboard of the structure at the
exterior face of the continuous
insulation? If the windows are
“inset” and the water and air
control layer is behind the con-
tinuous insulation everything
is real easy—things “line up.” If
the windows are “outset”§ and
the water and control layer is the
face of the continuous insulation
things are also real easy—things
also “line up.” But if the win-
dows are outset and the water
and control layer is behind the
continuous insulation things get
more complicated.
Let’s go with the easy stuff first.
“Innies” with the water and air
control layer being the sheathing
behind the continuous insula-
tion. Check out the sequence of
installation (Figure 3). Note that
the water control of the flanged
window lines up with the water
control of the sheathing. Note
the sloping sill. Note that the pan
flashing can be liquid applied or
a formable membrane. Note that
sealant is not necessary (or desir-
able) behind the window flanges.
For an explanation see “Stuck on
You,” ASHRAE Journal, February
2013. Note that the seams in the
continuous insulation do not
need to be sealed or taped.
And here’s a real neat point—
the continuous insulation does
§ Pretty sure this is not what Webster’s had in mind for the meaning of “outset.” But what the heck, I have been making things up for years. I coined the phrase “drainage plane” because I needed rhymes that would help architects and consultants understand water control: “you need to drain the rain on the plane” and “don’t be a dope, slope.”
FIGURE 1 (TOP) Structural Sheathing as the Water and Air Control Layer. Continuous insulation is installed over the structural sheathing. FIGURE 2 (BOTTOM) Continuous Insulation as the Water and Air Control Layer. Include or exclude the structural sheathing based on structural considerations.
A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 55 8
not have to be rigid with this approach—windows
being “innies” with the water control layer and air
control layer being the structural sheathing. The
continuous insulation does not have to be extruded
polystyrene (XPS) or expanded polystyrene (EPS) or
foil faced isocyanurate. It could be mineral fiber insu-
lation boards (aka “stone wool”). See Figure 4. It can
be any type of continuous insulation: rigid or mineral
fiber.
And you can make the continuous insulation pretty
much any thickness. Check out Photo 1. The trim is
returned to the flange or face of the inset window. The
flashing at the top of the window opening at the hori-
zontal strip of head trim just covers the top of the trim
itself—it only protects the top of the trim—it does not
have to extend to the back of the continuous insulation
and connect to the face of the structural sheathing/water
control and air control layer. The window head—the
flange at the top of the window—is already flashed to the
face of the structural sheathing/water control and air
control layer behind the continuous insulation. A gap
is left at the inboard side of the horizontal return trim
at the top of the window opening to let any penetrating
rainwater run out between the window flange and the
horizontal trim (Figure 5).
Now let’s go with “outies” with the water and air control
layer being the face of the continuous insulation. Check
out the sequence of installation (Figure 6). We have seen
this before. We have been doing this for over 50 years.
Note that the water control of the flanged window lines
A) Structural sheathing installed over frame wall; B) Install beveled wood siding in frame opening at sill to create slope; C) Install formable flashing at sill; D) Install window plumb, level and square; E) Install flashing tape at jambs.
A B C D E
F) Install flashing tape at head; G) Install continuous insulation; H) Interior view prior to window installation; I) Interior view after window installation; J) Air seal window around entire perimeter with sealant and sealant backer rod.
F G H I J
FIGURE 3 Window Installation Sequence for “Innies.” The water and air control layer is the sheathing behind the continuous insulation. Note that the water control of the flanged window lines up with the water control of the sheathing. Note the sloping sill. Note that the pan flashing can be liquid applied or a formable membrane. Note that sealant is not necessary (or desir-able) behind the window flanges. Note that the seams in the continuous insulation do not need to be sealed or taped.
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A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 56 0
FIGURE 4 Mineral Fiber Insulation (Stone Wool). With mineral fiber insulation the face of the mineral fiber insula-tion cannot be the water and air control layer. We also need structural sheathing with mineral fiber insulation. Typically, the structural sheathing is turned into the water and air control layer.
FIGURE 5 Window Head. The window head—the flange at the top of the window—is flashed to the face of the struc-tural sheathing/water control and air control layer behind the continuous insulation. A gap is left at the inboard side of the horizontal return trim at the top of the window open-ing to let any penetrating rainwater run out between the window flange and the horizontal trim.
up with the water control of the face
of the continuous insulation. Again,
note the sloping sill and that the pan
flashing can be liquid applied or a
formable membrane. Again, note
that sealant is not necessary behind
the window flanges. And finally,
note that there is no wood behind
the window flange—you don’t need
any—the flange is seated directly over
the continuous insulation—you attach
the window through the flange and
continuous insulation to the framing
with long screws.
But we have some important
changes from the “innies” approach
described previously. The continu-
ous insulation has to be rigid with
this approach. It cannot be mineral
fiber insulation boards (stone wool).
We will deal with mineral fiber insulation boards (stone wool)
later. The continuous insula-
tion in this approach is limited
to extruded polystyrene (XPS)
or expanded polystyrene (EPS)
or foil-faced isocyanurate. And,
the seams in the continuous
insulation do need to be sealed
or taped. And, pay attention
here, the thickness of the con-
tinuous insulation is limited
to 1.5 inches. If you want to
go thicker, the opening needs
to be lined with a structural
box (Photo 2) and the windows
attached with straps (Photo 3
and Figure 7). The structural
box is typically plywood or OSB and it protrudes past the
exterior face of the framing, extending the thickness of
the continuous insulation. How thick can you go with the
continuous insulation with the structural box? Typically 4
to 6 in. (102 to 152 mm). Note that with the structural box
the water control layer is wrapped into the box opening
and the material is typically flashing tape.
So what if I want to use mineral fiber insulation
(stone wool) as my continuous insulation and I want my
windows to be “outies”? Note that with mineral fiber
insulation the face of the mineral fiber insulation can-
not be the water and air control layer. We need that layer
to be located behind the mineral fiber insulation—recall
our previous discussion. We also need structural sheath-
ing with mineral fiber insulation—no option here either.
So we typically turn the structural sheathing into the
water and air control layer (go back and check out
Figure 4 again).
PHOTO 1 Beautiful “Innies.” The trim is returned tothe flange or face of the inset window. The flashing at the top of the window opening at the horizontal strip of head trim just covers the top of the trim itself—it only protects the top of the trim—it does not have to extend to the back of the continuous insulation and connect to the face of the structural sheathing/water control and air control layer.
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A P R I L 2 0 1 5 a sh r a e . o r g A S H R A E J O U R N A L 6 1
To get the windows to be “out-
ies” with mineral fiber insulation
(stone wool), we need to do a couple
of things. We need to line the win-
dow opening with wood framing
that is the thickness of the mineral
fiber insulation (stone wool) and
this “structural extension” needs
to be wide enough on its face to
be able to integrate the window
flange with the water control layer
at the face of the structural sheath-
ing. This is typically 2 × material.
With 1.5 in. (38 mm) thick mineral
fiber insulation (stone wool), the
A) Insulating sheathing installed over frame wall; B) Install beveled wood siding in frame wall opening at sill to create slope; C) Install formable flashing at sill; D) Install window plumb, level and square; E) Install flashing tape at jambs.
A B C D E
F) Install flashing tape at head; G) Install sheathing tape over flashing tape at head to terminate flashing tape; H) Interior view prior to window installation; I) Interior view after window installation; J) Air seal window around entire perimeter on interior with sealant and sealant backer rod.
F G H I J
FIGURE 6 Window Installation Sequence for “Outies.” The water and air control layer is the face of the continuous insulation. Note that the water control of the flanged window lines up with the water control of the face of the continuous insulation. Again, note the sloping sill and that the pan flashing can be liquid applied or a formable membrane. Again, note that sealant is not necessary behind the window flanges. And finally, note there is no wood behind the window flange—you don’t need any—the flange is seated directly over the continu-ous insulation—you attach the window through the flange and continuous insulation to the framing with long screws.
rough opening is “picture framed”
with 2×2s. If you want to go thicker
with the continuous mineral fiber
insulation (stone wool), use 2×4s or
2×6’s—trimmed to the correct thick-
ness—for the “picture framing.”
Check out the sequence of instal-
lation (Figure 8). Note that liquid
applied flashing is used to provide
continuity with the water control
layer on the face of the structural
sheathing and the “picture fram-
ing” “structural extension.” The
liquid applied flashing wraps into
the frame opening and creates the
PHOTO 2 Structural Box. Typically plywood or OSB protruding past the exterior face of the framing, extending the thickness of the continuous insulation. How thick can you go with the continuous insulation with the structural box? Typically 4 to 6 in.
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A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 56 2
PHOTO 3 Strap Window Attachment. Similar to window installation in masonry openings lined with window bucks.Unlike masonry openings the window flanges are retained for water control. FIGURE 7 Structural Box. Note that withthe structural box the water control layer is wrapped into the box opening and the material is typically flashing tape.
A) Structural sheathing installed over frame wall with opening “picture framed” with 2 × material extending past face of sheathing; B) Install beveled wood siding in frame opening at sill to create slope; C) Install liquid applied flashing wrapping into the frame opening; D) Install window plumb, level and square; E) Install flashing tape at jambs.
F) Install flashing tape at head; G) Install continuous insulation; H) Interior view prior to window installation; I) Interior view after window installation; J) Air seal window around entire perimeter with sealant and sealant backer rod.
A B C D E
F G H I J
FIGURE 8 Window Installation Sequence for Mineral Fiber Installation (Stone Wool). Note that liquid applied flashing is used to provide continuity with the water control layer on the face of the structural sheathing and the “picture framing” “structural extension.” The liquid applied flashing wraps into the frame opening and creates the “pan flashing” for the opening. The window installation now follows the same steps as for the “innie” approach.
“pan flashing” for the opening. The
window installation now follows
the same steps as for the “innie”
approach.
So which are better? “Innies” or
“outies”? And what is the correct
location of the water control layer?
Depends on whom you ask. And
when you ask them. It becomes a
Ginger or Mary Ann question. There
is usually no wrong answer. But
regardless of where you end up, the
water control layer of the wall has to
connect to the water control layer of
the window.
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A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 56 4
TECHNICAL FEATURE
Evan Berger is director of energy solutions for CALMAC Manufacturing Corp., in Fair Lawn, N.J.
BY EVAN BERGER
The Hidden Daytime Hidden Daytime Hidden PriceOf ElectricityOf ElectricityOfWhether or not you know it, know it, know if you if you if manage an office building, school, university, mall,or hospital and are in a region that has a demand charge over $10 per kilowatt eachmonth, the price you pay for pay for pay electricity is electricity is electricity likely more likely more likely than twice as much during the during the duringday thanday thanday it is at night. Even customers who receive “flat rates” from their utility or utility or utilitythird-party supplierthird-party supplierthird-party pay a pay a pay much higher rate during daytime during daytime during hours, due to the effectsof demandof demandof charges. In a sense, demand charges serve as a peak-time adder for a typi-cal nonresidential customer with a bell-shaped load curve, making energy making energy making twice energy twice energy asexpensive during the during the during day – day – day or, – or, – looking at looking at looking it from another perspective, half-off at half-off at half-off night.
Yet despite the outsized effect that demand charges have
on commercial, industrial, and institutional customers,
these costs are poorly understood by the entities who
pay them. This article provides an overview of various
“demand” charges, such as utility demand, grid demand,
and rate structure-related costs. Further, this article dem-
onstrates how reducing peak demand and managing one’s
load curve can provide customers with opportunities to
cut costs dramatically, and also potentially benefit from
revenue-generating programs such as demand response.
Utility Demand ChargesThe utility is, broadly speaking, the company that
delivers power to your home and business. It is the
“poles and wires company” that provides the last-mile
distribution to the end-user; in regulated states, it may
also be the company that owns the generators who make
your power as well.
The most commonly understood demand charges
are those levied by the utility. Many, but not all, utili-
ties use demand charges to earn revenue; in deregu-
lated regions, which include 16 states plus the District
of Columbia in the United States, demand charges
are a principal means by which investor-owned utili-
ties profit from commercial and industrial customers.
Utility demand charges are typically denoted in dol-
lars per kilowatt ($/kW) monthly, and set through a
ratemaking process between the utility and its public
A P R I L 2 0 1 5 a sh r a e . o r g A S H R A E J O U R N A L 6 5
TECHNICAL FEATURE
utility commission. Typically, the amount of kW assessed
on each monthly bill is based on the highest 15- or
30-minute kW interval within that billing period. Utility
demand charges are the most widely understood among
commercial customers because they are easiest to intel-
lectually comprehend, and also very often the most
transparent form of demand charge on a customer bill.
There are several complexities to navigate when
deciphering utility demand charges, however. The
first is time-of-use or seasonal adders. Many summer-
peaking utilities have summer adders: in New Jersey,
the utility PSE&G levies an annual demand charge
for commercial customers year-round; in the months
June through September there is an adder that effec-
tively triples the total utility demand charge. Another
demand charge adder is based on time-of-use. For
example, Southern California Edison (SCE) has one
rate with a summertime on-peak demand charge
adder during the weekday hours of 12 to 6 p.m. of
$26.01/kW, as well as a mid-peak adder of $7.17/kW, for
the site’s peak during weekday hours of 8 a.m. to 12
p.m. and 6 to 11 p.m. These two charges are in addition
to SCE’s year-round off-peak demand charge of $14.32/
kW.1 All of the California investor-owned utilities have
rates that model this format.
Another source of complexity in utility demand
charges is the use of ratchets. Many utilities use ratch-
ets to assess a higher kW number to commercial cus-
tomers. Oncor, one of Texas’s largest utilities, imposes
an 80% ratchet for large users. In Oncor’s case, the
ratchet works as follows: a customer’s assessed kW is
the greater of a) its monthly peak kW draw, or b) 80%
of the peak kW draw over the course of the previous
11 billing months.2 This penalizes customers who hit
a particularly high kW peak in any given month, as
that peak can affect their electricity expenditure for
the next year. For example, if a customer has a typical
monthly peak kW of 2,500 kW, but happens to hit a peak
of 5,000 kW in the month of August, its energy costs
will be affected for the following year: even if the cus-
tomer never exceeds 2,500 kW in any 15-minute interval
again, its assessed demand for the next 11 months will be
a minimum of 80% of its August peak, or 4,000 kW.
A final, and perhaps most confusing, source of com-
plexity in utility demand charges is pricing based on
load factor. Load factor is defined as the average kW
draw divided by the peak interval.
138.8 kW Average = 27.7 Load Factor500 kW Maximum
Other utilities use a more tortuous method referred to as
hours use of demand (HUD). A simple glance at an HUD-
based bill might give most customers no idea that they are
sensitive to peak demand fluctuations; but HUD actually
serves as a very expensive form of demand charge.
For its large C&I customers, Georgia Power’s PLL-9 rate
has no $/kW demand charge, but rather has an hours use
of demand structure that, if understood, functions as an
incentive for buildings to shave their daytime peak.3 The
best way to explain Georgia Power’s rate is by example.
Suppose you had a very small building – perhaps a large
doghouse or a toolshed – which has a steady 1 kW load all
month. At the end a 30-day month you would have used
720 kWh. With Georgia Power’s PLL-9 rate and a 1 kW peak
load, the first 200 “Hours Use of Demand” would charge
you 12.7 cents for the first 200 kWh and the remaining
520 kWh would be at a little more than a penny per kWh.4
Using the same example – with the exception being that
for 1 hour of the month the load went up to 2 kW and for
one hour the load was zero – the total kWh would be the
same 720, however now the first 400 kWh (2 kW x 200
HUD) would be at 12.7 cents, and the balance at 1.3 cents.
Therefore, the one single hour of increased demand
doubles the amount of electricity charged at the higher
rate. After surcharges and taxes, Georgia Power’s effective
demand charge for PLL-9 customers is in excess of $20/
kW monthly – and it is 95% ratcheted.
Grid Demand ChargesIndependent System Operators (ISOs) and Regional
Transmission Operators (RTOs) are both terms to
FIGURE 1 Nine ISO/RTOs in North America. Source: FERC.
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A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 56 6
describe the coordinators of the
bulk grid, the non-profit entities
that manage the dispatch of whole-
sale electricity in their respective
footprints.
ISO/RTOs’ role in demand
charges are poorly understood, in
large part because few consum-
ers know of their existence, and
because their demand charges are
often collected indirectly, through
a retail electricity provider, and
thus often buried in C&I bills.
There are nine ISO/RTOs across
North America, including ISOs
in the three largest U.S. states,
California, Texas, and New York,
and regional grid operators across
the country as seen in Figure 2. The
largest bulk grid in terms of MW
managed is PJM Interconnection,
which covers the mid-Atlantic, DC
Metro area, Virginia, Ohio, and
Chicago.
One of the most important func-
tions of the ISOs/RTOs is to ensure
that its territory has adequate gen-
eration to meet its worst-case con-
tingency – the grid’s equivalent to a
design day. Each ISO or RTO meets
this function differently, but many do
so by procuring so-called “capacity”
through an auction process for gener-
ators. Once the generators’ proceeds
are determined, the costs for capacity
are levied on consumers.
Most ISO/RTOs charge end-users
for their share of capacity costs
through a peak load contribution
(PLC), also referred to as a custom-
er’s ICAP, capacity tag, or “captag”
for short. A customer’s PLC is not
based on its own peak kW draw;
rather, it is based on the customer’s
kW consumption during the grid’s
peak kW draw. In PJM, for example,
each customer’s PLC is based on the
average of the customer’s load dur-
ing the grid operator’s five highest
hours of grid demand during the
year. These hours are known as the
five coincident peaks (5CPs), and it
should be noted that no more than
one of the 5CPs can be assessed
on any single day. In contrast,
NYISO determines each customer’s
captag based on the customer’s
consumption during the New York
State grid’s single highest hour of
demand each year. In both PJM and
NYISO, the peak hours of demand
fall almost exclusively on the hot-
test weekday afternoons of the
summer.
FIGURE 2 Cost of cooling per kW in New Jersey’s PSE&G utility. Sources: PJM, PSE&G; General Power & Lighting Rate. Note: C&I customers continue to pay for cooling during winter due to PJM’s grid demand charges, which are 100% ratcheted.
$/kW25
20
15
10
5
0Jan Feb Mar Apr May Jun Jul Aug Sep Oct Nov Dec 2014
PSE&G Annual Demand PSE&G Summer Demand PJM Capacity Demand PJM Network Transmission Demand
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A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 56 8
that a customer sets in the summer will affect its grid
demand charges for a full year. Second, there is often a
lag between when a customer’s peak load contribution
is assessed, and when it is levied. In PJM, NYISO, and
ERCOT, the grid demand charges that a customer must
pay are based on its PLC from the year before. Therefore,
in these regions, customers who set high PLCs in the
summer of 2014 will begin paying higher grid demand
charges beginning in the summer of 2015.
Since grid demand charges are frequently obscured in
the customer bill, it is typically a subject worth inquiring
about with one’s utility or third-party provider, or with a bill-
ing expert. These charges can be substantial, and are very
often blended into other charges within the electric bill.
Customers that would like to identify their grid demand
charges and find solutions to reduce those costs can often ask
and receive for the ISO/RTO demand charges to be separated
and listed on their bill in an itemized, line-by-line format.
Real-Time Pricing: Following the MarketReal-time pricing, also known as “indexed” or “float-
ing” rates, allow end-users to buy energy at the pre-
vailing market price, rather than at a fixed cents per
kilowatt-hour price. Over the long run, this tends to be
less expensive: fixed pricing is an insurance mecha-
nism, and insurance typically comes at a premium.
However, employing real-time pricing leaves customers
more exposed to the vagaries of the open market: if the
weather is unexpectedly hot or cold, or a large generator
fails, prices can spike dramatically.
For customers willing to manage the risk of cheaper
but spikier real-time pricing, shifting load from day
to night with smart building technologies such as
thermal storage is a cost-effective plan. As the graphic
of summertime real-time locational marginal prices in
Washington, D.C.-area PEPCO shows, nighttime elec-
tricity on the real-time market tends to be much less
expensive and less volatile.
It is important to note that regardless of whether a
customer is on real-time pricing or a fixed rate, it is still
likely to pay demand charges.
Special Rate StructuresSome utilities offer special rate structures for custom-
ers who have particularly high load factors. For example,
Potomac Edison in West Virginia offers a special High
Load Factor schedule for large customers; these custom-
ers pay a slightly higher demand charge than normal
users, but they are compensated with a lower cents per
kWh usage charge.5 This benefits industrial customers
with 24x7 operations and a flat load curve: the increase
in demand charges is offset many times over by the
decrease in cents/kWh.
Other special rate structures are given to customers
with specific technologies, such as thermal energy stor-
age (TES). Austin Energy in Texas offers a special rate to
end-users with thermal storage onsite.6 In exchange for
a slightly higher demand charge, customers in the spe-
cial TES Rate pay lower cents/kWh for most of the year,
particularly during nighttime hours; in the summer
months (June through September), TES rate customers
pay only 2.7 cents/kWh between 10 p.m. and 6 a.m., in
contrast to the typical user’s 6.4 cents/kWh. Since TES
users consume a significant amount of electricity at
night, when they are charging up their thermal storage
systems, the TES rate provides immense savings.
ISO/RTOs’ operation and maintenance
costs are determined through a regulatory
procedure, not an auction, but they are typi-
cally also charged to the customer through a
PLC-type process. This is the case in ERCOT,
which uses a “4CP” calculation to determine
its transmission cost recovery charges. In
ERCOT, the customer’s assessed kW is based
on the average of its consumption during
the highest demand hour in each of the four
summer months, from June to September.
Two additional notes are warranted on grid
demand charges. First, they are frequently
ratcheted: the peak load contribution
FIGURE 3 PEPCO Washington D.C. prices, average July Weekday. Source: PJM Interconnection. Average week-day Locational Marginal Price of electricity in PEPCO (Washington, D.C. area) in July 2013. Prices reached their highest at 2 p.m., at 9.7 cents per kWh; the highest hour during the month was 2 p.m. on July 17th, when prices reached 40.1 cents/kWh. Prices were at their lowest at 4 a.m., when they averaged 2.1 cents/kWh.
2 p.m.1 p.m.
8 a.m.7 a.m.6 a.m.5 a.m.
9 a.m.10 a.m.
4 a.m.3 a.m.2 a.m.
11 a.m.12 p.m.
1 a.m.
10 p.m.9 p.m.8 p.m.7 p.m.
11 p.m.12 a.m.
6 p.m.5 p.m.4 p.m.3 p.m.
$0.120
$0.100
$0.080
$0.060
$0.040
$0.020
$0.000
TECHNICAL FEATURE
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A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 57 0
Demand Response: Turning the Paradigm Upside DownMost of this article focuses on how demand costs con-
sumers money; with demand response, consumers can
use their load flexibility to earn money from revenue-
generating programs run at the ISO/RTO or utility level.
An example of this is PJM’s capacity market: users with
flexible load can bid demand reduction (known as
demand response) into the capacity market and receive
the same value for their flexibility as a generator does. In
return for the revenue they receive, demand response
participants must respond to grid or utility “events” – calls
to curtail – by reducing their electricity load, typically for
a period lasting four or six hours. Such programs can be
found throughout the country, and can be very lucrative:
in New York City, combining ConEdison’s and NYISO’s
Demand Response programs can earn a customer as
much as $250,000 per curtailable megawatt, annually.
There are other demand response-related programs
available to end-users aside from the traditional curtail-
ment programs. One such program garnering attention
is behind-the-meter frequency regulation, whereby
assets follow an ongoing grid signal to maintain the
grid at its desired frequency of 60 Hertz. Traditionally,
only natural gas and hydroelectric generators were dis-
patched to regulate grid frequency; but now, smaller
customer-sided assets such as electrical and thermal
storage as well as variable frequency drives (VFDs) are
engaging in this lucrative program as well. Part of this
change has been spurred by policy: FERC’s Order 755 in
2011 mandated that faster-acting devices, such as storage
and VFDs, should be paid an additional “performance”
payment for responding to grid signals more quickly
than large generators can.
ConclusionWhether their energy managers know it or not, most C&I
buildings pay a large percentage of their electricity costs
in the form of demand charges. Nonresidential customers
with bell-shaped load curves, including office buildings,
hospitals, schools, universities, and many industrial plants,
pay substantially more during the daytime than they do at
night, because of the effect of demand charges.
TECHNICAL FEATURE
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A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 57 2
If you could fill your car up with gasoline at noon for
$2.50 per gallon, or at 9 p.m. for $1.25 per gallon, which
would you choose? Many electricity customers face this
same choice – and because of the complexities of the
electricity bill, they have no idea they ever had a choice
in the first place.
Smart building technologies allow commercial, indus-
trial, and institutional customers to buy electricity at
night, when it is vastly cheaper. Thermal energy storage,
such as ice storage and chilled water storage, allow end-
users to build up cooling at night, when electricity is “on
sale,” and dispatch that cooling during the daytime to
displace the on-peak usage of their chillers and HVAC
equipment. Other demand-limiting technology, such
as battery storage or smart building controls, offer the
same opportunity to shift loads from daytime to night-
time, when electricity can be procured at a discount.
Because of the great but latent sensitivity of end-users to
demand, such load-shifting can result in electricity sav-
ings of 10% to 20% off of the total bill.
To save money, end-users and their energy advisors
must be able to understand the effects of demand charges
– and yet, many energy procurers do not understand
that, unlike a residential bill, most C&I bills have demand
charges of one form or another. While this knowledge
gap cannot be bridged with a single article, perhaps a few
final points will be useful to professionals looking to lower
their demand charges or those of their customers.
First, all else being equal, reducing daytime peaks low-
ers demand costs, and thus lowers electricity bills. Smart
building technologies such as thermal energy storage help
to reduce peaks and flatten the load curve; they should be
considered in all new construction and retrofit designs.
Second, it always helps to look closely at the electric-
ity bill. Specifically, it is of great value to add up the
demand charges (the per-kW line items) and compare
them to the usage charges (the per-kWh line items). This
gives one a sense of a site’s sensitivity to demand. When
looking at electricity bills, be sure to review at least one
bill from the summer (July or August) and one from the
winter (December, January, or February). Comparing
these two will determine whether there are seasonal
adders, and those can be a very substantial portion of
a user’s bill. However, make sure to be wary of third-
party suppliers’ “flat rate” or “blended rate”: these terms
can obscure the effect of demand, and give the wrong
impression that electricity is equally expensive during
day and night. Rarely is this true.
Finally, when in doubt, ask for help. Non-residential
customers have access to utility representatives who can
guide them through the process of understanding their
bills; additionally, third-party electricity suppliers can
be a valuable resource as well.
References and Notes1. Southern California Edison. 2013. Schedule TOU-8, Time-Of-
Use – General Service – Large.2. Oncor Electric Delivery Company. 2014. Tariff for Retail Deliv-
ery Service, Secondary Service Greater than 10 kW. 3. Georgia Power. 2014. Electric Service Tariff, Power and Light
Large Schedule: “PLL-8.”4. This does not include the Fuel Cost Recovery surcharge (FCR-
23), nor other Riders such as Environmental Compliance and Nuclear Construction Cost Recovery. Also note that PLL-9 covers loads 500 kW or greater; this highly simplified 1 kW site example is for expository purposes.
5. The Potomac Edison Company. 2014. Rates and Rules & Regu-lations for Electric Service in Certain Counties in West Virginia, Light and Power Service (High Load Factor) Schedule “PH.”
6. Austin Energy. 2014. City of Austin Electric Rate Schedules, Thermal Energy Storage.
TECHNICAL FEATURE
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A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 57 4
BUILDING AT A GLANCE
SECOND PLACECOMMERCIAL BUILDINGS, EXISTING
The addition of a new radiologyclinic at a residential complexchallenged the design team toreduce the impact of the clinicon the residential complex dur-ing and post construction. Thedesign team used heat recoveryand a new chiller with under-ground existing tanks as acondenser.
2015 ASHRAE TECHNOLOGY AWARD CASE STUDIES
Complex Southwest One
Location: Pointe-Claire, Québec
Owner: The Dorchester Corporation
Principal Use: Residential complex
Includes: Commercial & medical centers
Employees/Occupants: Approximately 1,500
Gross Square Footage: 750,000
Substantial Completion/Occupancy: Dec. 31, 2011
Occupancy: 100%
National Distinctions/Awards: Energia 2013
Daniel Robert, Eng., is vice-president of sales & engineering at Kolostat Inc. in Montreal. Stan Katz is general manager of the energy piping and plumbing division at Kolostat Inc. in Montreal. They are members of ASHRAE’s Montreal chapter.
BY DANIEL ROBERT, ENG. MEMBER ASHRAE; STAN KATZ, ASSOCIATE MEMBER ASHRAE
Complex Southwest One (SW1) is a mixed real estateproject near Montreal, consisting of consisting of consisting 662 of 662 of units of resi- of resi- ofdential rental housing totaling housing totaling housing 750,000 totaling 750,000 totaling ft2 (70 000 m2)and incorporating a incorporating a incorporating commercial center of 150,000 of 150,000 of ft2
(14 000 m2) and a medical center of 100,000 of 100,000 of ft2 (9300m2). Complex Southwest One combined its domes-tic water network retrofit and construction of a of a of newmagnetic resonance imaging (MRI) imaging (MRI) imaging clinic in one proj-ect to maximize energy savings, energy savings, energy cut first costs of the of the ofMRI clinic and preserve the living environment living environment living in thecomplex. This article demonstrates the benefits ofcombining thecombining thecombining two projects and presents the main bene-fits of the of the of domestic water retrofit project.
Southwest OneMixed Use Complex
TOLCHINSKY & GOODZ ARCHITECTS
A P R I L 2 0 1 5 a sh r a e . o r g A S H R A E J O U R N A L 7 5
2015 ASHRAE TECHNOLOGY TECHNOLOGY AWARD CASE STUDIES
ABOVE SW1 reception office.
LEFT Complex Southwest One is a mixed real estate project consisting of 662 units of resi-dential rental housing, incorporating a com-mercial center and a medical center.
Complex DescriptionBuilt in the late 1960s, this pioneering
project offers its customers a diverse range
of accommodation including 103 town-
houses and four residential towers of 10
floors each. Some roof terraces span build-
ings, and there is indoor and outdoor park-
ing, as well as pools and beautifully land-
scaped areas. All facilities of the complex
are connected by a network of passages and
underground parking.
The domestic hot and cold water of the
complex is supplied via a centralized district
system, distributing water to all buildings
through centralized constant volume pump-
ing stations. The complex is powered via a
single electric meter and a single gas meter.
Domestic Water NetworkDomestic hot water was distributed
through constant volume pumping stations
that pump the water from two underground
domestic water network to renew the main mechanical
system, ensure code compliance, and reduce the energy
cost related to domestic water heating. The daily domes-
tic hot water consumption of the complex was measured
to 26,500 gallons (100 313 L) in a typical day.
Radiology ClinicIn 2011, SW1 was looking to integrate a new radiology
clinic within its medical center. The new clinic was intended
to include an MRI section and some medical offices along
with the seating and common areas of a clinic. The design
of the new clinic was carried out with high energy efficiency
and sustainable development standards including efficient
envelope, mechanical and electrical systems.
One of the major challenges that the design team
faced was to reduce the impact of the implementation
of the new clinic on the residential complex during
and post construction. Medical spaces necessitate
TABLE 2 Real annual energy consumption before and after the project.
ELECTRICITY GAS TOTAL
$/YR KWH/YR $/YR FT3 /YR $/YR EKWH/YR EKWH/FT2·YR
July 2010 to June 2011
$906,314 15,820,000 $52,967 3.8 million $959,281 16,960,500 22.61
July 2012 to June 2013
$869,071 14,241,257 $32,083 2.3 million $901,154 14,915,809 19.89
Savings 1,578,743 1.5 million 2,044,691 2.72
Electrical Savings $96,303 (based on average cost of $0.061/kWh)Gas Savings $22,188 (based on average cost of $0.01/ft3)Total Energy Savings $118,491
TABLE 1 Projected financial highlights.
ENERGY SAV INGS PROJECT COST*
GRANTS PAYBACK REDUCTION
$/YR ELECTRICITY KWH/YR
ELECTRICITY KW/YR
GAS FT3 /YR
WATER GAL/YR
$ $ YEARS TON OF EQ. CO2
$139,634 1,908,262 3,858 1.7 million 929,261 $594,000 $96,500 3.6 93
* Cost related to energy efficiency measures
concrete tanks of 15,000 gallons (56 800 L) each to the
different facilities.
The domestic hot water network was an open system
where makeup water filled the concrete storage tanks.
The stored water was mainly heated via three atmo-
spheric boilers of 1,000 MBH each and two electrical
heater tanks of 500 kW controlled via a power demand
control system. Both the control system and the boilers
exceeded their useful average life. Because of heat dis-
sipation through the concrete tanks, water temperature
couldn’t be maintained at 140°F (60°C) during winter.
In addition to heat dissipation across the concrete tanks,
hot water recirculation was oversized causing additional
heat loss. SW1 was looking into a major retrofit to its
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7 6 A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 5
Project DescriptionWith 26,500 gallons daily consumption of domestic hot
water, the idea of recovering the heat generated by the
clinic chiller to preheat domestic water complex seemed
very trivial. However, the design team went beyond heat
recovery and proposed the operation of the new chiller
without any cooling towers. This proposal was made
possible by using the two existing concrete tanks as both
a major cooling demand and
need cooling availability year-
round. The design team origi-
nally adopted the installation of a
water-cooled chiller with a cooling
tower. However, locating a cooling
tower within a green residential
complex wasn’t obvious. Besides
affecting the aesthetics of the
green complex, the cooling tower
installation could have incurred
a high cost in civil work to respect
the city regulations and meet a
minimum social acceptance from
660 families living in the residen-
tial complex.
Recirculation Pump 70 gpm
Condensing Gas Heating
3 × 500 MBH1 × 1,000 MBH
Booster Pumps VFD
2xPHE
Cold Water In
Water Meter
M
PumpTwo Water Tanks30,000 gallons
170 tonsHeat Recovery Chiller For Radiology Clinic
To WSHP for Offices 30 tons
720 gallons
StorageHot
Water to Complex
1150 gallons550 kW
Off-Peak Electric Heating
FIGURE 1 Domestic hot water piping.
2015 ASHRAE TECHNOLOGY AWARD CASE STUDIES
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A P R I L 2 0 1 5 a sh r a e . o r g A S H R A E J O U R N A L 7 7
a condenser for the new chiller and a buffer tank for the
heat recovery to preheat domestic water. Therefore, the
project became a combination of the
domestic water network retrofit and
the installation of the new clinic.
Domestic Water Network RetrofitThe three components of the domes-
tic water network were optimized:
heating, storage and distribution
(Figure 1).
Heating optimization. The new
domestic hot water system is heated in
three steps:
1. Preheat from heat recovery.
The new chiller rejects its heat to the
two existing concrete tanks through
the heat rejection loop. Storing the
heat in the concrete tanks maximizes
the heat recovery to preheat domestic water even if the
domestic water heating demand doesn’t fully coincide
with available heat rejected from the chiller. The selec-
tion of the chiller was carefully made to be able to oper-
ate the chiller at high temperatures
on the condenser side (can go up to
160°F [71°C]).
2. Efficient heating via condens-
ing boiler and water heaters. The
three existing atmospheric boilers
(1,000 MBH each and an estimated
overall efficiency of 70%) were re-
placed by a condensing boiler of 1,000
MBH and three condensing water-
heaters of 500 MBH each that run at
an efficiency that can go up to 95%.
3. Off peak electrical heating
through a load shedding control sys-
tem. The electrical heating through
the two electrical heater tanks was
optimized through a load shedding
control loop that prioritizes the use of electrical heating
when power demand is available. Off-peak heating re-
Residential building.
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2015 ASHRAE TECHNOLOGY AWARD CASE STUDIES
A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 57 8
duces the energy costs since the electrical energy (as per
SW1’s utilities tariffs) is cheaper than the gas if we factor
out the electrical power demand cost.
Optimizing storage capacity to reduce heat dissipa-
tion. The huge storage capacity along with the lack of
insulation of the two underground concrete storage
tanks increased the heat dissipation across the domes-
tic water network. In addition, the oversized hot water
recirculation from the facilities to the storage tanks was
also contributing to the heat dissipation problem.
In winter, the existing three boilers and electrical heater
tanks weren’t able to maintain the storage mass at 140°F
at any time, which was creating a concern that made
SW1 invest in regular water quality tests. After, measur-
ing the domestic hot water usage on a typical day to
determine the peak water demand, it was decided to
reduce the hot water storage capacity from 30,000 gal-
lons (113 600 L) to approximately 2,000 gallons (7570 L).
New storage tanks were installed and the domestic water
network was transformed from an open system to a
closed system. Hot water recirculation flow was opti-
mized. Consequently, heat loss through the hot water
network was substantially reduced.
Optimizing water distribution. Booster pumps that
distribute domestic cold and hot water were optimized
by replacing them with efficient multistage pumps with
variable frequency drives and high efficiency motors.
New Radiology ClinicThe new radiology clinic includes:
• Efficient windows (low-e, argon filled double glaz-
ing, thermally broken aluminum frame); Green roof
(R30 + vegetated garden);
• Exhaust heat recovery to preheat makeup air using
an enthalpy wheel;
• High efficiency motors and variable frequency drives;
• Demand ventilation through CO2 sensors in the
administrative area;
• Ventilation by displacement;
• Full DDC system to control lighting and HVAC systems;
• Efficient T5 lighting system & lighting controls via
occupancy sensors.
Indoor Air QualityThe clinic was designed to meet the indoor air qual-
ity requirements of health care facilities as per ASHRAE
HVAC Design Manual for Hospitals and Clinics.
The project successfully preserved the residential living
environment from a noisy cooling tower and from poten-
tial risk of developing legionella in the cooling tower. In
addition, the project avoided potential risks of developing
legionella in the domestic hot water storage tanks by con-
verting the domestic water network to a closed system and
by maintaining the tanks at 140°F (60°C) all the time. A
rigorous risk review was commissioned before project
implementation to minimize the impact of the project
on the residential and commercial areas of the complex.
InnovationThe proposed concept of operating the new chiller with-
out a cooling tower is characterized by a remarkable auda-
ciousness and originality. The experienced design team
knew how to marry the technical solution with energy and
operational savings while at the same time enhancing the
complex’s residential community interests.
Although simple when represented in a schematic, the
concept touches kilometers of domestic hot water pip-
ing. The elimination of thermal losses associated with
oversized hot water recirculation required tracing all
isolation and control valves over the domestic hot water
system. The sensitivity of the availability of domestic hot
water to more than 660 families and small businesses
required a rigorous risk review. There was no room for
any error that could affect the availability of hot water at
any time. Because the domestic water network was built
in the 1960s and no plumbing plans existed, a compre-
hensive audit of the water distribution network was nec-
essary to evaluate the current state of the piping network.
In addition, operating a chiller with condenser tanks
instead of a cooling tower or a fluid cooler is a challenge
in itself. Respecting the operating temperature ranges of
the chiller at all times of the year was studied by using an
hourly simulation that takes into account the variation
of the ambient temperature, incoming water tempera-
ture, radiology clinic cooling load profile, and domestic
water usage profile.
Operation & MaintenanceAll new equipment of the project were centralized on the
building’s energy management and control system (EMCS),
which made the operation fully automatic with no inter-
vention required other than regular maintenance. Training
on the operation and trending of the new equipment was
delivered to SW1 operations team. The building EMCS was
2015 ASHRAE TECHNOLOGY AWARD CASE STUDIES
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203-445-9991www.accutrolllc.com | [email protected]
Airflow Control Valves, Fume Hood Controls,Room Pressure Monitors, Airflow Measurement,
Room Airflow and Temperature Controls
Innovative Airflow TechnologiesLaboratories - Life Science - Healthcare
Designed and manufactured in the USA
Manufacturer of the award-winningLow Pressure Drop AccuValve®
Airflow ProductsNow Offering
A P R I L 2 0 1 5 a sh r a e . o r g A S H R A E J O U R N A L 7 9
the key element in the commissioning process, espe-
cially the fine-tuning of the chiller operation and perfor-
mance as well as the optimization of the gas/electric final
stage of hot water heating. Operation and maintenance
costs were considerably reduced due to the automation
and the capital upgrade of main mechanical systems
(boilers, storage tanks, control system, heat exchangers,
and pump motors). The concept of using the underground
concrete tanks as a condenser of the new chiller saved the
operational costs of maintaining the cooling tower and
eliminated the necessary water chemical treatments. It
also saved the cost of several water quality tests per year.
Energy & Economic BenefitsThis project, which is a mix of a construction of an
efficient radiology clinic and the retrofit of an existing
domestic water network, cuts the complex’s energy cost
by $139,634/year and saved the cost of installing a new
cooling tower worth $250,000. The selection of the type of
chiller (water to water + heat recovery) was the subject of
a life-cycle cost analysis of 20 years. Table 1 (Page 75) shows
the resultant energy and cost savings of the project as calcu-
lated prior to project implementation. The energy savings
calculation was based on the measurement of key param-
eters such as the domestic hot water daily consumption and
the amperage and power demand of the booster pumps.
The overall payback of the project is 3.6 years.
However, if we consider the avoided cost ($250,000) of
the cooling tower and the maintenance savings ($5,000/
year), the payback goes down to 1.7 years.
Table 2 (Page 75) shows the energy consumption of SW1
before and after the project. The energy consumption data
shown in this table are rough data as taken from the utility
bills and haven’t been corrected to take into consideration
weather normalization and/or base year adjustments (such
as the implementation of the new 18,000 ft2 clinic).
Environmental ImpactThe project has avoided the emission of over 92 tons
of CO2 into the atmosphere, which is the equivalent of
planting 464 trees or removing 18 medium cars from the
road. This avoided emission is associated with the gas
energy savings. However, the electrical energy savings,
which represent 77% of the total energy savings, have no
direct avoided emissions in Quebec since electricity is
mostly produced by hydro-electrical plants.
In addition to avoided GHG emissions, the project
saved 929,261 gallons of water that could have been con-
sumed by the cooling tower, not to mention the chemical
products that go with it.
The project resulted in other intangible benefits such as:
• The preservation of the living environment in the
complex.
• GHG reductions associated with the manufacture
and transport of the avoided cooling tower.
• Recuperation of the two concrete tanks.
ConclusionThe combination of the medical radiology clinic and
the domestic water network retrofit allowed SW1 to
implement advanced energy efficiency standards while
respecting highly demanding healthcare requirements,
cutting installation and operation costs, and preserving
the complex’s green and aesthetics aspects.
The successful implementation and operation of a water
cooled chiller with existing condensing tanks instead of
a cooling tower demonstrated that there is always a way to
be creative and innovative in every HVAC project.
2015 ASHRAE TECHNOLOGY AWARD CASE STUDIES
A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 58 0
COLUMN REFRIGERATION APPLICATIONS
Andy Pearson
Andy Pearson, Ph.D., C.Eng., is group engineering director at Star Refrigeration in Glasgow, UK.
BY ANDY PEARSON, PH.D., C.ENG., MEMBER ASHRAE
English, Irish and Irish and Irish ScotsThree pioneers of engineering of engineering of science engineering science engineering have been immortalized been immortalized been through the through the through use of their of their ofnames as units in the in the in SI system, representing energy, representing energy, representing temperature and power. They are They are TheyJames Joule, James Watt, and William Thomson William Thomson William (Lord Thomson (Lord Thomson Kelvin) and it is it is it likely every likely every likely practic- every practic- everying refrigerationing refrigerationing engineer, refrigeration engineer, refrigeration designer, technician and technician and technician mechanic uses at least at least at one least one least of their of their ofnames every day every day every of day of day their of their of working their working their lives. working lives. working They create They create They an interesting an interesting an weave interesting weave interesting in space-time. in space-time. in
Watt and Kelvin worked in the same cramped, old-
fashioned and dingy university laboratories in Glasgow,
Scotland, but were not contemporaries—Watt left Glasgow
to settle in Birmingham, England, 50 years before Kelvin
was born. Watt and Joule’s lives overlap, but only by eight
months, and Watt was nearly 83 when Joule was born.
Kelvin and Joule, although separated by more than 200
miles, worked on the same mathematical and physical
problems and had a strong friendship based on mutual
respect and frequent letter-writing.
James Joule, the Englishman in this trio of
famous names, was born in Salford, just south-
west of Manchester, England, in 1818. His father
owned a brewery and Joule was raised and edu-
cated to take over the business, being tutored by
John Dalton who is famous for creating Dalton’s
law of partial pressures (also widely used by
refrigeration technicians, whether they realize
it or not). Joule developed a passion for science, particu-
larly topics that affected his working life such as electric-
ity, heat and power. He was a businessman and indus-
trialist who pursued science as a hobby, and his wealthy
background and successful brewery business provided
the means to follow his amateur enthusiasms.
He created sophisticated scientific experiments that
were completely at odds with the received wisdom of the
establishment at the time and he claimed, for example,
to be able to measure temperature to within 0.005°F
(0.0028°C); an accuracy that would not be out of place in
a modern, digital, science laboratory. The main goal of all
his experimentation was to demonstrate that mechani-
cal work could be converted to heat and to establish the
conversion factor; the so-called “mechanical equivalent
of heat.” Although this seems normal to us, it was so far
removed from scientific orthodoxy at the time that the
first reading of his theories, at a meeting of the British
Association for the Advancement of Science in 1843, was
met with complete silence from the audience. He was
24 years old. Despite this setback he persevered with his
experiments into electromagnetism and heat, presenting
further papers to the British Association in 1845 and 1847.
The latter meeting was attended by William Thomson,
recently appointed as Professor of Natural Philosophy at
Glasgow at the age of 23. Thomson was initially skeptical
because Joule’s ideas were so unlike conventional
thinking, but he noted that Joule’s theory helped
explain some shortcomings of traditional caloric
theory and over the next four years he convinced
himself that Joule’s reasoning was correct. Joule
and Thomson started a series of experiments
to validate Joule’s theory. Their correspondence
extended from 1852 to 1856, and Joule continued
stirring and measuring for a further 20 years.
Joule was not the only one to develop these ideas; similar
thinking surfaced at about the same time in Germany and
Denmark, but above all others Joule stuck to his task, even
in the face of stony opposition. He continually refined
his techniques and measurements, perfecting his craft
and homing in on the elusive value of equivalence. The
number he was seeking was the amount of mechanical
work, measured in foot-pounds, that was required to heat
one pound of water from 60°F to 61°F (15.56°C to 16.11°C).
When he died in 1889 his tombstone was inscribed with
the value “772.55,” this being, in his opinion, his most
accurate assessment, achieved in 1878 after 35 years of
testing. The fact that this is within one percent of the true
value of 778.17 ft·lb/Btu (4,187 Nm to raise 1 kg by 1 K) is tes-
tament to Joule’s precision, his patience and his eyesight.
Never, never, never give in.
Winston Churchill
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A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 58 2
PRODUCTS
PRODUCT SHOWPLACETo receive FREE info on the
products in this section, visit
the Web address listed below
each item or go to
www.ashrae.org/freeinfo.
A Multifunction AC SystemsNew York-based Impecca announces the 4-in-1 Multifunction Single- and Multi-Zone line of split-unit air-conditioning systems. They feature an air conditioner, heater, fan, and dehumidifier in a single unit.www.info.hotims.com/54427-151
UV FixtureThe X-Plus UV fixture from UV Resources, Santa Clarita, Calif., uses light in the UV-C wavelength (254 nm) to improve indoor air quality by preventing microbial buildup on HVAC cooling coils, air filters and duct surfaces and in drain pans. The fixture is designed to be 10% to 25% more energy efficient than conventional UV light systems.www.info.hotims.com/54427-152
MicrovalveDunAn Microstaq, Austin, Texas, announc-es the silQflo SSV MEMS-based microvalve, designed to precisely and quickly control fluid flow or pressure. The microvalve can be used as an individual unit or as an in-tegrated component of a more complex device.www.info.hotims.com/54427-153
B Dry-Runner PumpThe new TPE3 in-line, dry-runner pump from Grundfos, Downers Grove, Ill., features the company’s FLOWLIMIT technology and a heat energy meter for applications that are not suited for wet-runner circulators. The pump’s intelligent control technology enables users to use independent sensors for DT and DP control.www.info.hotims.com/54427-154
Economizer Retrofit KitBelimo Americas, Danbury, Conn., announces ZIP Packs, designed to be a quick, drop-in economizer replacement solution to meet utility incentive program requirements. The packs include a ZIP economizer base,
A
Multifunction AC SystemBy Impecca
B
Dry-Runner PumpBy Grundfos
sensors, an energy module for demand control ventilation (DCV) integration, a spring-return actuator, and retrofit mount-ing brackets.www.info.hotims.com/54427-155
www.info.hotims.com/54427-8
A P R I L 2 0 1 5 a sh r a e . o r g A S H R A E J O U R N A L 8 3
PRODUCTS
C Motorized Axial FansContinental Fan, Buffalo, N.Y., introduces the
EDXG & DXP ac motorized axial fans. Their
unique coupling of the motor and impeller
minimizes space requirements and provides
for vibration-free operation. Both motor
and impeller are located directly in the air-
stream, providing improved heat dissipation
and efficient motor cooling.
www.info.hotims.com/54427-156
Duct Booster FansDuct booster fans from Tjernlund Products,
White Bear Lake, Minn., are designed
to boost airflow to hard-to-heat or cool
rooms or exhaust foul air from a bathroom
or pole barn.
www.info.hotims.com/54427-157
Air FiltersCleanAire HEPA and carbon Filter Paks
from HEMCO, Independence, Mo., are
designed to be mounted inline in the
exhaust ducting from a fume hood with
airflow up to 1500 cfm (700 L/s).
www.info.hotims.com/54427-158
Redundant DrivesACH550 Redundant Drives from ABB,
New Berlin, Wis., consist of a pair of ABB
ACH550 drives integrated into a NEMA-
rated enclosure. The drives feature single-
point control connections, which eliminate
the need to duplicate control wiring.
www.info.hotims.com/54427-159
Dehumidification Rotors, CassettesRotor Source, Baton Rouge, La., provides des-
iccant dehumidification rotors and cassettes
from 220 mm (8.66 in.) to 3300 mm (130 in.)
diameter in depths of 50 mm (2 in.) to 400
mm (15.74 in.) depth for flow rates from 106
L/s (50 cfm) to 116,500 L/s (55,000 cfm).
www.info.hotims.com/54427-161
Zoning Control PanelsBraeburn Systems, Montgomery, Ill.,
announces the 4-Zone Expandable Zone
Control Panel and the 2-Zone Expander
Panel. The 4-Zone panel is dual-fuel
compatible when using the company’s wired
remote outdoor sensor.
www.info.hotims.com/54427-162
Temperature SensorsE+E Elektronik, Engerwitzdorf, Austria, offers a range of sensors for passive temperature measurement for HVAC and other building technologies. The EE431 duct sensor is designed for the measurement of air temperature in HVAC systems. The EE441 strap-on sensor can be fixed with a hose clamp onto ducts and pipes.www.info.hotims.com/54427-163
Building ManagementTrane, Piscataway, N.J., introduces the Trane Building Advantage suite of energy services products and services to assist building owners and managers to manage and operate efficient and sustainable buildings.www.info.hotims.com/54427-164
C
Motorized Axial FanBy Continental Fan
www.info.hotims.com/54427-5
A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 58 4
SPECIAL PRODUCTS
SOFTWARE, ENERGY MANAGEMENT Thermal Energy Storage AppThe Thermal Energy Storage app from
CALMAC Manufacturing, Fair Lawn, N.J.,
enables users to quickly simulate the effect
of thermal energy storage installations
on demand and predict reductions in
peak electrical demand from use of the
company’s IceBank energy storage tanks.
www.info.hotims.com/54427-203
Fan Selection ProgramThe new eCAPS Fan Application Suite
from Greenheck, Schofield, Wis., is an
online fan selection program that enables
users to compare multiple fan models
simultaneously based on fan performance,
sound levels, operating costs and first costs.
The program cautions users when selections
are close to maximum rpm or when the
selection is close to being unstable.
www.info.hotims.com/54427-204
Coil Selection SoftwareKrueger-HVAC, Richardson, Texas, offers
K-Select 13.0 software for fan coil and blower
coil selection. Users can either calculate
A Online Louver Selection ToolPottorff, Fort Worth, Texas, has updated the LIST online louver selection tool, which enables users to select the correct louver based on application and performance criteria. www.info.hotims.com/54427-201
B Energy Management SystemEnergy AnalytiX from ICONICS, Foxbor-ough, Mass., is an energy monitoring, ener-gy analysis and energy management system (EMS) that delivers browser-independent, real-time visualization. Users can create se-cure, custom energy dashboards and kiosks to view energy reports analyzing energy con-sumption patterns, resource use and prog-ress on sustainability initiatives.www.info.hotims.com/54427-202
A
Online Louver Selection ToolBy Pottorff
B
Energy Management SystemBy ICONICS
product performance data based on
building requirements or manually set coil
parameters, such as the number of coil rows,
fins per inch (FPI), and tube wall thickness.
www.info.hotims.com/54427-205
To receive FREE info on the prod-
ucts in this section, visit the Web
address listed below each item or
go to
www.ashrae.org/freeinfo.
www.info.hotims.com/54427-19
A S H R A E J o u R n A l a sh r a e . o r g A P R I L 2 0 1 58 6
CLASSIFIEDS
BUSINESS OPPORTUNITIES
ADIBATIC AIR INLET COOLING
EcoMESH Adiabatic Systems Ltd.
www.ecomesh.eu
EcoMESH Benefits
ADIBATIC AIR INLET COOLING
EcoMESH Adiabatic Systems Ltd.
www.ecomesh.eu
EcoMESH Benefits
StandardInstallation
EcoMESHAddition
WaterSpray
CoolerAir Intake
(1)
(4)
••
•••••
••
Before
••
•••••
••
Before
StandardInstallation
EcoMESHAddition
WaterSpray
CoolerAir Intake
•Reduced Running Cost
•Reduced Maintenance
•Easy Retrofit
•Improved Reliability
•Increased Capacity
•Self Cleaning Filter
•Shading Benefit
•No Water Treatment
•Longer Compressor Life
•Reduced Running Cost
•Reduced Maintenance
•Easy Retrofit
•Improved Reliability
•Increased Capacity
•Self Cleaning Filter
•Shading Benefit
•No Water Treatment
•Longer Compressor Life
Improving the performance of Air Cooled Chillers, Dry Coolers andCondensers and Refrigeration Plants. EcoMESH is a unique mesh andwater spray system that improves performance, reduces energyconsumption, eliminates high ambient problems, is virtually maintenancefree and can payback in one cooling season.
that
season.
that
season.
Improving the performance of Air Cooled Chillers, Dry Coolers andCondensers and Refrigeration Plants. EcoMESH is a unique mesh andwater spray system that improves performance, reduces energyconsumption, eliminates high ambient problems, is virtually maintenancefree and can payback in one cooling season.
BENEFITSBENEFITS
PCM ProductsPCM Productswww.pcmproducts.netwww.pcmproducts.net
THERMAL ENERGY STORAGETHERMAL ENERGY STORAGEPhase Change Materials between 8ºC(47ºF) and 89ºC(192ºF)release thermal energy during the phase change which releaseslarge amounts of energy) in the form
of latent heat. It bridges the gap between
energy availability and energy use and
load shifting
capability.
• EASY RETROFIT•LOW RUNNING COST• REDUCED MACHINERY• INCREASED CAPACITY
•GREEN SOLUTION• REDUCED MAINTENANCE• FLEXIBLE SYSTEM•STAND-BY CAPACITY
•
•
•
+8ºC(47ºF)
utilising
(PCM)
(1)
Phase Change Materials between +8~20ºC(47~68ºF)can be simply charged using a free cooler over-night without theuse of a chiller and later the stored FREE energy can be used tohandle the day-time sensible
building loads.
•REDUCED MAINTENANCE
• FLEXIBLE SYSTEM
•STAND-BY CAPACITY
• LOWER INSTALLATION COST
• SIGNIFICANT ENERY SAVING
• GREEN SOLUTION
+13ºC(55ºF)
Over-
during day
•
•
•
•
THERMAL ENERGY STORAGETHERMAL ENERGY STORAGE
FREE COOLING BENEFITSFREE COOLING BENEFITS
FOR RENT
HVAC ENGINEERSAll levels. JR Walters Resources, Inc., specializing in the placement of technical professionals in the E & A field. Openings nationwide. Address: P. O. Box 617, St. Joseph, MI 49085-0617. Phone 269-925-3940. E-mail: [email protected]. Visit our web site at www.jrwalters.com.
OPENINGS
Classified line advertisementsare inserted in 7-point type at the
rate of $12.00 per line or frac-
tion thereof, includes heading and
address. Six words to the line average.
Maximum insertion 15 lines. Prices
are net. Available Engineer insertions
up to 60 words for members are $6.00
per line.
Classified Column Inch Border Advertisements are inserted in 8-point bold heading
and address type of 7-point body
type at the rate of $115.00 per
column inch or fraction thereof,
includes heading and address. Maxi-
mum length 5 inches. Maximum width
2-1/8”. Prices are net. Available
Engineer insertions for members
are $55.00 per column inch.
Classif ieds are accepted in the
categories of Job Opportunities,
Rentals, Business Opportunities, and
Software.
Closing date:Copy must be received by the clas-
sified department by the 3rd of the
month preceding date of issue.
Address: Send request for further
information to:
ASHRAE JOURNAL
Vanessa Johnson
1791 Tullie Circle NE
Atlanta, GA 30329
Phone 678-539-1166
Fax 678-539-2166
E-mail: [email protected]
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Hiring Announcement
The Department of Construction Management and Engineering (CM&E) at North Dakota State University (NDSU) invites applications for a faculty position in the area of building mechanical systems design (e.g. HVAC) at the rank of assistant professor or associate professor. This is a new area under development with the purpose to meet the demand of fast growing job market in North Dakota and the nation. The newly hired faculty member will have the opportunity to lead the development of coursework and research emphasis and set the direction for future growth (e.g., establishing a BS in Architecture Engineering program). NDSU is a NSF sponsored ADVANCE Institution and a Carnegie Very High Research Activity Institution. More information about the Department can be found at www.ndsu.edu/construction.
Minimum Qualifications: A Ph.D. degree in archi-tectural engineering, civil engineering, mechanical engineering, or other related fields; demonstrated coursework and research experience in building mechanical systems. Preferred Qualifications: 5-years of relevant industry experience; rele-vant professional registration (e.g., PE); college level teaching and research experience in building mechanical systems; and knowledge about ABET accreditation.
Application Instructions: An applicant must include 1) a one-page written statement with examples of achievements; 2) current curriculum vita, including evaluation of teaching effectiveness if available; 3) names and contact information of three academic and professional references; and 4) a copy of tran-script showing graduate level courses. Applicants should go to the website https://jobs.ndsu.edu/, create an account, click on Search Jobs, and follow the instructions to submit the required documents via Internet. Search will remain open until the position is filled. NDSU is an EO/AA Employer and this position is exempt from North Dakota Veterans' Preference requirements.
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THE MOSING ENERGY CHAIR IN MECHANICAL ENGINEERING AT THE UNIVERSITY OF LOUISIANA AT LAFAYETTE
The University of Louisiana at Lafayette invites applications and nominations for the Mosing Endowed Energy Chair, a tenured faculty position in the Department of Mechanical Engineering. Energy has been identified as a major targeted research and development area by both the university and State of Louisiana and is the focus of several current projects being conducted by faculty in the Department. In addition to providing technical guidance to and supervision of graduate student research in his/her area(s) of specialization, the successful candidate will be expected to play the leading role in developing, sustaining and expanding external research funding in broader energy areas and leading the Department to increased national and international prominence.
Candidates must have an earned doctorate in Mechanical Engineering or a closely allied academic discipline and hold a B.S. in Mechanical Engineering. A strong record of federal funding, sustained publication and Ph.D. production, and national standing in their area of expertise is expected. Industry and teaching experience as well as P.E. licensure are highly desirable.
The department offers both an ABET accredited undergraduate degree as well as an MSME; in addition, the College of Engineering offers a PhD in Systems Engineering with concentration in Mechanical Engineering. The department has 14 faculty positions, has been growing steadily over the course of several years and has a current enrollment over 670 undergraduate and graduate students. The annual research expenditures for the department currently exceed $1.2M per year. Further information on the Department of Mechanical Engineering Department can be found at mche.louisiana.edu.
With over 18,000 students, The University of Louisiana at Lafayette is the largest university in the University of Louisiana system and is a Carnegie II (doctor/research intensive) institution. UL Lafayette is located in Lafayette, Louisiana, an exciting community in the heart of Louisiana’s Cajun Country. Lafayette is a major energy industry center, highly technology oriented and offers a quality lifestyle, pleasing climate, and friendly culture.
The preferred starting date is August 2015. A letter of application; name, address, and phone number of at least three references; a statement of research and teaching interests; and a detailed curriculum vitae should be forwarded C/O Dr. Sally Anne McInerny, Department Head and Search Committee Chair, Department of Mechanical Engineering via email at [email protected]. Screening of applicants will begin immediately and will continue until the position is filled. The university is in compliance with Title IX of the civil Rights Act, Section 504 of the Rehabilitation Act of 1973, and is an Equal Opportunity Affirmative Action Employer.
To place an ad contact: Vanessa Johnson Advertising Production & Operations Coordinator
1791 Tullie Circle NE Atlanta, GA 30329Phone: 678-539-1166 | Fax: 678-539-2166 | Email: [email protected]
A S H R A E J O U R N A L a sh r a e . o r g A P R I L 2 0 1 58 8
ADVERTISING SALESASHRAE JOURNAL
1791 Tullie Circle NE | Atlanta, GA 30329 (404) 636-8400 | Fax: (678) 539-2174
www.ashrae.orgGreg Martin | [email protected]
Associate Publisher, ASHRAE Media Advertising Vanessa Johnson | [email protected]
Advertising Production Coordinator
NORTHEASTNelson & Miller Associates – Denis O’Malley5 Hillandale Ave., Suite 101Stamford, CT 06902(203) 356-9694 | Fax (203) [email protected]
SOUTHEASTMillennium Media, Inc. – 590 Hickory Flat RoadAlpharetta, GA 30004Doug Fix (770) 740-2078 | Fax (678) 405-3327Lori Gernand (281) 855-0470 | Fax (281) [email protected]; [email protected]
EASTERN CANADANelson & Miller Associates – Denis O’Malley5 Hillandale Ave., Suite 101Stamford, CT 06902(203) 356-9694 | Fax (203) [email protected]
OHIO VALLEYLaRich & Associates – Tom Lasch512 East Washington St.Chagrin Falls, OH [email protected](440) 247-1060 | Fax (440) 247-1068
MIDWESTKingwill Company – Baird Kingwill; Jim Kingwill664 Milwaukee Avenue, Suite 201Prospect Heights, IL 60070(847) 537-9196 | Fax (847) [email protected]; [email protected]
SOUTHWESTLindenberger & Associates, Inc. – Gary Lindenberger; Lori Gernand7007 Winding Walk Drive, Suite 100 Houston, TX 77095(281) 855-0470 | Fax (281) [email protected]; [email protected]
WESTLaRich & Associates – Nick LaRich, Tom Lasch512 East Washington St.Chagrin Falls, OH [email protected]@larichadv.com(440) 247-1060 | Fax (440) 247-1068
KOREAYJP & Valued Media Co., Ltd – YongJin ParkKwang-il Building #905, Dadong-gil 5 Jung-gu, Seoul 100-170, Korea+82-2 3789-6888 | Fax: +82-2 [email protected]
CHINA, HONG KONG & TAIWANChina Business Media – Sean Xiao6-310 Xinchao No.162 Liaoyuan RoadFuzhou, Fujian, China86 186 5099 [email protected]
INTERNATIONALSteve Comstock(404) 636-8400 | [email protected]
RECRUITMENT ADVERTISING AND REPRINTSASHRAE – Greg Martin(678) 539-1174 | [email protected]
Advertisers Index/Reader Service InformationTwo fast and easy ways to get additional information on
products & services in this issue:
1. Visit the Web address below the advertiser’s name for the ad in this issue.2. Go to www.ashrae.org/freeinfo to search for products by category or company name. Plus, link directly to advertisers’ Web sites or request information by e-mail, fax or mail.
Company PageWeb Address
Company PageWeb Address
Company PageWeb Address
*Regional
AAON, Inc .........................................................15info.hotims.com/54427-1
Accutrol, LLC ....................................................79info.hotims.com/54427-2
Acrefine Engineering ......................................32info.hotims.com/54427-3
Acutherm ..........................................................25info.hotims.com/54427-4
Aerionics, Inc./Macurco .................................84info.hotims.com/54427-5
AHR Expo Orlando 2016 .................................81info.hotims.com/54427-6
Airius LLC .........................................................48info.hotims.com/54427-7
A-J Mfg. Co. .....................................................83info.hotims.com/54427-8
AQC Ind. ............................................................39info.hotims.com/54427-9
Armacell, LLC ...................................................77info.hotims.com/54427-10
*ASHRAE Hospitals and Clinics ...................59info.hotims.com/54427-71
*ASHRAE PCBEA .............................................69info.hotims.com/54427-72
Belimo Aircontrols USA ..................................67info.hotims.com/54427-11
Berner International .......................................41info.hotims.com/54427-12
Bluebeam Software ........................................51info.hotims.com/54427-13
Cambridge Engineering Inc. ............................6info.hotims.com/54427-14
Captiveaire .......................................................71info.hotims.com/54427-15
Captiveaire/Rupp Management Systems ...23info.hotims.com/54427-16
Carrier Corp........................................................9info.hotims.com/54427-17
ClimaCool Corp ................................................32info.hotims.com/54427-18
Climatemaster .................................................85info.hotims.com/54427-19
Climaveneta S.p.A. ..........................................36info.hotims.com/54427-20
Contemporary Controls ..................................24info.hotims.com/54427-21
Daikin North America LLC ............... 2nd Cvr-1info.hotims.com/54427-22
Data Aire, Inc .............................................28-29info.hotims.com/54427-23
Delta Controls ..................................................33info.hotims.com/54427-24
Ductsox Corp....................................................16info.hotims.com/54427-25
ebm-papst, Inc ................................................45info.hotims.com/54427-26
Ebtron .......................................................3rd Cvrinfo.hotims.com/54427-27
FasTest Inc .......................................................76info.hotims.com/54427-29
Flexim Americas Corp ......................................8info.hotims.com/54427-30
Genesis International .....................................72info.hotims.com/54427-31
Goodway Technologies ...................................76info.hotims.com/54427-32
Greenheck.........................................................11info.hotims.com/54427-33
Greentrol Automation Inc ..............................55info.hotims.com/54427-28
Heat Pipe Technology Inc ..............................70info.hotims.com/54427-34
LG .......................................................................21info.hotims.com/54427-66
M & G & Security ............................................66info.hotims.com/54427-35
MacroAir Technologies .....................................5info.hotims.com/54427-36
Mestek/KN Series .............................................7info.hotims.com/54427-37
Mestek/RBI Water Heaters ...........................17info.hotims.com/54427-38
Mestek/Xcelon ................................................63info.hotims.com/54427-39
Mitsubishi Electric & Electronics USA Inc 73info.hotims.com/54427-40
*Mitsubishi Electric Sales Canada, Inc ......59info.hotims.com/54427-41
*Modular Framing Systems ..........................69info.hotims.com/54427-42
Munters Corp ..........................................4th Cvrinfo.hotims.com/54427-43
Munters Corp ...................................................19info.hotims.com/54427-44
Ontrol .................................................................14info.hotims.com/54427-45
Panasonic Eco Solutions of N.A. ..................37info.hotims.com/54427-61
Petra Engineering ...........................................38info.hotims.com/54427-46
Pottorff ..............................................................40info.hotims.com/54427-47
Reliable Controls ...............................................2info.hotims.com/54427-48
Renewaire .........................................................18info.hotims.com/54427-65
Rotor Source, Inc. ...........................................82info.hotims.com/54427-50
Shortridge Instruments, Inc ..........................82info.hotims.com/54427-51
Soler & Palau USA, Inc ..................................26info.hotims.com/54427-52
Southland Industries ......................................49info.hotims.com/54427-53
Spectronics Corp .............................................35info.hotims.com/54427-54
Tekleen Automatic Filters ..............................41info.hotims.com/54427-55
Tempeff North America Ltd ...........................47info.hotims.com/54427-56
Thybar Corp ......................................................14info.hotims.com/54427-57
Unilux Advanced Mfg, LLC.............................50info.hotims.com/54427-58
Xylem, Inc .........................................................27info.hotims.com/54427-60
www.info.hotims.com/54427-27
www.info.hotims.com/54427-43