trane engineers newsletter live - ashrae standard 90.1 2010

Trane Engineers Newsletter Live ASHRAE Standard 90.1 2010 Program Date: October, 2010

©2010 Trane a business of Ingersoll Rand

Abstract: Major envelope, mechanical, lighting, and modeling addenda that will be incorporated into 90.1-2010 will be discussed.

Presenters: Mick Schwedler, Susanna Hanson, Mike Patterson, Matthew Bye, What the viewer can expect to learn: 1. How 90.1-2010 saved close to 30% energy cost over 2004

2. Major changes, with specific emphasis on mechanical related system design, control and modeling.

3. Mechanical updates: equipment efficiencies, design requirements for hydronics, airside, and ventilation.

4. Controls updates for system design and operation.

5. Modeling changes for Appendix G baseline definitions and proposed buildings.

6. Summaries for lighting, envelope and other changes

7. Trane expertise in systems and controls can help meet requirements

8. Learn where to go for help

Program Outline: 1) Opening

a) Welcome, agenda, introductions 2) Introduction

a) The forced march to 30% over 2004 b) Number of addenda processed c) Energy savings estimates

3) Envelope highlights a) Insulation b) Air barrier c) Fenestration d) Lighting e) Daylighting and skylights f) WWR, orientation

4) Mechanical with examples a) Equipment efficiency updates. b) Unitary system design c) Waterside system design d) Airside system design e) Ventilation and exhaust

5) Controls with examples a) Reheat minimums b) VAV heating temp c) Ventilation reset d) Zone DCV e) Supply air reset

6) ECB with examples a) Change G to normative (what this means) b) Purchased heating and cooling c) Lab exhaust modeling d) Fan power limit definition in Appendix G (different than in Ch. 6) e) What prescriptive changes weren’t yet picked up by 11 and G

7) Close – How Trane can help, other resources

ANSI/ASHRAE/IESNA Standard 90.1-2010,Energy Standard for Buildings Except Low-Rise Residential Buildings

[JEANNE] Welcome to our Engineers Newsletter Live program. Today we'll be provide an overview of changes made inASHRAE Standard 90.1-2010 sections that pertain to HVAC systems. I'm Jeanne Harshaw from Trane's Systems Engineering Department and I'll be your host today. Before we get started let’s quickly cover some housekeeping…

Slide 2

© 2010 Trane, a business of Ingersoll-Rand2

Ingersoll Rand

ASHRAE Standard 90.1-2010

1.5

This course is approved by the U.S. Green Building Council (USGBC) for [1.5] GBCI CE Hours towards the LEED Credential Maintenance Program. Upon successful completion of this course, LEED Professionals may submit their hours to Green Building Certification Institute (GBCI) under the “Professional Development/Continuing Education” activity type in “My credentials” at www.gbci.org.

Slide 3


“Trane” is a Registered Provider with The American Institute of Architects Continuing Education Systems. Credit earned on completion of this program will be reported to CES Records for AIA members. Certificates of Completion for non-AIA members available on request.

This program is registered with the AIA/CES for continuing professional education. As such, it does not include content that may be deemed or construed to be an approval or endorsement by the AIA of any material of construction or any method or manner of handling, using, distributing, or dealing in any material or product.Questions related to specific materials,methods, and services will be addressedat the conclusion of this presentation.

[SLIDE] Today’s program is registered with the AIA/CES education system and qualifies for HSW and Sustainable Design credit so make sure you provide your member number to your local host before leaving today's session. In several states, Certificates of Completion can also be applied to engineers' continuing education requirements. So please check your state's rules to see if this might apply to you.

Trane Engineers Newsletter Live Program Series ASHRAE Standard 90.1-2010

© 2010 Trane a business of Ingersoll Rand


Copyrighted Materials

This presentation is protected by U.S. and international copyright laws. Reproduction, distribution, display, and use of the presentation without written permission of Trane is prohibited.

© 2010 Trane, a business of Ingersoll-Rand. All rights reserved.

Slide 5


ASHRAE Standard 90.1-2010What you’ll learn…

Evolution of Standard 90.1 Overview of the major changesMechanical updatesControl updatesModeling changes Appendix G Summary

[JEANNE] If you have questions during the program, they can be faxed in to the number on the screen or emailed at any time to [email protected]. Include your email address so we can respond directly to you. Answers to all questions will also be available in a few weeks so be sure to follow up with your Trane sales office for a copy. [JEANNE] ASHRAE Standard 90.1-2010 will be published this fall, with an aggressive goal of 30 percent energy cost savings over the 2004 version of the standard. Today you’ll learn about the major changes and how they’ll affect future minimally-compliant and above-code programs. Our goal is to [SLIDE] [CLICK] provide designers with an understanding of the development process for 90.1. [CLICK] and then highlight the major changes with respect to HVAC systems. [CLICK] We’ll dive into the mechanical section updates including equipment efficiencies and system requirements and provide some examples [CLICK] [CLICK] we’ll then discuss changes to control strategies for system design and operation. And finally we’ll cover modeling changes to Appendix G baseline definitions and proposed buildings.




Today’s Presenters

Mick SchwedlerApplications

Engineering Manager

Susanna Hanson Applications

Engineer

[SLIDE] To cover this information today we’re fortunate to have two people with an inside view of 90.1. Mick Schwedler Applications Engineering manager and immediate past chair of 90.1, will give us an overview of the development process of 90.1 and provide an overview of the major changes. Susanna Hanson, who also served on the 90.1 committee, will provide a closer look at the changes in the mechanical section and provide some examples.

Slide 7


Today’s Presenters

Mike PattersonSales training manager

Matthew ByeProduct engineer

[CLICK] We’re delighted to introduce two new members to the ENL program series. Matthew Bye, a product manager with our controls group will give us an update on the control requirements. [SLIDE] and Mike Patterson. Who was responsible for development of LEED and 90.1 curriculum for TRACE training and will provide an overview of the impact of the changes for Appendix G. [MICK AND JEANNE] So Mick we know there have been a lot of changes, why don’t you get us started with how the standard has evolved?

Slide 8

Development Overview of 90.1

ASHRAE/IES 90.1-2010




Historical TimelineCognizant TC, 7.6 Systems Energy Utilization

90.1-2001minorrevisions

90.1-2004updates,reorganization

90.1-1999major rewrite

90.1-1989updated

90-1975first issued

90.1-1980updated

1990 2000 20101970 1980

90.1-2007updates

90.1-2010(planned)extensiveupdates

[MICK] Standard 90.1 is sponsored jointly by the American Society of Heating, Refrigerating and Air-Conditioning Engineers, Inc. (ASHRAE) and The Illuminating Engineering Society (IES). [SLIDE] It was first published in 1975, partially in response to the oil embargo. However, ASHRAE and IES also felt that the national impact of energy conservation was important enough to keep the standard active. The standard was enhanced in 1980. In 1989, an updated version of the standard was published. For almost 10 years a committee worked to rewrite ASHRAE 90.1 and this was designated 90.1-1999. [MICK] At that point the standard was put on continuous maintenance. Subsequently revisions were made through that process, resulting in the 2001, 2004, and 2007 versions of 90.1.

Slide 10


ASHRAE Standard 90.1 andModel Codes

ASHRAE Standard 90.1 is adopted by:• National Fire Protection Association by reference• International Code Council (2009)

(International Energy Conservation Code®)Chapter 5: Commercial Energy Code– Comply with 90.1-2007 or– Comply with the rest of Chapter 5

[MICK] 90.1 is a standard, that is written in language so it can easily be adopted into a local code. So, how does the process take this from a standard to a code in a state or city? [SLIDE] ASHRAE 90.1 is adopted by reference by the National Fire Protection Association, so if a locale adopts NFPA, it adopts 90.1. The International Code Council has also developed a single set of regulatory documents for use by states and other locales. One of the International Code documents is the International Energy Conservation Code. The 2009 IECC has two paths within its chapter 5. The first is to comply with 90.1-2007. Or one can follow the prescriptive requirements of the rest of Chapter 5. [MICK] Many of those requirements are similar, but not identical to 90.1-2007.

Slide 11


ASHRAE Standard 90.1 andUSGBC, LEED®-2009 (v3)

EAp2: Minimum energy performanceComply with 90.1-2007– Mandatory provisions of 90.1-2007 and– Prescriptive requirements of 90.1-2007 or

Energy Cost Budget method of 90.1-2007 and– 10% improvement over 90.1-2007

EAc1: Optimize energy performance1 point for 12% savings3 points for 16% savings…Up to 19 points (of 100)

[MICK] 90.1 is also used by the U.S. Green Building Council’s Leadership in Energy and Environmental Design (or LEED) products. [SLIDE] In LEED 2009 (sometimes referred to as version 3) One’s building must use 10% lower energy cost than a building that meets the requirements of 90.1-2007. In addition, points must be earned to achieve higher levels of LEED recognition. From an energy perspective, for each 2% additional energy cost reduction, a point is earned, up to a maximum of 19 points for a 48% reduction. [MICK] It’s expected that as 90.1 is changed, local jurisdictions will move toward its adoption, either directly or through IECC, and the LEED products will also use the newer version as its basis. So, what is happening with 90.1-2010?




SSPC 90.1 Work Plan(unanimous June 2007)

Goal: A 2010 standard that results in 30% total energy cost savings improvement compared to Standard 90.1-2004.• Measurement is aggregated, may not be met

for every building in every location90.1-2010 = 90.1-2007 + All IES and ASHRAE BOD approved addenda

In June of 2007 the SSPC 90.1 committee unanimously adopted a WorkPlan goal for a [SLIDE] 2010 standard with 30% energy cost savings compared to 90.1-2004. That will not be realized on every building, but is aggregated across 16 building types in 17 climate zones. Since 90.1 is on continuous maintenance, addenda are developed by the committee. [MICK] 90.1-2010 is simply 90.1-2007 plus all addenda that have been approved by both the IES and ASHRAE Boards of Directors.

Slide 13


How is 90.1 Updated?Through Addenda

Developed and voted on by 90.1 committee• SSPC 90.1 uses economic criteria

Approved by ASHRAE oversight committeesPublic Review• Comments require formal response • Changes must be re-approved and sent subsequent

public review• Resolution of commenters is the goal

If not resolved, they may appeal

Must reach consensus

[MICK] ASHRAE follows a rigorous, open process to develop or change its standards [SLIDE] To move an addendum to publication the committee uses an economic criteria in developing proposed changes. Once approved by the committee those addenda must also be approved by other ASHRAE committees prior to going out for public review – during which anyone may comment on the proposed changes. The committee must vote a response to each comment, and if changes to the addendum result, the addendum must be sent for another public review. [MICK] The SSPC worked very hard to resolve each and every comment, but there were times when either there were opposing comments, or the committee could not reach agreement with the commenter. Those unresolved commenters’ reasons are shared throughout the process, including with the Boards of directors, and the unresolved commenter has a right to appeal. Put succinctly, changes are not lightly made and must reach consensus.

Slide 14


Where have addenda come from?YouOther publications• Advanced Energy Design

Guides• California Title 24• ASHRAE Standard 189.1

ASHRAE Technical CommitteesStakeholders (working groups)

Energy conscious ownersSSPC 90.1 volunteers• 4 meetings per year

(3-4 days each, 8 am – 9 pm)

• Additional web meetings• Monthly (or more often)

conference calls

[SLIDE] Addenda come from many people and groups as shown here. Some of the most gratifying are those energy conscious building teams that have shared practices that reduce energy costs and are economical. For example, one building owner did research on daylighting and found it to be very cost-effective in specific cases. They not only shared this information with ASHRAE and IES, but also had their researcher attend committee meetings to explain it. [MICK] However, the brunt of the work fell to the committee and subcommittee members drafting, refining and writing proposals. Hard-working, dedicated members are always appreciated. So where did this lead?




SSPC 90.1 Accomplishments06/2007 through 07/31/2010

119 Addenda processed• 111 approved with no appeals• 1 approved and is being appealed• 7 still in comment resolution and will not be in 90.1-2010

2010 User’s Manual in progress

In the past 3 years the 90.1 committee [SLIDE] has authored and sent 119 addenda through the public review process, some up to four times in response to comments received. Of those, 111 are approved by the IES and ASHRAE Boards of Directors and have not be appealed. 1 is approved by the boards, and is being appealed. And on 7 addenda the committee is still working with commenters to reach resolution, these addenda will hopefully be included in future versions of 90.1 [MICK] In addition, following publication of the 90.1-2010 standard this fall there are plans for a User’s Manual to be available in early 2011.

Slide 16


ASHRAE Standard 90.1-2007Sections

Section 1: PurposeSection 2: ScopeSection 3: Definitions, Abbreviations, and AcronymsSection 4: Administration and EnforcementSection 5: Building EnvelopeSection 6: HVAC

Section 7: Service Water HeatingSection 8: PowerSection 9: LightingSection 10: Other EquipmentSection 11: Energy Cost Budget (ECB) MethodSection 12: Normative ReferencesAppendices

The rest of today’s ENL will cover the significant mechanical, control, and modeling addenda, but we want to highlight some of the other addenda first. ASHRAE 90.1 covers the entire building, including the envelope (walls, roofs, windows, etc.), lighting systems and controls, as well as motors and other electrical equipment. Let’s look at a few of these addenda.

Slide 17


ASHRAE Standard 90.1-2010 (AQ)Purpose

“To establish the minimum energy efficiency requirements of buildings, other than low rise residential buildings, for:

1. design, construction, and a plan for operation and maintenance, and

2. utilization of on-site, renewable energy resources ”

Addendum AQ changed the Title, Purpose, and Scope of the standard. Note that the purpose of 90.1 is to define minimum requirements … not state-of-the-art. The key phrases on this slide are: Minimum requirements; They are not suggestions or guidelines, they are requirements. The second phrase is Energy-efficient design. So a building designed in accordance with the standard , theoretically represents the worst building that could be built from an energy perspective.




ASHRAE Standard 90.1-2010 (AQ)Scope

New buildings and their systemsNew portions of buildings and their systemsNew systems and equipment in existing buildingsNew equipment or building systems specifically identified in the standard that are part of industrial or manufacturing processes

[SLIDE] The standard applies to new buildings, but also additions and alterations to existing buildings. This modification, first made in 1999, changed many people’s perception of the standard. Building owners on the committee, such as BOMA, worked to ensure the wording clearly states how the standard applies to additions and alterations. [MICK] 90.1-2010 applies to commercial processes (2007 could not). Also, the final clause shown here allows 90.1 to apply to industrial or manufacturing processes specifically identified in the standard.

Slide 19


ASHRAE Standard 90.1-2010 (AQ)Does Not Apply To

Single-family houses, multi-family structures of three stories or fewer above grade, manufactured houses (mobile homes), and manufactured houses (modular), or

Buildings that use neither electricity nor fossil fuel

Although Standard 90.1 applies to buildings such as high-rise condominiums, [SLIDE] it does NOT apply to low-rise residential buildings three stories or less. Also excluded from 90.1 are buildings that don’t use fossil fuel or electricity. [MICK] OK, now that we know the purpose and scope of the standard, let’s take a very high level look at a few of the envelope and lighting addenda. We’ll begin with the building façade. Architects need to know about the changes to the building envelope, since they are significant.

Slide 20


Addendum bb – Building EnvelopeMore Insulation and Better Glass

Opaque• Roofs• Walls• Floors• Slab-on-grade insulation• Doors

Fenestration (glass)• 30% maximum window to

wall ratio (WWR)• Better U-Factor• Lower Solar Heat Gain

Coefficient (SHGC)• Visible transmittance/SHGC

RatioVT/SHGC > 1.10

Allowance up to 40% WWR(Addendum cx)• Proper daylighting layout• Automatic dimming controls

on lights

With the adoption of addendum BB, almost all the insulation requirements on opaque elements (those we cannot see through) are more stringent. We’ll look at an example in a minute. For the glazing, the prescriptive tables are for use up to 30% of gross wall area. This is a reduction from 40% maximum in the 2007 version. The fenestration installed must have a better U-factor and solar heat gain coefficient. In addition, there is a new requirement that the glass have a ratio of visible transmittance to solar heat gain coefficient of more than 1.1 – This ensures that less heat is transmitted, but the amount of visible light allowed through the glazing may be used for daylighting the space. During comment resolution an alternative path was added that allows up to 40% glass. To do this prescriptively, the layout must be conducive to daylighting the space – that is, using sunlight to light the space -- and have automated controls that reduce electricity used for space lighting when possible.




Climate Zones and Climatic DataNormative Appendices B and DFigure B-1 and Table B-1 US Climate Zones

Shown are the climate zones within the continental U.S. Let’s take a quick look at the requirements for a mass wall building built slab-on-grade in climate zone 4 – across the middle of the U.S.; Climate Zone 4 includes cities such as St. Louis, Philadelphia, Wichita, Louisville, and New York City.

Slide 22


Climate Zone 4 Requirements

U-0.32 and 0.30 SHGC

U-0.40 and 0.40 SHGC

Non-metal-framed vertical fenestration

U-0.50U-0.70Opaque swinging door

c.i.F-0.843 or R-20 for 24 in.

c.i.F-0.860 or R-15 for 24 in.

Heated slab-on-grade floor

U-0.104 orR-9.5

U-0.104 or R-9.5

Mass wall above grade

R-30 c.i. R-20 c.i. Roof – insulation entirely above deck

90.1 – 2010 (Addendum bb)

90.1-2007

c.i. - continuous insulation

As shown here, all the requirements except the mass wall insulation level are more stringent due to the changes in Addendum bb. In other climate zones the mass wall requirements also become more stringent.

Slide 23


90.1-2010 Envelope Changes

bn, fenestration orientationbf, continuous air barrierf, cool roofsEnvelope/lighting interactions

There are a number of other significant envelope addenda. Hidden slides are contained in the handouts that give more information. Addendum bn prescriptively requires more fenestration on the south and north sides of the building than the east and west sides. There are exceptions in urban areas, or where such orientation is not possible due to lotline setbacks. Bf prescribes continuous air barrier requirements that can be met by installing materials with a maximum air permeance level or an assembly limiting the air leakage to less than 0.04 cfm/square foot. The goal is less infiltration. Cool roofs are required in Climate zones 1 through 3, but there are exceptions for example, for roofs with a specific ballast weight or vegetative roofs. Finally, there are a number of addenda that span the envelope and lighting portions of the standard. So that’s a great segue to the lighting addenda.




5.5.4.5. Fenestration Orientation.

The vertical fenestration area shall meet the following requirement:Area South ≥ Area West and Area South ≥ Area East,

Addenda bnOrient Buildings with More Glass On South

Slide 25


Exceptions to 5.5.4.5:

Vertical fenestration that complies with the exception to 5.5.4.4.1 (c).(Storefronts)Buildings that have an existing building or existing permanent infrastructure within 20 ft (6 m) to the south (north in the southern hemisphere) which is at least half as tall as the proposed building.(Urban infill buildings)Buildings with shade on 75% of the west and east oriented vertical fenestration areas façade from permanent projections, existing buildings, existing permanent infrastructure or topography at 9 AM and 3 PM on the summer solstice (June 21 in the northern hemisphere).(Shaded buildings)Alterations and additions with no increase in vertical fenestration area.

Addenda bnOrient Buildings with More Glass On South

Slide 26


Addendum bfContinuous Air Barrier

Using individual materials that have an air permeability ≤ 0.004 cfm/ft2

Using assemblies of materials and components that have an average air leakage ≤ 0.04 cfm/ft2




5.5.3.1.2 Roof Solar Reflectance and Thermal Emittance. Roofs in climate zones 1 through 3 shall have one of the following:A minimum three-year-aged solar reflectance of 0.55 when tested in accordance with ASTM C1549 or ASTM E1918, and in addition, a minimum three-year-aged thermal emittance of 0.75 when tested in accordance with ASTM C1371 or ASTM E408.A minimum three-year-aged Solar Reflectance Index of 64 when determined in accordance with the Solar Reflectance Index method in ASTM E1980 using a convection coefficient of 2.1 BTU/h-ft2 (12 W/m2.K),or.Increased roof insulation levels that meet the following:Roofs: Insulation entirely above deck

Nonresidential Residential U-0.030/R-33 U-0.029/R-34

Addenda fCool Roofs

Slide 28


Exceptions to 5.5. 3.1.2:a. Ballasted roofs with a minimum stone ballast of 17 lbs/ft2 (74 kg/m2) or 23 lbs/ft2 pavers (117

kg/m2).b. Vegetated Roofs Systems that are either extensively and/or intensively vegetated, containing a

minimum thickness of 32.5 inches (76 63.5 mm) of growing medium and covering a minimum of 75% of the roof area with durable plantings.

c. Roofs, where a minimum of 75% of the roof area:i. Is shaded during the peak sun angle on June 21st by permanent components or features of

the building, or ii. Is covered by off-set photovoltaic arrays, building-integrated photovoltaic arrays, or solar air

or water collectors, oriii. Is permitted to be interpolated using a combination of parts i and ii above.

d. Metal building roofs in climate zone 3. Steep sloped roofse. roofs over ventilated attics or roofs over semi-heated spaces or roofs over conditioned spaces

that are not cooled spaces. Low sloped metal building roofs in climate zones 2 and 3. f. Asphaltic membranes in climate zone 3. Roofs over ventilated attics or roofs over semi-heated

spaces or roofs over conditioned spaces that are not cooled spaces.g. Asphaltic membranes in climate zones 2 and 3.

Addenda fCool Roofs

Slide 29


5.5.4.2.2 Maximum Skylight Fenestration Area. The total skylight area shall be less than 5% of the gross roof area.5.5.4.2.3 Minimum Skylight Fenestration Area. In enclosed spaces that are:

• i. greater than 10,000ft2, and• ii. directly under a roof with ceiling heights greater than 15 ft, and• iii. one of the following space types: office, lobby, atrium, concourse, corridor, storage,

gymnasium/exercise center, convention center, automotive service, manufacturing, non-refrigerated warehouse, retail, distribution/sorting area, transportation, or workshop.

The total skylight area shall be either;• a. a minimum of 3% of the roof area of that enclosed space with a skylight VLT at least

0.40, or• b. such that the daylight area under skylights will be a minimum of half the floor area and

provide a minimum skylight effective aperture of at least 1%.These skylights shall have a glazing material or diffuser with a measured haze value greater than 90% when tested according to ASTM D1003. General lighting in the daylight area shall be controlled as described in Section 9.4.1.4.

Addenda alSkylights Large Spaces




exampleBuilding Lighting Power Density (LPD) Changes

[Addendum “by” - completed]

Most whole building values reduced or unchanged

Addendum BY changed the lighting power allowed. Now, it’s important to remember that the Illuminating Engineering Society is a co-sponsor, and IES members made sure that proper space illuminance can be achieved using these lighting power allowances. In almost all cases, the whole building lighting power allowances are reduced.

Slide 31


Mixed reduction and increase in LPDs based on technology improvements and model corrections.

TABLE 9.6.1 Lighting Power Densities Using Space-by-Space MethodCommon Space Types

exampleSpace Type LPD Changes

The lighting designer still has the option to calculate the building lighting power allowance by taking the space-by-space allowances and summing them. Again, in most cases the allowed space-by-space LPDs went down. In addition to changing the levels, a new column was added. RCR stands for room cavity ratio – and is used by lighting designers. If a particular space is a different geometry, which results in a different RCR more lighting power may be allowed.

Slide 32


Lighting Addenda

Envelope/lighting interaction• D, AB, AL – daylighting control• Ct, dd – modify the area thresholds for top and side

daylightingAV – changes alteration threshold (10%) at which replacement lighting and controls must complyCe – requires bi-level switchingCZ – parking garage lighting controlBS – control of 50% of receptacles

For good daylighting, the windows and skylights must be properly placed on the building envelope. Addenda d, ab and al require daylighting control, and CT and DD define the area thresholds for which daylighting is required. AV significantly reduces the level for which lighting alterations take effect. Lighting control requirement changes are also significant, for example: CE requires bi-level switching some spaces, which means a level of lighting between on and off, Parking garage lighting controls are required by addendum CZ And half the receptacles must be able to automatically shut off, for example at night, per the requirements of Addendum BS. Again, there are slides available in the handouts that give more information. OK, we spent about 5 minutes total on the envelope and lighting addenda. During the June meetings in Albuquerque each presentation took about 25 minutes – and they’re available from ASHRAE. Now let’s move on to some of the mechanical, control, and modeling requirements changes.



Susanna, as a member of the mechanical subcommittee I know that you have a lot to share.

Slide 33


Addenda d, ab, and ALDaylighting Control Additions

Three separate addenda that:Require the control of electric lighting when top and side daylight is presentandRequire the installation of skylights when appropriateAdditional addenda “ct” and “dd” modify the area thresholds for top and side daylighting

Slide 34


Addendum ce“Bi-Level” Space Lighting Control

Exceptions:• Lights in corridors, electrical/mechanical rooms, public

lobbies, restrooms, stairways, and storage rooms• Spaces with only one luminaire with rated input power

less than 100W.• Spaces types with a lighting power allowance of less

than 0.6 W/ft2

Requires the controlled lighting have at least one control step between 30% and 70% (inclusive) of full lighting power in addition to all off.




Addendum avChanges to Alterations Requirements

Includes retrofits where luminaires are added, replaced, or removed.Also includes lamp plus ballast retrofitsAlterations of less than 10% of connected lighting load are exempted.

Requires that BOTH Interior and Exterior alterations comply with LPD and automatic shutoff requirements

Slide 36


Addendum czParking Garage Control

Must reduce lighting power by minimum of 30% when no activity detected within a lighting zone (< 3,600 sf)Daylight transition zone lighting (66 ft wide by 50 ft) must be separately controlled to turn lighting on during daylight hours and off at sunset.Daylight control required for luminaires within 20 feet of perimeter wall with net opening to wall ratio of 40%.Exceptions:• Daylight transitions zones and ramps without parking are exempt from

30% reduction and daylight control.• Applications using HID of 150 watts or less or Induction lamps are

exempt from 30% reduction.

Requires parking garage lighting to be automatically controlled including daylighting

Slide 37


Addendum bsReceptacle (wall plug) Control

Applies to 125 volt 15- and 20-ampere receptacles in private offices, open offices, and computer classroomsRequires automatic control using:• Time-of-day schedule,• Occupancy sensor, or• Other automatic control based on occupancy

Exceptions:• Spaces where automatic shutoff would be

safety/security issue• Spaces where all loads require 24-hour operation.

Requires that 50% of receptacles (wall plugs) in a space have automatic shutoff control




Mechanical Section

Slide 39


Mechanical

Equipment efficiencySystem design requirements

[SUSANNA] Thanks Mick. Now lets turn our attention to the mechanical section. I won’t cover all updates in the same detail, and there will be some I don’t cover. For more detail, look to the other documents included in your handouts. [SLIDE] There are equipment efficiency changes and new system design requirements. There are also control requirements, and that’s what Matt is going to cover later.

Slide 40


Equipment Efficiency

UnitaryChillersHeat rejection Fans and pumps

I’ll group the Equipment efficiency changes into Unitary, Chillers, and Heat Rejection. Fans and pumps are addressed in system design requirements. Most of the equipment listed in 90.1 will be required to have higher efficiency.




Table 6.8.1A Electrically Operated Unitary Air Conditioners and Condensing Units - Minimum Efficiency Requirements

[Susanna] Let’s look at unitary first, starting with air conditioners and heat pumps. Before we go any further, let me briefly touch on a common question. I have a hard time figuring out which categories apply to which products. [SLIDE] When in doubt, look at the test procedure referenced in the final column. Then compare it to the certification program called out on the equipment data sheets and submittal documents. This helps you make sure you’re looking at the right product category.

Slide 42


equipment efficiencyUnitary

AC and HP – air cooledIEER metric for part load

2010 Unitary addenda: S, K, N, Y, AO, S, T, BG, BU, BW, CO, CP

ASHRAE 1989

ASHRAE 2001

2005 Energy Act

9.7 9.7

8.98.5 8.5 8.3

9.7 9.710.3

9.7 9.59.2

7

8

9

10

11

12

13

14

15

16

<5 Tons 1P <5 Tons 3P 5 to 11.2 Tons 11.2 to 20 Tons 20 to 63 Tons >63 Tons

13.0 (06) 13.0 (06-08)

SEER EER/IPLV

11.2 (2010)11.0 (2010)

10.0 (2010)9.7 (2010)

(2010)

Fede

ral L

imit

(Tod

ay)

Fede

ral L

imit

(201

0)

[slide] Efficiencies for Air-conditioners and heat pumps have been improved substantially in recent years. And, they HAVE basically the entire system wrapped up into their numbers. Take a look at where they were in 1999, 2001 and now 2010. For those of you playing along at home, compared to 1999 that’s about a 17% EER improvement in the larger sizes, about 30% in the 5 to 20 ton category and 34% on a SEER basis for small, less than 5 ton equipment.

Slide 43


equipment efficiencyUnitary

What is IEER? • a new metric, the Integrated Energy Efficiency Ratio• used on unitary products to replace IPLV• designed to encourage better real world part load

performance by putting different spices in the soupi.e. manufacturers are rewarded for designs that save energy but were not reflected in the IPLV metric

IEER = 0.02A + 0.617B + 0.238C + 0.125 DA = EER at AHRI standard rating conditionB = EER at 75% net capacity, reduced ambientC = EER at 50% net capacity, reduced ambientD = EER at 25% net capacity, reduced ambient

You may also have noticed on equipment schedules a new term called “IEER”. This stands for Integrated Energy Efficiency Ratio, and it’s a new metric developed for unitary products, to replace IPLV. It was developed to encourage designs that have better part load performance. Those of you familiar with the chiller equation may recognize this format.




equipment efficiency Unitary

In 2012 (DX) and 2010 (chilled water)Single zone systems• DX ≥ 110,000 Btu/h (9.2 tons) • Chilled water AHUs with fan motors ≥ 5hp

Two-speed motors or VFDsRequired for implementing • Discharge temperature sensors or multiple stages of

compression• Care needed to meet ventilation codes

Damper position compensation for fan speedAirflow measurement and variable OA dampers

Addendum N

I’m going to mention this now, even though it also applies to non-unitary equipment, because it’s a more significant change for unitary product designs. The so-called ‘Single zone VAV’ requirement, addendum N. As of January 2012 for DX systems and January 2010 for chilled water systems, Variable-air-volume fan control will be extended to large single-zone systems. Direct expansion units 9.2 tons and higher and chilled water air handlers with 5 horsepower motors or greater are affected. This change requires either two-speed motors or variable-speed drives on the supply fan(s). Practically speaking, this means that you’ll see equipment with either discharge air temperature sensors or multiple stages of compression with a least 2 speeds on the supply fan. This is going to present some challenges for making sure that you meet the ventilation codes at part speed, especially since these systems are often installed in zones with high occupant densities and required demand-controlled ventilation. Either the damper position can be compensated for fan speed, or better yet, specify airflow measurement and coordinate the required ventilation with the outdoor air damper position.

Slide 45



Water- and evaporatively cooled AC and HPWater- and evap-cooled condensing units are now two different categories3 to 5% more stringent than 2001-2007 levels Effective 6/1/2011

Addendum CO

Water and evaporatively cooled Air conditioners and heat pump levels will be 3 to 5 percent more stringent as of June 2011. The categories have been split apart, to accommodate divergence in the rating procedures.





PTACs and PTHPs‘Non-standard’ size defined• less than 16” high or less

than 42” wide and• less than 670 in2 area

All others meet requirement

Addenda T, BW

TABLE 6.8.1D

In a federal ruling, as of October 2012, Packaged Terminal Air Conditioners and Packaged Terminal Heat Pumps will be required to meet new, aggressive efficiency levels. 90.1 has a sliding capacity scale as units get larger [CLICK -show close up of equation]. This is because standard wall sleeve sizes make it more and more difficult to add surface area for heat transfer, as cooling capacities increase.[CLICK-to remove] The other addition is a definition of a non-standard size PTAC. Standard size units in new construction must meet a higher efficiency level than replacement units having to fit into an existing wall sleeve.

Slide 47



Water-water heat pump efficiency levels <11.25 tons

Addendum BG

[SUSANNA] One class of product that until now had been outside the scope of the standard is the water-to-water heat pump. [SLIDE] The efficiency levels that must be met depend on the type of application (such as water source, ground water source, and ground source) are determined at cooling and heating mode rating temperatures typical for those applications.

Slide 48



Computer room air conditioners (CRAC)ASHRAE 127 test procedure• conditions reflect sensible (mostly) data center cooling• SCOP is defined (sensible coefficient of performance)

Addendum BU

[SUSANNA] Recall that addendum AQ expanded the scope to include systems used in what might be called process cooling applications. This allowed 90.1 to bring a new class of product into the Standard. [SLIDE] Computer room air-conditioners, sometimes called CRAC units. ASHRAE 127 is the referenced test procedure for the CRAC units. The ASHRAE test procedure has defined a term called SCOP, or sensible coefficient of performance, which calculates efficiency at conditions more reflective of the mostly sensible cooling that goes on in data centers and computer rooms. [SLIDE] Air handlers serving computer room units must meet the fan power limits in section 6-5.





Minisplits have been covered under 210-240Multi-splits (VRF) • certification program

likely fall 2010

Addendum CP

[SUSANNA] Minisplits have been covered by 90.1 for many years. [SLIDE] They are tested with AHRI 210/240, just like any other small split system. However, a similar class of equipment sometimes called a multi-split or variable-refrigerant flow (VRF) system was previously not covered.

Slide 50


equipment efficiency Unitary Addendum CP

[SLIDE] This type of split system has multiple indoor DX fan coils sharing a common compressor and condenser. Manufacturers first had to agree on a standard test procedure for a combination of indoor terminals with a condensing section, before levels could be set. [CLICK] AHRI 1230 is now published and efficiency requirements for VRF multi-splits are now in 90.1. [CLICK] And in July 2012, the IEER requirements become more stringent. VRF systems can include a heat recovery heat exchanger, or not. And there is a special category in each size break for VRF systems with heat recovery. [SUSANNA] As of the time of this program, AHRI is developing a certification program.

Slide 51


equipment efficiency Chiller

Two compliance paths for water-cooled chillers• Full load and part load metrics in both paths• Water-cooled positive displacement classed together

Addendum M

Now let’s move on to chillers. As of January 2010, Addendum M has been in effect. The big change from M is the addition of an alternative compliance path for water-cooled chillers. [SLIDE] One path has a more stringent IPLV requirement, while the other has a more stringent full load requirement. EACH PATH has a both a full load and a part load metric to meet. You might also notice that the energy units have been changed to reflect what the industry prefers.




Chiller Table 6.8.1C - excerpt

0.639 kW/ton0.450 IPLV


Centrifugals < 300 tons



600+ tons



300 – less than 600 tons

0.639 kW/ton0.490IPLV


300+ tons



150 - less than 300 tons



75 - less than 150 tons



Water cool. pos. displ. >75 tons

9.562 EER12.75 IPLV

Air cooled 150+ tons

9.562 EER12.5 IPLV

Air cooled < 150 tonsPath BPath A

Addendum M

[SLIDE] for air cooled that means EER, for water cooled it’s kW per ton, and for absorption, COP.

Slide 53



Two compliance paths for water-cooled chillers• Full load and part load metrics in both paths• Water-cooled positive displacement classed together

Air-cooled chillers part load improvementNew categories• Less than and 150+ tons air-cooled categories• 600+ tons water-cooled centrifugal category

Removed categories• Air-cooled chillers without condensers (use matched)• Reciprocating chillers now with screw and scroll

Addendum M

[SLIDE][CLICK] Other changes from this addendum were air cooled part load improvement, [CLICK] and new categories for 150 tons and greater air cooled, and 600 tons and greater centrifugals. [CLICK] The category for reciprocating chillers was removed. Recip chillers now have to meet the positive displacement water-cooled or the air cooled requirements. The other category that was removed was for Condenserless air cooled chillers. These now must meet the air-cooled requirements with a suitable, matched condenser.

Slide 54



Test tolerances and fouling• Deviations from test procedures are at the discretion of

the customer, but 90.1 values correspond to data collected using the referenced test procedure

• Performance degradations must be absorbed by the design

Starter and drive losses• Measurements occur on line side of starter or drive

Interpretations

[SUSANNA] Interpretations have been issued in recent years to define how to accommodate deviations from the defined test conditions, such as non-standard tolerances and tube fouling. Any machine changes needed for meeting non-standard test tolerances or tube fouling will remain in the design, while the performance data computed with standard test tolerances and fouling. [SLIDE] It is this performance to be compared with the required efficiency. Excessive modifications to chillers needed to accommodate customer requirements may make it difficult to meet 90.1 requirements, and any performance degradations these changes cause at standard test conditions must be compensated for in the equipment design. [CLICK] Also, ASHRAE affirmed that the AHRI test procedure requires that starter and drive losses are included in the chiller efficiency.





Different treatment for glycol• No more blanket exception from scope, depends on

operating temperaturesPositive displacement: greater than 32°F leaving evapCentrifugal: 36°F or higher leaving evap (and other reqs.)Absorption: 40°F or higher leaving evap

• Dual mode chillers, where one or both modes are outside the covered temperatures, continue to be out of scope

Addendum BL

[SUSANNA] Other changes to the chiller section will bring more chillers under the scope of the standard. The first one is in how we treat chillers with glycol for freeze protection, but that operate at a “normal”, otherwise covered, chilled water temperature. [SLIDE] In the past, chillers with a freeze point of 27 degrees or lower had enough glycol in them to exempt them from meeting the standard. In reality, designers add glycol to air cooled chillers in cold climates, even though there are no design changes to the chiller. The test procedure AHRI 550/590 always uses water. Efficiency levels are to be calculated for these chillers with water as the test fluid, when comparing to the table 6.8.1C values in 90.1. [SUSANNA] This change is slightly more nuanced for centrifugal chillers. When a centrifugal chiller has glycol in it, heat transfer is degraded. More lift is required of the compressor and this changes the design slightly, and its ability to meet the performance in Table 6.8.1C when tested with water. The additional efficiency needed to overcome this loss must be absorbed by the chiller design, which serves to discourage unnecessary use of glycol and improves the stringency of the Standard. [SLIDE] [CLICK] Dual mode chillers with glycol, where one mode violates the covered temperatures, continue to be out of scope. An example of out of scope would be ice-making chillers or chillers making brine cold enough, depending on the type of chiller. The covered conditions have been changed in both BL and BT.

Slide 56



Scope changes — centrifugals• 36°F or higher leaving evaporator• 115°F or lower leaving condenser temperature• 20 to 80°F lift range (leaving cond minus leaving evap)

New non-standard centrifugal equation• Tables removed – equation only• Spreadsheet calculator on User’s Manual CD• Examples in User’s Manual (see support material)

Addendum BT

[SUSANNA] Let’s look closer at the covered conditions for centrifugals. The next change is the non-standard centrifugal equation and the temperatures and flows that are within the scope. [SLIDE] The equation is now more robust and as chillers deviate from standard conditions, there is a slight efficiency improvement. The equation is valid over a wider range of performance. Leaving evaporator fluid temperature 36 degrees F or higher, leaving condenser 115 degrees F or lower, and a range for lift of 20 to 80. Lift is now defined by 90.1 as leaving condenser minus leaving evaporator temperature. [SUSANNA] Roughly 98% of centrifugal chillers sold will now be subject to meeting 90.1. As an example, 85.1 design entering condenser water temperature can no longer be used to avoid the 90.1 requirements. [SLIDE][CLICK] All of these changes together made it difficult to keep the non-standard adjustment tables for centrifugals within the pages of the standard. Instead, a spreadsheet tool will be included on the User’s Manual CD and examples in the printed version of the User’s Manual. I included a version of this in your supporting materials.




equipment efficiencyHeat Rejection

Limits on centrifugal fan cooling tower use• Above 1,100 gpm, centrifugal fan towers have to meet

axial fan power levels (≥ 38.2 gpm/hp)• Some exceptions

Closed circuit cooling towers• Requirements added (14 gpm/hp axial, 7 gpm/hp prop)• Rating conditions 90-102°F water, 75°F entering wb

Liquid-liquid heat exchanger certification • No efficiency requirements, test procedure AHRI 400• More heat exchanger manufacturers are choosing to

certify, rather than pay for independent lab testing

Addenda A, L, U, and AD

[SUSANNA] Heat rejection is another area that saw a significant change. [SLIDE][CLICK]There are now limits on the use of centrifugal fans in cooling towers, once the tower handles more than eleven hundred gpm. Towers above this flow rate now have to meet the more stringent axial fan power level of 38.2 gpm per horsepower. [CLICK]A new category was added for closed circuit cooling towers. Closed circuit cooling towers have their own test conditions more reflective of the range and approach. And again, axial fan equipped closed circuit cooling towers have a more stringent level than centrifugal fan towers. [CLICK]Liquid to liquid heat exchangers now have a referenced test procedure. This has driven a lot more heat exchanger manufacturers to submit their products to a certification program, and gives a common reference point for performance. No target efficiency levels have been set, but could be in the future.

Slide 58


summary Equipment Efficiency

Equipment efficiencies are more stringent• Chillers: once a path is chosen both full and part load

requirements must be met• Unitary equipment now uses Integrated Energy

Efficiency Ratio (IEER)New coverage• Computer room air conditioners• Variable refrigerant flow (VRF) equipment• Closed-circuit cooling towers• Water-water heat pumps

[MICK] Thanks, Susanna. [SLIDE][CLICK] The bottom line is that for almost every piece of equipment referenced in ASHRAE/IES 90.1, efficiency requirements have become more stringent. There are two alternate paths for chillers. Once the path is chosen, both full and part load requirements must be met. In addition to increased stringency, a number of the new requirements are based on new AHRI standards, that have new metrics – specifically IEER – or integrated energy efficiency ratio. [CLICK] In addition computer room air conditioners, variable refrigerant flow equipment, water-to-water heat pumps, and closed circuit cooling towers are included in 90.1 for the first time. But 90.1 is about a lot more than just equipment efficiency. Susanna, please take us through some of the changes in system requirements.

Slide 59


System Design

HydronicsOutdoor airSystem fan power

[SUSANNA] When it comes to energy savings, a good portion of the mechanical section’s impact relates to system design requirements. I’ve classified these into [SLIDE] three general categories: hydronics, outdoor air, and system fan power.




system designHydronics

Water-cooled unitary• Shut-off valves required in all (formerly only required in

water source hp, now also water cooled self contained)• If system power >5hp, have to have VFD pump

Lower threshold for VFD on pump motors• Formerly only on 50hp pumps with 100’ head, now each

5+hp pump when system power is at least 10hpBooster pumps (limits on pressure-reducing valves)• Measure pressure and vary pump speed or stage

pumps

Addenda AK and CV

[SUSANNA] I’ll start with the hydronics changes. [SLIDE][CLICK] Condenser water flow for unitary systems can only be variable if (at least) two-position valves are included at the units, so they don’t take water when they’re turned off. Since 1999, water-source heat pumps have been required to have these valves, but now water-cooled unitary air conditioners do too. An example of this product is a water-cooled self-contained unit. These systems are also subject to the variable flow requirements. If the system pump power is greater than 5 hp, you have to have a VFD on the pump motor, or similar performance. [CLICK] And in other types of hydronic systems, the threshold has plummeted for requiring a VFD on the pump motor. In the past, at 10hp for the system you had to at least ride the pump curve. At 50 hp pump, with at least 100’ of head, you had to have a VFD. Now, when individual pumps are 5 or more horsepower, and the system power is at least 10 hp, you have to have VFD like performance. [CLICK] Booster pumps are also now addressed. These are pumps in tall buildings used to boost pressure at an intermediate point. Pressure reducing valves are used to create the actual pressure needed by the coil control valves, for example on each floor. There are now limits on these pressure reducing valves, and you must measure the pressure and vary the booster pumps to better follow the load.

Slide 61



Pump pressure optimization• DP setpoint no more than 110% of design flow’s DP• Reset DP setpoint until one valve nearly wide open

Pipe and pump sizing • Based on pressure limits and economics• Applies to both chilled water and condenser water• Pump head must be calculated for sizing pumps

Addenda V, AF, and CC

[SUSANNA] With all the new requirements for variable speed pumping, it follows that 90.1 now requires pump pressure optimization. [SLIDE] [CLICK] There are two main requirements here. One: the differential pressure setpoint can be no more than what corresponds to 110 percent of the design flow. The DP setpoint has to be reset until one valve is nearly wide open. Matt will go through this in greater detail in the controls section. [CLICK] There are new maximum allowable flows in nominal pipe sizes. The allowances change based on the annual hours of operation of that system type, and whether it is variable flow slash variable speed or not. And Pump head calculations must be completed prior to sizing pumps. You can’t just guess at pump sizing anymore. This is similar to the requirement for load calculations.




system designHydronics Addenda V, AF, and CC

[SLIDE] The pipe sizing limits are based on limiting the amount of frictional losses included in the sizing of system pumps. The table shown here met the economic justification rules of 90.1. It applies to both chilled water and condenser water systems. One way to reduce the pipe size you’re allowed to have is to increase the delta T (cooling capacity) of the water. The ASHRAE GreenGuide suggests 12 to 20 degree delta T on chilled water, and 12 to 18 degree delta T on condenser systems. If you follow these guidelines you likely won’t have any trouble meeting the permitted flow rate for a given pipe size, and can reduce installed and/or operating costs..

Slide 63



Pipe insulation• Biggest changes are in steam and hot water piping• when pipes are in the interior walls between conditioned

spaces. • Non-metallic pipe optional path if > schedule 80

Addenda BA and BI

Another change to hydronics system design is pipe insulation. Chilled water piping had modest change, but hot water and especially steam pipes have significant upgrades. There are exceptions, for example when pipes are in the interior walls between conditioned spaces. And if non-metallic pipe is used, and it’s greater than schedule 80 thickness, you are permitted to reduce insulation thickness to an equivalent heat transfer per linear foot.

Slide 64



Table footnotes allow adjustments for conductivity and thickness reductions for buried pipe.




summarySystem Design: Hydronic

VSD-like performance required on much smaller systemsPump pressure optimization is requiredMaximum flow rates definedPipe insulation more stringent

[MICK] In short, a lot more systems will use technologies such as variable speed drives on pumps – and Matt will cover the new requirement for pump pressure optimization. From a piping standpoint, the minimum pipe size is now prescribed – and pipe insulation requirements are more stringent. And there are also a significant number of airside system changes, right?

Slide 66


System Design: Airside

EconomizersEnergy recoveryDampersVentilation and exhaust

[SUSANNA] Correct. I’ve classified them into four main sections: [SLIDE] economizers, energy recovery, dampers and ventilation and exhaust. Matt will cover the controls changes for ventilation in a few minutes, so I’ll focus on the design requirements.

Slide 67


airside system design Economizers

In all climates, except • 1A-hot, humid: such as South Florida, parts of Hawaii,

the Caribbean, India, Indonesia• 1B-hot, dry: such as Dubai, Saudi Arabia

Addenda AU, BU, and CY

[SLIDE] A sweeping addendum changed economizer requirements for somewhere close to 40% of the installed cooling systems in the United States. That is, economizers are now required in most climate zones.





Zone 1 includes Hawaii, Guam, Puerto Rico, and the Virgin Islands

Economizer required if individual fan plus coil ≥ 54,000 Btuh(4.5 tons)


[SLIDE] Two exceptions are climate zones 1a and 1b, which include South Florida, the Caribbean, parts of Hawaii, China, India and Indonesia, among others.

Slide 69





Down to 54,000 Btu/hMust be integrated • economize, then supplement with mechanical cooling

Efficiency tradeoff for applied as well as unitary• % improvement over full or part load metric


[SLIDE] Smaller systems will need them as well. If the individual fan and coil is 54,000 Btu/h (4.5 tons) or greater, then an economizer is required. [CLICK] One way that more climates were justified is by dropping the exceptions for integrated economizing. This means that the economizer will be the first stage of cooling, followed by mechanical cooling, until the high limit shutoff point. The high limit changes by climate zone.

Slide 70


airside system design Economizers Addenda AU, BU, and CY

economizer tradeoff with equipment efficiency

[SLIDE] There ARE lots of exceptions. If you don’t WANT an economizer, and you don’t meet one of the exceptions, you can trade off the economizer with an improvement in equipment efficiency. The tradeoff has been expanded to include more types of mechanical cooling equipment, including applied systems.







Down to 54,000 Btu/hMust be integrated • economize, then supplement with mechanical cooling

Efficiency tradeoff for applied as well as unitary• % improvement over full or part load metric

Some data centers will need economizer (water or air)


[SLIDE][CLICK] Based on the scope change that Mick mentioned, and an addendum written by TC 9.9 Mission Critical Facilities, some data centers will now be required to have either an air- or a water-side economizer.

Slide 72



Heat recovery exception expanded• No longer requires 6,000,000 Btu/h heat rejection and

1,000,000 Btu/h service water heating• May be useful on large air-cooled systems with DOAS

e.g. VRF, fan coils with air-cooled chiller (54,000+ terminals)

• HR may be preferred in some climates, applications• Requires heating peak service hot water draw to 85°F • or 60% of the peak service water heating load

[SUSANNA] As I mentioned there are a number of exceptions, one of which was expanded. Heat recovery is often at odds with economizer operation. This is because a number of hours when heating is needed happens when the cooling load is being shed by the economizer. You can’t have all of the benefits of both economizing and condenser heat recovery. And, to reflect the new systems that are going to need economizers,[SLIDE] the heat recovery exception directed at large, water-cooled systems didn’t really work. There will be some systems you might need an economizer for, but they normally don’t have ductwork sized for economizer operation. Generally these are systems with dedicated outdoor air systems, such as VRF, Water source heat pumps, large fan coils, etc. [SUSANNA] Granted, most of these will fall under the 54000 btu per hour threshold, but some will not. These systems can be designed to alternatively include heat recovery or water side economizers.

Slide 73


airside system design Energy Recovery

Energy recovery ventilation system• Threshold changes• Climate specific• Exempted from ventilation optimization control

Addendum E

[SLIDE] Next, energy recovery ventilators are required in a lot more situations. There are three intersecting thresholds: climate, a percentage outdoor air, and the supply air flow rate. Naturally, there are exceptions. [SLIDE] The ventilation optimization control that Matt will discuss is not required if the system meets the threshold and other requirements for energy recovery ventilators.




airside system design Energy Recovery

Example: 40% OA system with 5,000 cfm• prior to 2010, less than 70% OA, so no ERV required• now, ERV required in climates 1A through 6A, 7, 8

[SLIDE] For example, take a 5000 cfm system with 40 percent outdoor air. In the past, since it’s under 70 percent outdoor air, ventilation system energy recovery would not have been required, in any climate. Now, energy recovery ventilation is required in all humid climates, 1A through 6A, and cold climates 7 and 8. Only dry and marine climates are exempt in this case.

Slide 75


airside system design Dampers

Motorized dampers required on ventilation air intakes in cool and cold climatesClimate 5a now requires low leak dampers (4 cfm/ft2)Leakage class per damper style unchanged

Addenda AT and CB

Motorized dampers are now required in a few more situations. Outdoor air intake dampers in cool and cold climates now have to be motorized.

Slide 76


airside system design Dampers

Zone 5a

5a change — low leak dampers (Class 1) on:• exhaust/relief dampers if three or more stories• ventilation air intakes, all buildings

[SUSANNA] One example of the changes to the damper requirements is that low leak dampers are now required in climate zone 5a, [SLIDE] a fairly broad swath of the country that includes portions of Illinois, Indiana, Iowa, Ohio, Nebraska, Pennsylvania, and several states in New England. You can still use gravity or backdraft dampers for ventilation intakes in climates 1 through 3, and for exhaust and relief dampers in buildings less than three stories in height.




airside system design Fan Power Limitation

Exhaust system credits• Fully ducted return and.or exhaust air

system in lab and vivariums, 0.5 in w.g. • Exhaust system serving fume hoods,

0.35 in. w.g. • Lab and vivarium exhaust systems in

high-rise buildings 0.25 in. w.g. per 100 ft of vertical duct exceeding 75 ft

Pressure-dependent spaces can reheat more if they have VAV meeting 6.5.7.2

Addenda P, AS

[SUSANNA] The final change I’m going to highlight in the mechanical section is consolidation and clean up in the fan power limitation. Allowances for exhaust systems were poorly defined. This was really a hardship for several types of buildings, specifically laboratories, hospitals, and vivariums. [SLIDE] The changes are as follow: fully ducted return and.or exhaust systems in labs and vivariums are given 2.15 in. w.g. In addition, the blanket exception to the fan power limitation for fume hoods has been removed. Instead, exhaust systems serving fume hoods get 0.35 in w.g. and lab and vivarium exhaust systems in high rise buildings get a quarter inch per 100 feet of vertical duct exceeding 75ft.

Slide 78


airside system design Fan Power Limitation

Energy recovery ventilator pressure drop credit tied to effectiveness• if more effective, can have more pressure drop and

have equivalent system energy performanceCoil run around loops treated differently, reflecting that use in applications where other types of ERV are not feasible

Addendum DJ

[SUSANNA] An astute engineer I know noticed how difficult it was to meet the fan power limit with a highly effective ERV. [SLIDE] He proposed a solution: a pressure drop credit equation for ERVs that compensates for effectiveness. A higher pressure drop adjustment is allowed for more effective heat recovery.

Slide 79


airside system designFan Power Limitation

Definition of VAV for fan power column use• single zone VAV has to use the constant volume limit

Addendum CA

[SLIDE] When the single-zone VAV change occurred, 90.1 realized it needed to revise the definition of which column applies to VAV systems that don’t have dampers increasing the system pressure. Single-zone systems are required to use the more stringent constant volume fan power limit.




airside system designOther Changes

Motor efficiency (general purpose)Elevator lighting and ventilation allowancesGarage ventilation controlsDuct leakage to seal class A• tested sections selected by the building owner

Kitchen exhaust hoods— large ones listedRadiant panels—insulate ineffective surfacesHeat pump pool heaters Furnace and water heating cleanup

Addenda K, Y, AE, AJ, AO, AX, BK, CQ, DF, DI

[SUSANNA] The motor efficiency change will affect other products besides fans. The general purpose motor type that’s affected is defined by NEMA, and an excerpt of this is included in 90.1 for ease of reference. Other changes in the 2010 standard relate to [SLIDE][CLICK]elevator lighting and ventilation allowances, [CLICK]garage ventilation controls, [CLICK]seal class A for duct leakage, [CLICK] large kitchen exhaust hoods, [CLICK]insulated ineffective surfaces on radiant panels, [CLICK]heat pump water heaters, [CLICK]other water heaters and furnaces.

Slide 81


airside system design Summary

Economizers now required in most climate zonesAirside energy recovery will be required in many more systems and based on• Climate zone• % OA at design

[MICK] Outside of controls, which Matt will cover, the two major changes in airside system design is that economizers are now required in all but the hottest locations, and airside energy recovery will be required on significantly more systems – and the requirement is based on climate zone and % outdoor air at design cooling conditions. Let’s move on.

Slide 82


Controls




Controls and ASHRAE 90.1-2010

Existing controls requirements • Fan pressure optimization• Demand control ventilation (DCV)

Changes to controls requirements• Ventilation reset• Pump pressure optimization• Supply air temperature reset• VAV minimum airflow/reheat minimums

[MATT] Today we will be discussing some existing control strategies required by ASHRAE 90.1 as well as new requirements for 2010. [SLIDE][CLICK] We’ll start with quick review of currently required control strategies specifically Fan Pressure Optimization and Demand Control Ventilation [CLICK] Then we’ll discuss some of the changes to control strategies including: Ventilation Reset Pump Pressure Optimization Supply Air Temperature Reset VAV Minimum Airflow

Slide 84


existing requirementsFan Pressure Optimization

Required since by ASHRAE 90.1 since 1999Goal:• Control system static pressure to the lowest level while

maintaining zone airflow requirements; thereby minimizing fan energy consumption.

What is needed to implement?• Communicating controls on the VAV boxes• Static pressure sensor• Building automation system

[MATT] We’ll start with current requirements, the first of which is Fan Pressure optimization. [CLICK] Fan pressure optimization has been required since 1999 [CLICK] The goal of Fan pressure optimization is to control system static pressure to the lowest level while maintaining zone airflow requirements. By controlling static pressure, we can reduce fan speed and thereby minimize energy consumption. [CLICK] The components needed typically include: Communicating controls on the VAV boxes, A Static Pressure Sensor, and a building automation system.

Slide 85


existing requirementsFan Pressure Optimization

fan speed

communicating BAS

damper position

ductpressuresensor

supplyfan

P

damper position

Let’s review an illustration. [CLICK] In this example, the building automation system continually communicates with the individual VAV box controllers, looking for the one with the most-open damper. [CLICK] The fan’s static-pressure setpoint is reset lower and lower until this particular VAV box is nearly wide open. During this process, total supply airflow remains constant because each box opens to maintain its required airflow, but static pressure in the supply duct is reduced. [CLICK] The result is that the supply fan generates only enough static pressure to push the required quantity of air through the “critical” VAV box. In addition to the fan energy savings, this method assures that zones cannot be starved for air.




Controls and ASHRAE 90.1 - existing requirements

Fan Pressure Optimization

More information available:• Engineer’s Newsletter Live presentation from

November, 2009 titled “Air-Handling Systems, Energy and IAQ”

• Engineer’s newsletter article “Energy-saving control strategies for rooftop VAV systems, 2006, volume 35-4”

For a more details on Fan Pressure Optimization and its benefits, we have two excellent sources of information listed in your bibliography.

Slide 87



Demand Control Ventilation (DCV)Background:• VAV systems are designed to bring in at least the minimum

outdoor airflow at worst case condition• At any other condition, design airflow results in over-

ventilationGoal: • Reduce over-ventilating a space by resetting the level of

outdoor air introduced during times when occupancy is lower than design conditions

[Matt] Next, let’s review another current requirement, Demand Control Ventilation at the Zone level. [CLICK] In a typical VAV system, the air handling unit delivers a mixture of outdoor and recirculated air to individually-controlled zones. Ventilation systems are designed to bring in at least the minimum required outdoor airflow to properly ventilate all zones at the worst case condition. This means that at any other condition, the same intake airflow results in over-ventilation.

Slide 88



DCV MethodsOccupancy SensorsOccupancy SchedulesCO2 SensorsEach method is appropriate for different types of zones

[MATT] ASHRAE Standard 62 permits the dynamic reset of outdoor airflow as operating conditions change. There are several methods that can be used to help determine the dynamic reset of outdoor airflow [CLICK] Occupancy sensors where whenever the space is detected to be unoccupied, lower ventilation setpoints can be used. [CLICK] Occupancy schedules where ventilation setpoints can be determined based on predictable, scheduled occupancies. [CLICK] CO2 sensors, where ventilation setpoints are adjusted according to the measured CO2 level of a space. [CLICK] A good strategy is to use CO2 sensors on densely occupied rooms and rooms where population varies significantly, while using time of day schedules for areas that are more consistently occupied or unoccupied. [MATT] Finally, occupancy sensors might be used for rooms like private offices that are frequently unoccupied during normal operating hours.





Demand-Controlled Ventilation (DCV)

Required at zone level if:• Larger than 500 ft2

• Design occupant density greater than 40 people per 1,000 ft2

• Served by systems with one or more of the following

– An air-side economizer– Automatic modulating control of the outdoor air damper

or– A design outdoor airflow greater than 3,000 cfm

[CLICK] At the zone level, Demand controlled ventilation is required for spaces greater than 500 ft2 [CLICK] and when occupancy rates are greater than 40 people per 1,000 ft2. Also, [CLICK] the system serving the space must include an airside economizer, controls for the outdoor air damper, or a design airflow of greater than 3000 cfm.

Slide 90


Controls and ASHRAE 90.1 - existing requirementsSystem Level: Ventilation Optimization

Multiple zone VAV systems with DDC shall• automatically reduce outdoor air intake flow below

design rates in response to changes in system ventilation efficiency as defined by ASHRAE Standard 62.1, Appendix A.

Exceptions• systems required to have energy recovery in 6.5.6.1• some dual-path systems, such as dual-duct dual-fan or

fan-powered VAV systems• systems where the design exhaust airflow is more than

70% of the design outdoor air intake airflow

[MATT] Multiple zone VAV systems with DDC shall automatically reduce outdoor air intake flow below design rates in response to changes in system ventilation efficiency as defined by ASHRAE Standard 62.1, Appendix A. Exceptions include systems required to have energy recovery in 6.5.6.1 some dual-path systems, such as dual-duct dual-fan or fan-powered VAV systems systems where the design exhaust airflow is more than 70% of the design outdoor air intake airflow

Slide 91


Controls and ASHRAE 90.1 - existing requirementsSystem Level: Ventilation Optimization

OA

CO2 OCC OCC

• Required ventilation (TOD, OCC, CO2)• Actual primary airflow (flow ring)

DDC VAV controllers

SA RA

air-handling unit withflow-measuring OA damper• Reset outdoor airflow

communicating BAS• New OA setpoint

…per ASHRAE 62

CO2TOD TOD

[MATT] This system level ventilation optimization is a new requirement for 2010. [SLIDE] Here’s an example of how it might be implemented. [CLICK] The building automation system periodically solves the multiple-zone system equations defined in ASHRAE 62.1. [CLICK] The building automation system then sends the calculated outdoor airflow set point to the air handling unit controller, which modulates the outdoor-air damper to maintain this new set point. The system ensures each zone receives at least its minimum required outdoor airflow. [SUSANNA] The best way to ensure you’re ventilating no more than you need to is through outdoor air flow measurement. What’s not required is to dynamically reset the critical zone box position to minimize the system outdoor air fraction. Those of you looking for extra energy savings may want to look at this option, which is permitted under 6.5.2.1. Matt – can you give us an example of a system that could have demand control ventilation at the zone level and ventilation optimization at the system level?




lounge restroom

storage office

office conference rm computer roomreception area elev

ator

s

vestibule corridor

ventilation optimizationZone Level: DCV

communicating BAS

CO2

CO2

OCC

OCCAHU

TOD TOD

[MATT] Sure Susanna. As discussed, flexibility is allowed when choosing the method used for controlling zone ventilation rates – [SLIDE] in this example, CO2 sensors, occupancy sensors, and time of day schedules are used. [CLICK] In addition to resetting the zone outdoor airflow with changes in occupancy, each VAV controller can continuously monitor primary airflow being delivered to the VAV box. The fraction of outdoor air currently required is then calculated for each zone. [CLICK] These zone-level ventilation requirements are combined together in an overall ventilation reset strategy at the system level. For a more detailed review of system level ventilation reset and demand control ventilation at the zone, refer to the Engineer’s newsletter article mentioned previously. Next, let’s look at Pump pressure optimization. A new requirement for 2010.

Slide 93


Controls and ASHRAE 90.1Pump Pressure Optimization

Control system pump pressure to the lowest level while maintaining chilled (or hot) water flow requirements— minimize pump energyWhen is it required?• Systems having a total pump system power exceeding 10 hp

Reduce pump flow rates to 50% or less of the design flow rate • Individual chiller water pumps exceeding 5 hp

Limit demand to less than 30% of design wattage at 50% design water flow

• When more than 3 water control valves are usedWhat is needed to implement?• Communicating controls on the AHU or terminal unit valves• Pressure differential controller• Building Automation System

[CLICK] When variable-flow pumping is used in either the chilled-water or hot-water distribution system, a method is needed to control the pump capacity. Similar to the supply fan in a VAV system, the pump is often controlled to maintain a set pressure differential at some location in the piping system. In some systems, a differential pressure transducer is located between the inlet and the discharge of the pump, while in others it is located at the most distant point in the piping system. The goal of Pump Pressure Optimization is to reduce pump pressure to the lowest level while maintaining flow requirements, thereby reducing energy consumption. [CLICK] Pump pressure optimization is required when the system includes control valves designed to modulate open or closed as a function of load. In this case, when system pumping power exceeds 10 hp, the pump flow rates must be reduced to 50% or less of design flow rate. When an individual chiller’s pump exceeds 5 hp, the pump motor must be able to limit its demand to no more than 30% of design wattage at 50% of design water flow. [CLICK] To implement this control strategy using DDC controls, the system will need: * Communicating controls on the AHU or terminal unit modulating valves * Pressure differential controller * Building automation system




Controls and ASHRAE 90.1Pump Pressure Optimization

Air Handling Units

control valveswith communicating controllers

communicating BAS

pressure differential controller /transmitter

Let’s look at a quick illustration [SLIDE] The BAS continually polls the individual controllers, [CLICK] looking for the valve that is the furthest open. The pump-pressure setpoint is then periodically reset [Click] so that at least one valve is nearly wide open. The result is that the pump generates only enough pressure to push the required quantity of water through this “critical” or furthest open water valve. This strategy results in less pump energy use by allowing the pump to operate at a lower pressure at part-load conditions.

Slide 95


Controls and ASHRAE 90.1Supply Air Temperature Reset

Background: • HVAC systems designed to meet peak cooling loads• Cooling load is many times below peak conditions• Load can be met with a higher supply air temperature

Goals:• Decrease compressor energy usage• Decrease reheat• Increase the effectiveness of economizer

Control Sequence• Outside air temperature• Critical zone Load

Next, let's look at Supply Air Temperature Reset [CLICK] Generally, HVAC systems are designed to meet peak cooling loads. However, in most systems the cooling load is often below peak conditions and can be met using a higher supply air temperature. [Click] Some of the reasons to use Supply Air Temperature Reset include: [CLICK] It Decreases compressor energy usage. Increasing the supply-air temperature reduces compressor energy because it allows the compressor to unload or cycle off. [CLICK] It Decreases reheat energy for those zones with very low cooling loads. When the supply airflow has been reduced to the minimum setting of the VAV box, raising the supply-air temperature also decreases the use of reheat energy. [CLICK] Finally, it Increases the effectiveness of economizers because they will be used more often at higher ambient temperatures. When the outdoor air is cooler than the supply-air setpoint, the compressors are shut off, and the outdoor and return-air dampers modulate to deliver the desired supply-air temperature. A higher supply-air temperature setpoint allows the compressors to be shut off sooner and increases the number of hours when the economizer provides “free cooling.” [Click] There are two types of control strategies used to reset Supply Air Temperature: Using the outside air temperature as the indicator for when to reset and, Using the critical zone load as a signal to reset There are many tradeoffs between compressor energy, reheat energy, fan energy, and space humidity levels to consider when designing a supply air temperature reset strategy. Each system will need to be analyzed to reconcile the tradeoffs, which are often best balanced by first reducing supply airflow, taking advantage of the significant energy savings from unloading the



fan. Then, after fan airflow has been reduced, raise the supply-air temperature to minimize reheat energy and enhance the benefit of the airside economizer. While one could think of numerous control schemes for supply-air-temperature reset, the simplest approach is likely the most commonly applied. Let’s look at a common method used to reset Supply Air Temperature - reset based upon outdoor dry bulb temperature. [Slide]

Slide 96


Controls and ASHRAE 90.1Supply Air Temperature Reset – OADB

55 60 6550 807570outdoor dry-bulb temperature, °F

SA

tem

pera

ture

setp

oin

t, °

F

61

60

59

58

57

56

55

[CLICK] When resetting based upon outdoor dry bulb temperature, the reset high limit is set to 70 degrees Fahrenheit. When the outdoor dry-bulb temperature is warmer than 70, no reset takes place and the supply-air set point remains at its design value of 55. At temperatures above 70 degrees, the outdoor air provides little or no cooling benefit for economizing, and the cooling load in most zones is likely high enough that reheat is not required to prevent sub-cooling the space. Additionally, the colder supply-air temperature allows the system to provide sufficiently dry air to the zones, improving part-load dehumidification. [Click] Next, when the outdoor dry-bulb temperature is between 60 and 70 degrees, the supply-air temperature set point is reset at a 2-to-1 ratio. That is, for every 2 degrees change in the outdoor temperature, the supply-air set point is reset upward 1 degree. In this range, reset enhances the benefit of the economizer and it is likely that some zone-level reheat can be avoided. [CLICK] Finally, when the outdoor temperature is colder than 60 degrees, no further reset occurs, and the set point remains at 60. [Matt] Limiting the amount of reset to 60 degrees, allows the system to satisfy cooling loads in interior zones without needing to substantially oversize VAV terminal units and ductwork. Now, let's look at another reset strategy. [Slide]




Controls and ASHRAE 90.1Supply Air Temperature Reset – Critical Zone

lounge restroom

storage office

office conference rm computer roomreception area elev

ator

s

vestibule corridor

BAS

TT

TTTT

TTTTTT

Supply Air Temperature reset based upon representative building loads is also allowed. In this case, reset is activated based upon the temperature in the critical zone. The critical zone is the one that is most at risk of overcooling, which would require activating local reheat. A building automation system monitors the temperatures in all the zones. The critical zone is determined to be the one with a temperature closest to its heating setpoint. Based upon a signal from the BAS, the rooftop unit resets its supply-air-temperature setpoint to prevent the critical zone from requiring reheat. [Click-Slide]

Slide 98


Controls and ASHRAE 90.1Supply Air Temp Reset – Considerations

Raises humidity levels in the zones• Climate zones 1a, 2a, and 3a are exempted from using supply air

temperature reset in ASHRAE 90.1 2010• May incorporate zone humidity into reset sequence

Zones with constant loads must be designed for fully reset SAT• Enables SAT reset while still providing needed cooling to these

zones• May require larger VAV terminals and ductwork

Increases fan energy• Supply air is warmer• Zones that require cooling will need more air• Employ fan-pressure optimization

Supply Air Temperature Reset strategies should be analyzed for the particular system to determine the tradeoffs in energy savings. When considering using supply-air-temperature reset in a rooftop VAV system, first review the system to determine if the savings in compressor and reheat energy will outweigh the increase in fan energy. [CLICK] Also, consider the following: [CLICK] In non-arid climates, warmer supply air means less dehumidification at the coil and higher humidity levels in the zones. [CLICK] Climate zones 1a, 2a, and 3a are exempted from using supply air temperature reset. [CLICK] 90.1 also allows suspension of supply air temperature reset using humidity as a factor in the control sequence. [SUSANNA] [CLICK] Also, “zones which are expected to experience relatively constant loads, such as electronic equipment rooms, shall be designed for the fully reset supply temperature”. This requirement: [CLICK] Enables reset while still providing needed cooling to these zones [CLICK] May require larger VAV terminals and ductwork. Finally, [CLICK] When supply air is warmer, [CLICK] zones that require cooling will need more air to offset the cooling load. This increases supply fan energy. [CLICK] Remember to use the fan-pressure optimization strategy to minimize the penalty of increased fan energy when the supply-air temperature is raised.




Controls and ASHRAE 90.1VAV Reheat Limits

For VAV reheat systems, here are two ways to meet the reheat limit• 30% minimum airflow setting (maximum reheat)

• can go lower than this airflow in cooling mode• New: alternate sequence for VAV with reheat –

• raises amount of reheated air to 50% for heating provided 20% airflow in dead band between heating and cooling and modulated between.• requires a discharge air temperature sensor

• These limits can be exceeded if site-sourced or site-recovered energy is used

[MATT] Finally, let’s take a look at VAV reheat limits. The control sequence must not allow: Reheating or Recooling of air that was previously heated/cooled Simultaneous mixing of previously heated or previously cooled air or other simultaneous operation of heating and cooling systems in the same zone. However; there are two control methods that can be used to meet the requirement: [slide] The first sequence allows for 30% airflow to be reheated. and An alternative control sequence which allows for 50% reheat maximum for heating and a 20% maximum for the dead band between heating and cooling. [Susanna] If you use site recovered or site sourced energy, you can exceed these limits. Let’s review the sequences of operation for each method. In the case of a VAV box with reheat, the VAV box contains an air damper, a flow sensor, communicating controls, and an electric or hot-water heating coil. [Slide]

Slide 100


Controls and ASHRAE 90.1Reheat Minimums

20%

30%

Here’s the control sequence we been using for a VAV box for decades. When the space calls for cooling, primary airflow is gradually reduced as the cooling load in the space decreases. When the primary airflow reaches the minimum airflow setting for the unit, and the cooling load continues to decrease, the heating coil warms or tempers the air to avoid overcooling the zone. When the zone heating load requires the air to be delivered at a temperature warmer than the zone, the primary airflow may be increased to a higher minimum setting than is used during the cooling mode, but no higher than 90.1 allows for simultaneous heating and cooling, for example 30 percent. Trane and others have had two minimum airflow settings in VAV boxes available for years. This “heating minimum airflow” setting is needed because when warm, buoyant air is supplied from the ceiling, increased airflow is required to effectively mix the air and avoid temperature stratification in the occupied portion of the zone. The other reason is for safe and proper operation of an electric heating coil. [susanna] One of the overlooked things about having the two different settings in the VAV box, is you can reduce airflow in cooling lower than the airflow setting that corresponds to the maximum reheat limit [click], so long as your other objectives like ventilation can be achieved. If you just have one setting available, or you set them both the same, this isn’t possible. And that’s the reason why the alternative sequence was developed. Matt let’s



go through that one. [Click]

Slide 101



Less

Coo

ling

Mor

e Co

olin

g

20%

50%

[MATT] OK so here’s the new method that can be used for controlling a VAV reheat terminal. [SLIDE] When the zone requires cooling, the control sequence is unchanged; primary airflow is varied between maximum and minimum cooling airflow to maintain the desired temperature in the zone. When primary airflow reaches the minimum cooling airflow setting, and the cooling load continues to decrease, the heating coil is activated to warm the air to avoid overcooling the zone. As more heat is needed, the controller resets the discharge-air temperature setpoint upward to maintain zone temperature at setpoint until it reaches a defined maximum limit. Notice this control sequence requires a discharge-air temperature sensor installed for each VAV terminal. The discharge temperature is limited to minimize temperature stratification when delivering warm air through overhead diffusers. When the discharge-air temperature reaches the maximum limit, and the zone requires more heating, primary airflow is increased, while the discharge-air temperature set point remains at the maximum limit. The result is that the damper and hot-water valve will modulate open simultaneously. By actively controlling the discharge-air temperature, you have more options for reducing with temperature stratification and short circuiting of supply to return.





Benefits of traditional VAV reheat sequence• Pre-engineered control sequences• Doesn’t require a discharge air temperature sensor

Benefits of alternative VAV reheat sequence• Uses a lower discharge air temperature for less

temperature stratificationEnergy used by these strategies could be comparable• Using a single minimum setting on the box for both

cooling and heating leads to more reheat• Increases fan energy at over 30% airflow, decreases

fan energy between 20 and 30% airflow

[SUSANNA] Here’s a summary of the two control strategies. [SLIDE][CLICK] The VAV reheat sequence we’ve traditionally used has pre-engineered control sequences and doesn’t require a discharge air temperature sensor. [CLICK]The alternative sequence requires a discharge air temperature sensor, and the temperature delivered will be lower, due to the increase in airflow at the peak heating design condition. [SUSANNA] Which one uses more energy? I guess it depends on how low you are able to let the cooling minimum airflow get. Nothing in 90.1 prevents you from going lower and reheating the cooling airflow less. [SLIDE][CLICK] If you’re using a single minimum setting on the box that’s set up for heating design, then I’d say the new sequence will use more energy. [MATT] We’re planning a program on high performance VAV for 2011, so we’ll use that forum to go over more of the tradeoffs between these two options. Now I will turn it over to Mike Patterson who will discuss changes to Appendix G.

Slide 103


Modeling




Appendix G Overview

Changes that clarify existing requirementsChanges specific to laboratory applicationsNew baseline system types

[MIKE] Thanks Matt. We will now turn our attention to updates made to Appendix G of the standard. Many of the changes made also affect Section 11, the Energy Cost Budget method; however, we will focus on appendix G changes as these primarily affect national programs such as LEED. You will find significant changes have occurred. Unfortunately, we do not have time to address all the changes. Instead, we will focus on some of the more impactful changes and discuss them here. To begin, appendix G is now a normative section and no longer permissive. What does this mean? This particular change does not have much impact on your normal day-to-day dealings with the standard. It simply incorporates appendix G fully into the standard making it subject to the same rigorous public review process the rest of the standard undergoes. As for the other changes, we can group them into three categories: [SLIDE] [CLICK] Changes that clarify existing requirements [CLICK] Changes specific to laboratory applications And [CLICK] New baseline system types

Slide 105


2007 Ventilation Requirementswithout addenda

G3.1.2.5 Ventilation.

Minimum outdoor air ventilation rates shall be the same for the proposed and baseline building designs.Exception: When modeling demand-control ventilation in the proposed design when it is use is not required by Section 6.4.3.8.

[MIKE] Let’s begin by looking at those changes that clarify existing requirements. For those already familiar with 90.1, we will compare associated 2007 requirements with those for 2010. By doing so, the change will be better illustrated. For those unfamiliar with the 2007 standard, it will serve as a means for understanding the impact of and intent behind the change. Let’s first look at how to model baseline building ventilation rates compared to the proposed building model. [SLIDE] At first glance, the 2007 requirement appears straight forward. However, some confusion arose as to what the term rate really referred to. Did it refer to the volumetric rate of air…cfm? Or, did they mean cfm/per person? Well, ASHRAE cleared up the issue with an official interpretation back in June of 2008. Simply put, ASHRAE wanted the total ventilation cfm for the proposed building to match the baseline building.




appendix GVentilation RequirementsG3.1.2.5 Ventilation.

Exceptions:b. When designing systems in accordance with Standard 62.1 Section 6.2 Ventilation Rate Procedure, reduced ventilation airflow rates may be calculated for each HVAC zone in the proposed design with a zone air distribution effectiveness (Ez) > 1.0 as defined by Table 6-2 in Standard 62.1.

Baseline ventilation airflow rates in those zones shall be calculated using the proposed design Ventilation Rate Procedure calculation with the following change only. Zone air distribution effectiveness shall be changed to (Ez)=1.0 in each zone having a zone air distribution effectiveness (Ez)>1.0.

Proposed design and baseline design Ventilation Rate Procedure calculations, as described in Standard 62.1, shall be submitted to the rating authority to claim credit for this exception.

Addendum da

[SLIDE] In 2010, things change. Like 2007, the basic requirement remains the same; however, two additional exceptions have been added…B and C…A stays the same. So, let’s look at Exception B first. In short, it changes how we define ventilation when using ASHRAE 62.1. Simply put, if designing per 62.1, use the same ventilation rates…cfm/person and cfm/square foot…in your baseline as you do in your proposed. With this exception, the total ventilation cfm for the proposed does not have to match the total ventilation cfm of the baseline. The other noteworthy item from this exception deals with zone air distribution effectiveness values. [MIKE] For those who do not know, the zone air distribution effectiveness value describes how effectively ventilation air is distributed throughout a space. Low effectiveness values mean you will have to bring in more ventilation to get the same effect. Therefore, you want a high effectiveness value. [MIKE] The highest defined by 62.1 are for systems that have a floor supply and ceiling return with low-velocity displacement ventilation. These systems have an effectiveness value of 1.2. So, knowing this, we can now make better sense of this exception. Basically, this exception states that you may use an effectiveness value greater than one in your proposed, but your baseline will never use an effectiveness value greater than 1.0. What does this mean? A proposed system with an effectiveness greater than 1.0 will bring in less ventilation air than your baseline because it can more effectively use the air it brings into the system.

Slide 107


appendix GVentilation Requirements

G3.1.2.5 Ventilation (continued).

Exceptions (continued):c. If the minimum outdoor air intake flow in the proposed design is

provided in excess of the amount required by the rating authority or building official then the baseline building design shall be modeled to reflect the greater of that required by the rating authority or building official and will be less than the proposed design.

Addendum da

[MIKE] Now, let’s shift our attention to Exception C. This exception clarifies an often asked question regarding increasing proposed building ventilation beyond what is required by the standard. For example, USGBC’s LEED Indoor Environmental Quality credit 2 provides one point if the proposed building’s design ventilation is increased 30%. Based on the 2007 version, there was no energy “penalty” for increasing the proposed airflow by 30% since both the proposed and baseline total building ventilation cfm had to be the same. [SLIDE] In 2010, the proposed design ventilation includes the increase; however, the baseline design does not. So, in this case, the proposed design ventilation will have a greater ventilation requirement than the baseline.




appendix GVentilation Requirements

IEQ Credit 2, Case 1 RequirementASHRAE 62.1 – 2007 - Proposed• People based

5 cfm/person * 1.3 = 6.5 cfm/person• Area based

0.06 cfm/ft2 * 1.3 = 0.078 cfm/ft2

ASHRAE 62.1 – 2007 - Baseline• People based – 5 cfm/person• Area based – 0.06 cfm/ft2

Addendum da

[SLIDE] Let’s look at an example. Using IEQ credit 2 from LEED for New Construction version 3 and focusing on Case 1 from the credit…which deals with mechanically ventilated spaces…The ASHRAE Standard 62.1-2007 ventilation rates for an office space are shown. Per the 2010 requirement, we increase the proposed ventilation by 30%. This is done by simply multiplying the requirement by 1.3. As for the baseline design, we simply mirror the ASHRAE 62 values. We would then model the proposed using the increased values and the baseline using the ASHRAE 62 values without the 30% increase. The result of this change…the proposed design will condition more ventilation air than the baseline design. This additional energy use can be overcome in any number of ways.

Slide 109


appendix GPurchased Chilled Water/HeatG3.1.1.3.2 Purchased Chilled Water Only.

System 1 & 2 shall be constant volume fan coils with fossil fuel boilersSystem 3 & 4 shall be constant volume single zone air handlers with fossil fuel furnace(s)System 7 shall be used in place of System 5System 8 shall be used in place of System 6

G3.1.1.3.3 Purchased Chilled Water and Purchased Heat.System 1 shall be constant volume fan coil unitsSystem 3 shall be constant volume single zone air handlersSystem 7 shall be used in place of System 5

G3.1.1.3.4 On-site Distribution Pumps.“All on-site distribution pumps shall be modeled in both the baseline and proposed designs.”

Addendum ai

[MIKE] The next issue clarified in the 2010 standard deals with purchased heat and purchased chilled water. The use of purchased heat is covered in the 2007 standard; however, purchased chilled water is not. Furthermore, the Baseline System Descriptions table, Table G3.1.1B, did not mention either. 2010 expands on purchased heat and addresses purchased chilled water. As would be expected, if you utilize purchased heat or chilled water in the proposed building, then you will also use it in your baseline building model. The change also updates the Baseline System Descriptions table adding these terms; plus, system specifications are defined for each. [SLIDE] This slide shows what system types are used in the baseline building model when purchased chilled water is being used and when both purchased chilled water and heating are used. You will notice fan coils are substituted for the packaged units normally defined by systems 1 and 2. The last change dealing with this topic is straight-forward… Simply, model all on-site distribution pumps in both the proposed and baseline designs.




appendix GUnmet Load Hours Requirement

Temperature control throttling range:

The number of degrees that room temperature must change in order to go from full heating to no heating or from full cooling to no cooling.

Addendum cr

[MIKE] Our last clarification deals with unmet hours. This is perhaps one of the most significant clarifications in the new standard. Please note…the associated changes made to the Energy Cost Budget Method slightly differ from those discussed here pertaining to appendix G. If you are employing the ECB Method, please review those changes. To begin, let’s take a look at a new term defined by the 2010 standard. [SLIDE] Temperature control throttling range may be a straight forward and seemingly obvious term, but it is a critical component to the revised unmet hour definition and helps clarify the unmet hour concept. It is, “the number of degrees that room temperature must change in order to go from full heating to no heating or from full cooling to no cooling.” Let’s now take a look at the revised unmet hour definition…

Slide 111



2007 Unmet load hours definition:An hour in which one or more zones is outside of the thermostat setpoint range.

2010 Unmet load hours definition:An hour in which one or more zones is outside of the thermostat setpoint plus or minus one half of the temperature control throttling range. Any hour with one or more zones with an unmet cooling load or unmet heating load is defined as an unmet load hour.

Addendum cr

[SLIDE] For the benefit of those not familiar with the 2007 definition, it is included here along with the updated 2010 definition. The obvious change is the 2010 definition is much longer. But, the true change is in the clarification made by the additional verbiage. Both definitions start out the same and begin to differ after mentioning the thermostat setpoint range. In the past, we were left wondering what the thermostat setpoint range was. Now, we know it to be “plus or minus one half of the temperature control throttling range.” Here’s an example…

Slide 112



Throttling range: 2° F

½ Throttling range: 1° F

Setpoint: 75° F

Thermostat Setpoint Range: 74° - 76° F

Addendum cr

[SLIDE] To begin, let’s assume a throttling range of 2°. The throttling range will vary based on the energy modeling software you use. Some programs allow you to define the throttling range; whereas, others do not. [CLICK] Once the throttling range is known, we can easily determine half the value. [CLICK] Assuming a setpoint of 75°, we apply ½ the throttling range to either side of our setpoint. [CLICK] Therefore, if the space is in cooling mode and the temperature is higher than 76° by the end of the hour, then an unmet hour for that space will be generated. [MIKE] Further changes to appendix G clarify that the temperature control throttling range shall be the same in both the proposed and baseline buildings. Additionally, neither the proposed nor baseline may have more than 300 unmet hours. The requirement for the proposed building’s unmet hours not to exceed the baseline total by more than 50 hours has been removed.




appendix GLaboratory Requirements

G3.1.3.13 VAV Minimum Flow Setpoints (Systems 5 and 7).

Exception: Systems serving laboratory spaces shall reduce the exhaust and makeup air volume during unoccupied periods to the largest of 50% of zone peak air flow, the minimum outdoor air flow rate, of the air flow rate required to comply with applicable codes or accreditation standards.

Addendum ch

[MIKE] That is it for the major clarification changes. Before we shift all our attention to laboratories, there is a change worth highlighting regarding the minimum volume setpoint of VAV reheat boxes. In the past, the minimum flow setpoint was defined as 0.4 cfm/square foot. 2010 changes this to 30% of zone peak airflow. With that said, we can now focus on laboratories. The first change deals with what system to use in the baseline building when dealing with a building incorporating laboratory spaces exhausting greater than 5000 cfm. If such a space exists, you will apply System 5, packaged VAV with reheat, or System 7, VAV with reheat. If the building is all electric heat, electric resistance will be used for heating in conjunction with the specified cooling system. Susanna did not have time to cover this, but it is worth noting that this change was made to mirror a change made in the mechanical prescriptive path. The next change deals with an exception to the VAV Minimum Flow Setpoint requirement I mentioned a moment ago. [SLIDE] This exception details how laboratory spaces define their VAV minimum flow setpoints. Specifically, setpoint determination is based on unoccupied periods and reducing exhaust and makeup air volume to the larger of… 50% of peak zone airflow, Minimum outdoor air flow rate, or The air flow rate required by applicable code or accreditation standard.




appendix GLaboratory Requirements

G3.1.2.8 Design Air Flow Rates.

Exception: For systems serving laboratory spaces, use a supply-air-to-room-air temperature difference of 17 deg F or the required ventilation air or makeup air, whichever is greater.

Addendum db

[SLIDE] Staying on the topic of laboratories, an exception for laboratory spaces has been added to the design air flow rate requirement. Laboratory spaces now must use a supply-air-to-room-air temperature difference of 17 degrees…instead of the normally required 20 degree difference. These changes address some of the unique characteristics of laboratory spaces making the baseline building model a better comparison than in previous versions.

Slide 115


appendix GNew Systems

G3.1.1 Baseline HVAC System Type and Description.

Exceptions:e. Thermal zones designed with heating only systems in

the proposed design, serving storage rooms, stairwells, vestibules, electrical/mechanical rooms, and restrooms not exhausting or transferring air from mechanically cooled thermal zones in the proposed design shall use System type 10 or 11 in the baseline building design.

Addendum dn

[MIKE] The final change we will take a look at today deals with two new system types. Those in the energy modeling community that have modeled per appendix G in the past are familiar with the requirement to model both mechanical cooling and heating for conditioned spaces regardless if the actual space will include mechanical cooling or not. The 2010 version of the standard addresses this issue and added two baseline systems: System 10, Heating and Ventilation utilizing electric or other heat, and System 11, Heating and Ventilation utilizing fossil fuel, hybrid, or purchased heating sources. [SLIDE] In order to qualify for one of these systems, the proposed design thermal zone must serve one of the space types listed in exception E…storage rooms, stairwells, vestibules, electrical/mechanical rooms or restrooms. Additionally, these spaces may not exhaust or transfer air from mechanically cooled thermal zones. Therefore, if a proposed design thermal zone complies with one of the space types you see here, you may apply one of the new system types to the associated thermal zone in the baseline.




appendix GNew SystemsG3.1.2.6 Economizers.Outdoor air economizers shall not be included in baseline HVAC Systems 1, 2, 10, and 11…

G3.1.2.8.2 Baseline System Types 10 and 11.System design supply airflow rates for the baseline building design shall be based on the temperature difference between a supply air temperature setpoint of 105° F and the design space heating temperature setpoint, the minimum outdoor air flow rate, or the airflow rate required to comply with applicable codes or accreditation standards, whichever is greater.

Addendum dn

[SLIDE] Along with these new system types, you will find several supporting requirements. First, economizer controls will not be used in conjunction with these system types. This makes sense when you consider these are heating and ventilation only systems. Two, system design airflow rates are set based on the greatest of the following three criteria…design space heating temperature setpoint, the minimum outdoor air flow rate, or the airflow rate required to comply with applicable code or accreditation standard.

Slide 117


appendix GNew Systems

G3.1.2.9 System Fan Power.

For Systems 10 and 11 (supply fan),Pfan = CFMs * 0.3

For Systems 10 and 11 (non-mechanical cooling fan if required by Section G3.1.2.8.2),

Pfan = CFMnmc * 0.054

Addendum cr

[SLIDE] The final requirement associated with the new system types deals with the system fan power equation. Before detailing this requirement, it is imperative we understand these systems do not deal with mechanical cooling. They are heating and ventilation systems only. Therefore, if the proposed design system has mechanical cooling, then these systems can not be used as the associated baseline system. So, when we consider fan energy for these systems, the proposed system may or may not have a fan associated with it. If it does not have an associated fan, then a fan will not be modeled for either the proposed design or the baseline design. However, if the proposed design system has a fan associated with it…for example, a ventilation or heating fan, then the system fan power rules shown here apply. [MIKE] While on the subject of fan energy, let’s review the general rule regarding what fans are considered in the appendix G system fan power calculation. When using the appendix G system fan power equation, only the supply, return, exhaust, and relief fans are considered. Any fan powered VAV boxes are not included in the calculations.




appendix GBaseline Design Comparison

General Parameters• 75,600 ft2

• Office building• Columbus, Ohio• Rooftop VAV

Proposed Design• High efficiency equipment• Daylighting• Enthalpy economizer• Improved Supply Air Temperature Reset

[MIKE] That concludes the major changes found in the 2010 version of Appendix G. As mentioned at the beginning, these are only some of the more impactful changes, but there are many others. Please take the time to review Appendix G prior to your first analysis using the 2010 standard. In an effort to illustrate the impact these changes will have, let’s take a look at how these changes may affect future energy models. Using TRACE 700, an analysis was conducted comparing the 2010 standard and the 2007 standard against a proposed building design. As many of you are aware, a complete building energy analysis consists of many variables and is highly dependent on geographical location. The values presented here are offered as a means to illustrate the impact of the changes made by the 2010 standard and not necessarily provide definitive results for your projects. In a few minutes, Mick will address a formal analysis being conducted by Pacific Northwest National Laboratories. [SLIDE] This slide highlights some of the basic assumptions made regarding the baseline building. An office building at just over 75,000 square feet located in Columbus, Ohio was considered. The building is cooled utilizing a rooftop VAV system and heated with electric heat. One alternative was modeled following the Appendix G requirements from the 2007 standard and another alternative was modeled following the 2010 requirements. Finally, the proposed design was modeled the same with some exceptions. The proposed design incorporated several energy conservation measures such as high efficiency equipment, daylighting, enthalpy economizer and supply air temperature reset with a 10° reset instead of the Appendix G required 5° used with the baseline systems. Supply air temperature reset was one of the control strategies Matt spoke about earlier. So, let’s look at some results.

Slide 119


baseline design comparisonResults

$54,954

$60,453

$75,5132007 Baseline

2010 Baseline

Proposed Design

$0 $10,000 $20,000 $30,000 $40,000 $50,000 $60,000 $70,000 $80,000

Energy Cost

1

2

3

Alte

rnat

ive

ASHRAE Standard 90.1 Appendix G Analysis

[SLIDE] What you see here is the total building energy cost for each alternative modeled. The average retail price for electricity in Ohio was used to determine energy costs for the analysis. Only electrical consumption was considered, not demand. Let’s briefly review each alternatives results… [CLICK] Considering cooling, heating, fan, and lighting/receptacle energy, the 2007 baseline design energy costs just over $75,000. [CLICK] The 2010 baseline costs just over $60,000 and [CLICK] the proposed design cost just under $55,000. Now, let’s look at how they compare




2007 Baseline

2010 Baseline

Proposed Design

$0 $10,000 $20,000 $30,000 $40,000 $50,000 $60,000 $70,000 $80,000

Energy Cost

1

2

3

Alte

rnat

ive


baseline design comparison Results

27%

[SLIDE] When we compare the 2007 results to our proposed building… [CLICK] We find the proposed building saved 27% in terms of energy costs.

Slide 121


2007 Baseline

2010 Baseline

Proposed Design

$0 $10,000 $20,000 $30,000 $40,000 $50,000 $60,000 $70,000 $80,000

Energy Cost

1

2

3

Alte

rnat

ive


Comparison Results

9%

9%

[SLIDE] Now, looking at how the proposed compares to the 2010 alternative. [CLICK] Our savings shrink to 9%. What happened to our savings? In short, the net effect of the changes made in 2010 make it more difficult to achieve energy savings. The good news. We achieved 9% savings from only 4 areas: High Efficiency equipment Implementation of daylighting controls Using an enthalpy economizer compared to the baselines’ dry bulb economizer And improved supply air temperature reset controls as compared to the baseline. Other areas to consider that were not included here for simplicity are… Envelope improvements…this analysis used the same envelope parameter for all alternatives Lighting design improvements…with the exception of daylighting, the lighting power densities were the same across alternatives Other airside/waterside strategies such as heat recovery and systems with higher ventilation effectiveness should also be considered [MIKE] So, what does this all mean? Finding energy savings when compared to the new 2010 standard will prove more difficult than we saw with the 2007 standard; however, energy savings still exist. As ASHRAE President Lynn Bellenger mentioned in her presidential address, an integrated design approach will be critical towards the optimization of future building design.




Summary

Slide 123


Publication and Final Savings Estimates

Performed by Pacific Northwest National Laboratory (PNNL)• Savings shared are modeled as of June 28, 2010• Addenda approved by the ASHRAE and IES Boards of

Directors will be added to the models• Final PNNL savings estimates planned for

November 2010

[MICK] So, those are a lot of changes. How did the committee do reaching its WorkPlan goal? Modeling has been done by Pacific Northwest National Laboratories and the results were shared in a seminar delivered at the annual ASHRAE meetings in June. Since the June meetings additional addenda have been approved, and PNNL hopes to have the final savings estimates modeling by about November of this year. We’ll share both energy and energy cost saving estimates.

Slide 124


90.1 Progress Indicator

Including receptacle loads in modelingIncluding receptacle load in % savings calculation

23.4

Energy cost savings %

24.8Ventilation rate changes

between 62.1-1999 and 62.1-2007

Energy savings %

In addition to the changes in 90.1, there were ventilation rate changes in ASHRAE Standard 62.1. These are included in the modeling. [SLIDE] From a whole building perspective, including receptacle loads (for example copiers, vending machines, etc.) The energy cost savings is over 23% and the energy savings is almost 25%. [MICK] Recall that earlier we shared the change in the Title, Purpose, and Scope (the TPS) made by Addendum AQ. Until this TPS change, the committee could not address loads from receptacles or processes. So another calculation was made.




90.1 Progress IndicatorExcluding receptacle loads in % savings calculation only

Including receptacle loads in modelingExcluding receptacle load in % savings calculation

28.9

Energy cost savings %

30.9Ventilation rate changes

between 62.1-1999 and 62.1-2007

Energy savings %

If we keep the receptacle thermal loads in the model, but exclude their electrical consumption from the percentage calculation,[SLIDE] the savings estimates rise to almost 29% for cost and 31% for energy!

Slide 126


90.1 Progress Indicator as of 28 June 2010

Additional addenda to be includedF – Cool Roofs S – DX efficiencyCK – ventilation resetCT, DD – DaylightingBF – Continuous air barrierothers

Final savings expected to be higherMany thanks to PNNL

In addition, there are a significant number of addenda that have yet to be modeled, so the final saving estimates are expected to be even greater. We thank PNNL for their work, and congratulate all who worked on 90.1-2010. [MICK] When I rolled of my position as committee chair in June, I reflected on the many people who helped developed 90.1-2010

Slide 127


Thanks to…Mark HydemanSteve SkalkoJerine AhmedSusan IsenhourAndersonWagdy AnisPete BaseliciJeff BoldtDave BransonKeith EmersonDrake ErbeJim GarrigusJason GlazerPekka HakkarainenRichard HeinischNed HemingerJohn HoganHy KaplanMichael LaneDick LordRon MajetteItzhak MaorJim McClendonMichael MehlHarry MisurielloFrank MorrisonTim PeglowEric RichmanMaria SpinuChristian TaberMike TillouMartha VanGeem

Tom CulpDarryl DeAngelisJohn DunlapKrishnan GowriMark HalvorsonDavid HandworkScott HintzTianzhen HongRon JarnaginMichael JouanehLarry KoumaBing LiuFrank MyersJeff ParkRobert RossCedric TruemanEmily YoungRandy CasteelPat ChinodaPaul LindahlKen LutherRick PavlakLeon ShapiroJim WattsRita HarroldDoug ReindlJohn Montgomery David SchaafDennis SczomakDavid WeitzRobin Wilson

Ken BrendanLawrence BrownJohn LewisBill HolyFrank JakobMichael WoodfordTony ArboreTodd BrownLeo SmithDennis StankeOur employersPublic

CommentersNMHCGANAPresenters at meetingsCMP proposersInterpretation requesters

PNNL Staff (analysis)Brian ThorntonDr. Weimin WangDr. Yulong XieDr. Heejin ChoDr. Jian ZhangYunzhi HuangRahul AthalyeVrushali Mendon

All our families

ASHRAE/IESCassandra CraigBeverly FulksSteve HammerlingBruce HunnSusan LeBlancJeff LittletonJudy MarshallCindy MichaelsAngela McFarlinMark OwenElizabeth ParrishLilas PrattClaire RamspeckStephanie ReinicheAmelia SandersEmily ScottEmily SigmanMatt WalkerMark WeberJan YoungSPLSCarol MarriottStandards CommitteeSteve BushbyTechnology CouncilTom WatsonBoards of DirectorsKent PetersonBill HarrisonGordon HolnessLynn Bellenger

Mike WaiteMack WallaceRichard WatsonJerry WhiteRon BurtonCharles CottrellCraig DrumhellerAllan FraserRon KurtzSteve RosenstockFrank StanonikKarim AmraneErnie ConradChuck FosterChad GroshartMerle McBrideKen SaganRandy BlanchetteDon BrundageBrian HahnlenSusanna HansonJonathan HumbleRay McGowanMike RosenbergMarty SalzbergJeff SteinWayne StoppelmoorBill TalbertDan WalkerJim BowmanJim Calm

Steve Ferguson,ASHRAE Staff Liaison aka “Radar”

They include Project Committee voting members [CLICK] Subcommittee voting members and Consultants [CLICK] Liaisons and Past SSPC members [CLICK] Technical Committees and the ASHRAE Standards Committee, Technology Council and IES and ASHRAE Boards [CLICK] Public review commenters, people who proposed addenda and industry groups – an important part of the open, consensus process. Our cosponsoring organization IES ASHRAE staff. One group that is often forgotten is our families who sacrifice so that we were able to perform the work of the society. We don’t expect you to be able to read the names, but the purpose is to show that 90.1-2010 is the result of literally hundreds of people’s work, for thousands and thousands of hours. [CLICK] There is one, single person who has done an amazing amount of work – the ASHRAE staff Liaison to SSPC 90.1. We call him “Radar” – many refer to him as Steve Ferguson. Thanks to all for their work on this, and to you for taking the time to stay up-to-date with the changes that reduce the energy



consumption and cost of buildings. Jeanne?

Slide 128


summaryASHRAE/IESNA Standard 90.1-2010

[Jeanne] Well, that brings us to end of the today's presentation. Today we’ve provided you with a long list of changes to Standard 90.1 and some examples of approaches for you, the designer. Bottom line is that the new requirements will help drive building energy use down

Slide 129


references for this broadcastWhere to Learn More

www.trane.com/

[SLIDE] There is an Engineers Newsletter that supplements today’s program and a bibliography with additional resources is available - ask for copies from you local site coordinator.




watch past broadcastswww.trane.com/enl

Insightful topics on HVAC system design:• Chilled-water plants• Air distribution• Refrigerant-to-air systems• Control strategies• Industry standards and

LEED• Energy and the environment• Acoustics• Ventilation• Dehumidification

www.trane.com/ENL

[SLIDE] Additionally, past broadcasts are available to order on trane.com - check out the website for information on specific broadcasts.

Slide 131


Earn an average of 1.5 learning unitsNew courses added monthlyTopics include:• Central Geothermal

Systems• ASHRAE Standards• Ice Storage• Industry standards and

LEED• Energy and the

environment

Continuing Education

www.trane.com/ContinuingEducation

Or visit trane.com/continuing education for on-demand programs accredited for LEED continuing education and AIA CES learning units. [JEANNE] Please remember to fill out a survey and let us know how we're doing. AIA members, please remember to turn in your member information to your local site coordinator.

Slide 132


MarchUpgrading Chilled-Water Systems

JuneHigh Performance VAV Systems

OctoberDedicated Outdoor Air Units

2011

[SLIDE] We are excited to announce our 2011 Engineers Newsletters Live program line up. In Spring we’ll be back to discuss upgrades and improvements to chilled-water systems to increase efficiency and better serve building occupants. In June we’ll discuss design and control strategies that can significantly reduce energy use and ensure proper ventilation in VAV systems and, in fall, we’ll cover various types of equipment used for dedicated OA conditioning [JEANNE] So mark your calendars! Thanks for joining us today – Have a fabulous holiday season we’ll see you in Spring!



ANSI/ASHRAE/IESNA Standard 90.1-2010,Energy Standard for Buildings Except Low-Rise Residential Buildings



October 2010 ASHRAE 90.1-2010

Mick Schwedler, | manager, applications engineering | Trane

Mick has been involved in the development, training, and support of mechanical systems for Trane since 1982. With expertise in system optimization and control (in which he holds patents), and in chilled-water system design, Mick’s primary responsibility is to help designers properly apply Trane products and systems. To do so, he provides one-on-one support, writes technical publications, and presents seminars.

A recipient of ASHRAE’s Distinguished Service Award, Mick is the immediate past Chair of SSPC 90.1, which was responsible for writing ANSI/ASHRAE/IESNA 90.1-2007, a prerequisite for LEED. He also contributed to the ASHRAE GreenGuide and is a former member of the LEED Energy and Atmospheric Technical Advisory Group (TAG). Mick earned his mechanical engineering degree from Northwestern University and holds a master’s degree from the University of Wisconsin Solar Energy Laboratory. He also is a registered professional engineer in the State of Wisconsin. Susanna Hanson | applications engineer | Trane

Susanna is an applications engineer at Trane with over twelve years of experience with chilled-water systems and HVAC building load and energy analysis. Her primary responsibility is to aid system design engineers and Trane personnel in the proper design and application of HVAC systems. Her main areas of expertise include chilled-water systems and ASHRAE Standard 90.1. She is also a Certified Energy Manager. She has authored several articles on chilled water plant design, and is a member of ASHRAE SSPC 90.1 Energy Standard for Buildings Except Low-Rise Residential Buildings. Susanna earned a bachelor’s degree in industrial and systems engineering from the University of Florida, where she focused on building energy management and simulation. Mike Patterson | sales training manager | Trane

Mike joined Trane as a Marketing Engineer with Customer Direct Service (C.D.S.), the group responsible for the development of and training for HVAC design and analysis software. As a CDS engineer he developed expertise in the areas of energy modeling and ASHRAE Standard 90.1. Mike was specifically responsible for the development and continuity of the TRACE 700 training programs including modules on ASHRAE Standard 90.1 & LEED. As an instructor, he was responsible for training customers on energy fundamentals and energy modeling programs. Currently Mike is involved with the Trane Graduate Training Program and is responsible for the development and training of sales and marketing engineers for Trane. Prior to joining Trane, Mike spent 10 years as a pilot in the United States Air Force with over 2,300 hours in the KC-135 and T-37. Mike is a LEED AP BD+C and earned his bachelor’s degree in Engineering Mechanics from the United States Air Force Academy. He also holds a Master’s in Business Administration from Regis University. Matthew Bye |product engineer | Trane

Matt is a Product engineer at Trane with over 15 years of experience in designing, managing, and implementing energy management related products and services. Currently, his primary responsibility is the design and definition of Building Automation Systems controls and software applications. He is a LEED accredited professional. He has also designed software on behalf of the Electric Power Research Institute (EPRI) that is used by electric utilities across the country to model incentives for energy efficiency programs, design demand response programs, and aid in the develop tariffs. Matt began his career implementing demand side management programs for the local electric utility and has found the study of energy from production to end use to be fascinating. One of his favorite recent projects was co-authoring a winning grant to install 600kW of solar photovoltaics on the roof of a local facility. He earned a Bachelor of Science degree in Energy Management at Minnesota State University.

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trane engineers newsletter live - ashrae standard 90.1 2010

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