ashrae_ashraejournal_201504

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

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

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.


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


INDUSTRY NEWS


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.


INDUSTRY NEWS

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


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

)

www.info.hotims.com/54427-57www.info.hotims.com/54427-45


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



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

1-800-627-4499 renewaire.com



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


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

TECHNICAL FEATURE


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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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



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

xyleminc.com© 2015 Xylem Inc. Bell & Gossett is a trademark of Xylem Inc. or one of its subsidiaries.

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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


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



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

TECHNICAL FEATURE



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


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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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



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



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



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


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.



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




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



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.


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


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



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.



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.



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.


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.



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.



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.



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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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


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.



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


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



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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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


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.


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


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


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.




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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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



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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.



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



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



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.


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.


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).


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.


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).


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.


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



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.


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.


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.


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.

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]

RATE SCHEDULE:

Classified ads are

ALWAYS productive.

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.

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 7

SOFTWARE

www.bcatech.comwww.bcatech.com 407407--659659--06530653

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The power of BIM for MEP design•Calculations directly from the BIM model•Automatic generation of all the case study results •Automatic generation of the final set of drawings (plan views, vertical diagrams, axonometric diagrams, Piping/Ducting Networks in 2D and 3D and others) •Complete documen-tation of results (detailed calculation sheets, Technical Reports, Bill of Materials and many more) •IFC import/export to ensure collabora-tion with other BIM applications.

FineHVAC - HVAC Design HVAC Loads (Ashrae 2013), Chilled and Hot Water piping, Airduct Sizing, Psychrometric Analysis (includes also design for Merchant and Naval Surface Ships - Ashrae ch. 13.1 & 13.3).

FineFIRE - Fire Fighting Design NFPA 13 fully calculated systems for tree, gridded or looped systems (includes also EN 12845, BS 9251, FM, CEA 4001 & AS 2118 regulations)

FineSANI - Plumbing Design Water supply and Sewerage design

FineELEC - Electrical Design

FineGAS - Gas Network Design

FineLIFT - Elevator Design

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]


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]

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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]

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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



*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

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