water heating design, equipment and … 94 ashrae 90.1-2013 updates.pdfgreen plumbing and mechanical...

31GREEN PLUMBING AND MECHANICAL CODE SUPPLEMENT

WATER HEATING DESIGN, EQUIPMENT AND INSTALLATION

EQUIPMENT TYPE SIZE CATEGORY (INPUT)

SUBCATEGORY OR RATING CONDITION

PERFORMANCEREQUIRED1

TEST PROCEDURE2,3

Electric Table Top Water Heaters ≤12 kW Resistance≥20 gal 0.93–0.00132035V EF DOE 10 CFR

Part 430

Electric water heaters

≤12 kW Resistance≥20 gal 0.97–0.00132035V EF DOE 10 CFR

Part 430

>12 kW Resistance ≥20 gal 20 + 35√V SL, Btu/h0.3 + 27√Vm %/h

Section G.2 of ANSIZ21.10.3

≤24 Amps and≤250 Volts Heat Pump 0.93–0.00132035V EF DOE 10 CFR

Part 430

Gas storage water heaters

≤75 000 Btu/h ≥20 gal 0.627–0.00190005V EF DOE 10 CFRPart 430

>75 000 Btu/h <4000 (Btu/h)/gal 80% Et (Q/800799 +11016.6√V)SL, Btu/h

Sections G.1 andG.2 of ANSI

Z21.10.3

Gas instantaneous water heaters

>50 000 Btu/h and <200000 Btu/h

≥4000 (Btu/h)/galand <2 gal 0.62–0.00190005V EF DOE 10 CFR

Part 430

≥200 000 Btu/h4 ≥4000 (Btu/h)/galand <10 gal 80% Et Sections G.1 and

G.2 of ANSIZ21.10.3≥200 000 Btu/h ≥4000 (Btu/h)/gal

and ≥10 gal80% Et (Q/800799 +

11016.6√V) SL, Btu/h

Electronic instantaneous water heaters5

≤ 12 kW ≥ 4000 (Btu/h)/gal and < 2 gal 0.93 – (0.00132•V) EF DOE 10 CFR

Part 430

> 12 kW ≥ 4000 (Btu/h)/gal and < 2 gal 95% Et Section G.2 of ANSI

Z21.10.3

Oil storage water heaters

≤105 000 Btu/h ≥20 gal 0.59-0.00190005V EF DOE 10 CFRPart 430

>105 000 Btu/h <4000 (Btu/h)/gal 7880% Et (Q/800799 +11016.6√V) SL, Btu/h


Z21.10.3

Oil instantaneous water heaters

≤210 000 Btu/h ≥4000 (Btu/h)/galand <2 gal 0.59–0.00190005V EF DOE 10 CFR

Part 430

>210 000 Btu/h ≥4000 (Btu/h)/galand <10 gal 80% Et Sections G.1 and

G.2 of ANSIZ21.10.3>210 000 Btu/h ≥4000 (Btu/h)/gal

and ≥10 gal78% Et (Q/800799 +

11016.6√V) SL, Btu/h

Hot-water supply boilers, gas and oil ≥300 000 Btu/h and<12 500 000 Btu/h

≥4000 (Btu/h)/galand <210 gal 80% Et


Z21.10.3Hot-water supply boilers, gas ––––– ≥4000 (Btu/h)/gal

and <≥10 gal80% Et (Q/800799 +

11016.6√V) SL, Btu/h

Hot-water supply boilers, oil ––––– ≥4000 (Btu/h)/galand ≥10 gal

78% Et (Q/800799 +11016.6√V) SL, Btu/h

Pool heaters, oil and gas All ––––– 78% Et ASHRAE 146

Heat pump pool heaters All

50.0°F db44.2°F wbOutdoor air

80.0°FEntering Water

4.0 COP AHRI 1160

Unfired storage tanks All R-12.5 (none)

For SI units: 1 gallon = 3.785 L, 1000 British thermal units per hour = 0.293 kW, 1 degree Fahrenheit = t/cº = (t/ºF-32)/1.81 Energy factor (EF) and thermal efficiency (Et ) are minimum requirements, while standby loss (SL) is maximum Btu/h (W) based on a 70°F (21ºC)

temperature difference between stored water and ambient requirements. In the EF equation, V is the rated volume in gallons. In the SL equation, V is therated volume in gallons and Q is the nameplate input rate in Btu/h.

2 Section 12 of ASHRAE 90.1 contains a complete specification, including the year version, of the referenced test procedure.3 Section G1 is titled “Test Method for Measuring Thermal Efficiency” and Section G2 is titled “Test Method for Measuring Standby Loss.”4 Instantaneous water heaters with input rates below 200 000 Btu/h (58.6 kW) must comply with these requirements if the water heater is designed to heat

water to temperatures of 180°F (82ºC) or higher. 5 Not part of ASHRAE 90.1 Table 7-8.

TABLE 603.4.2PERFORMANCE REQUIREMENTS FOR WATER HEATING EQUIPMENT [ASHRAE 90.1: TABLE 7.8]

Item Number: 94 Submitter: IAPMO Staff Proposed Change: ASHRAE 90.1-2013 updates


701.0 General. 701.1 Scope. The provisions of this chapter shall establishthe means of enhancing energy efficiency associated withmechanical systems in a building.

702.0 Heating, Ventilation, and Air-ConditioningLow-Rise Residential Buildings. 702.1 General. The heating, ventilating, air-conditioning,for single-family houses, multi-family structures of threestories or fewer above grade, and modular houses shall be inaccordance with Section 702.2 through Section 702.13. Theheating, ventilation, and air-conditioning system of otherbuildings shall be in accordance with Section 703.0.702.2 Heating, Ventilating, and Air-ConditioningSystems and Equipment. This section shall regulate onlyequipment using single-phase electric power, air conditioners,and heat pumps with rated cooling capacities less than 65 000British thermal units per hour (Btu/h) (19.0 kW), warm airfurnaces with rated heating capacities less than 225 000 Btu/h(66 kW), boilers less than 300 000 Btu/h (88 kW) input, andheating-only heat pumps with rated heating capacities less than65 000 Btu/h (19.0 kW). [ASHRAE 90.2:6.2]

702.2.1 Non-Residential Type Systems andEquipment. Heating, ventilating, and air-conditioningsystems and equipment that does not fall under therequirements in Section 702.0 shall be in accordancewith the applicable requirements of Section 703.0.

702.3 Balancing. The air distribution system design,including outlet grilles, shall provide a means for balancingthe air distribution system unless the design procedureprovides a system intended to operate within ± 10 percent ofdesign air quantities. [ASHRAE 90.2:6.3]

702.3.1 Balancing Dampers. Balancing dampersshall be installed in all branch ducts and the axis of thedamper must be installed parallel to the direction ofairflow in the main duct.

702.4 Ducts. Ducts shall be sized, installed, and tested inaccordance with Section 702.4.1 through Section 702.4.4.

702.4.1 Insulation for Ducts. Portions of the air distri-bution system installed in or on buildings for heating andcooling shall be R-8. When the mean outdoor dew-pointtemperature in any month exceeds 60°F (16°C), vaporretarders shall be installed on conditioned-air supply ducts.Vapor retarders shall have a water vapor permeance notexceeding 0.5 perm [0.0000000000286 kg/(Pa•s•m2)] whentested in accordance with Procedure A in ASTM E96.

Insulation is not required when the ducts are withinthe conditioned space. [ASHRAE 90.2:6.4]702.4.2 Ducts and Register Penetrations. Joints,seams, and penetrations of duct systems shall be madeairtight by means of mastics, gasketing, or other meansin accordance with the mechanical code. Register pene-

trations shall be sealed to the wall or floor assemblies.Where HVAC duct penetrates a conditioned space, theduct penetration shall be sealed to the wall or floorassembly to prevent leakage into an unconditioned space. 702.4.3 Duct Leakage Test. For systems with anyduct or air handler outside of the conditioned space, aduct leakage test shall be performed in accordance withSection 702.4.3.1.

702.4.3.1 Duct Leakage Verification Test.Ductwork shall be tested to the maximum permittedleakage in 1 cubic foot per minute (ft3/min)/100square feet (ft2) (0.05 L/s/m2) of duct surface areain accordance with the SMACNA Air Duct LeakageTest Manual. All register penetrations shall besealed during the test. The test shall be conductedwith a pressure differential of 0.1 inch water gauge(0.024 kPa) across the tested system.

702.4.4 Duct Sizing. Duct systems shall be sized inaccordance with ACCA Manual D or other methodsapproved by the Authority Having Jurisdiction with thevelocity in the main duct not to exceed 1000 feet perminute (ft/min) (5 m/s) and the velocity in the secondarybranch duct not to exceed 600 ft/min (3.05 m/s).

702.5 Insulation for Piping. HVAC system piping installedto serve buildings and within buildings shall be thermally insu-lated in accordance with Table 702.5. [ASHRAE 90.2:6.5]702.6 Ventilation and Combustion Air.

702.6.1 Ventilation Air. The building shall bedesigned to have the capability to provide the ventilationair specified in Table 702.6.1. Mechanical ventilationshall be calculated in accordance with Equation 702.6.1.[ASHRAE 90.2:6.6.1]

Mechanical (Equation 702.6.1)Ventilation = [(0.35 – Summer) × Volume] / 60

Where:Mechanical Ventilation = required mechanical ventilation rate to

supplement summer infiltration, cfmSummer = summer design infiltration rate, achVolume = volume of conditioned space, ft3

702.6.2 Combustion Air. Combustion air for fossilfuel heating equipment shall be in accordance with thelocally adopted code or with one of the following:natural gas and propane heating equipment, NFPA 54;oil heating equipment, NFPA 31; or solid fuel burningequipment, NFPA 211. [ASHRAE 90.2:6.6.2]

702.7 Electric Heating Systems. Electric heatingsystems shall be installed in accordance with the followingrequirements. [ASHRAE 90.2:6.7]

CHAPTER 7HEATING, VENTILATION AND AIR-CONDITIONING SYSTEMS

AND EQUIPMENT - ENERGY EFFICIENCY


36 GREEN PLUMBING AND MECHANICAL CODE SUPPLEMENT

HEATING, VENTILATION AND AIR-CONDITIONINGSYSTEMS AND EQUIPMENT – ENERGY EFFICIENCY

702.7.1 Wall, Floor, or Ceiling Electric-Resis-tance Heating. Where wall, floor, or ceiling electric-resistance heating units are used, the structure shall bezoned and heaters installed in each zone in accordancewith the heat loss of that zone. Where living and sleeping

zones are separate, the number of zones shall not be lessthan two. If two or more heaters are installed in any oneroom, they shall be controlled by one thermostat.[ASHRAE 90.2:6.7.1]702.7.2 Electric Central Warm Air Heating. Whenelectric central warm air heating is to be installed, an elec-tric heat pump or an off-peak electric heating system withthermal storage shall be used. [ASHRAE 90.2:6.7.2]Exceptions:(1) Electric resistance furnaces where the ducts are

located inside the conditioned space, and not lessthan two zones are provided where the living andsleeping zones are separate.

(2) Packaged air-conditioning units with supplementalelectric heat.

702.8 Bath Ceiling Units. Bath ceiling units providing anycombination of heat, light, or ventilation shall be providedwith controls permitting separate operation of the heatingfunction. [ASHRAE 90.2:6.8]702.9 HVAC Equipment, Rated Combinations. HVACsystem equipment and system components shall be furnishedwith the input(s), the output(s), and the value of the appro-

For SI Units: t/ºC= (t/ºF-32)/1.8, 1 British thermal unit = 1055 J, 1 inch = 25 mm1 For insulation outside the stated conductivity range, the minimum thickness (T) shall be determined as follows:

T = r{(1 + t/r)K/k – 1}Where:T = minimum insulation thickness (inches).r = actual outside radius of pipe (inches).t = insulation thickness listed in this table for applicable fluid temperature and pipe size.K = conductivity of alternate material at mean rating temperature indicated for the applicable fluid temperature [Btu∙inch/(h∙ft2∙ºF)]k = the upper value of the conductivity range listed in this table for the applicable fluid temperature.

2 These thicknesses are based on energy efficiency considerations only. Additional insulation is sometimes required relative to safety issues/surface tempera-ture.

3 Piping insulation is not required between the control valve and coil on run-outs when the control valve is located within 4 feet (1219 mm) of the coil and thepipe size is 1 inch (25 mm) or less.

4 These thicknesses are based on energy efficiency considerations only. Issues such as water vapor permeability or surface condensation sometimes require vaporretarders, additional insulation or both.

5 For piping exposed to outdoor air, increase insulation thickness by 1⁄2 inch (12.7 mm). The outdoor air is defined as any portion of insulation that is exposedto outdoor air. For example, attic spaces and crawlspaces are considered exposed to outdoor air.

INSULATION CONDUCTIVITY NOMINAL PIPE DIAMETER (inches)

FLUID DESIGN OPERATINGTEMPERATURE RANGE

(°F)Btu•inch/(h•ft2•°F)

MEAN RATINGTEMPERATURE

(°F)<1 1 TO 1-1⁄4 1-1⁄2 TO 3-1/2 4 TO 6

EQUAL TO OR

GREATERTHAN 8

HEATING SYSTEMS (STEAM, STEAM CONDENSATE, AND HOT WATER)2, 3

201–250 0.27–0.30 150 1.5 1.5 2.0 2.0 2.0141–200 0.25–0.29 125 1.0 1.0 1.0 1.5 1.5105–140 0.22–0.28 100 0.5 0.5 1.0 1.0 1.0

COOLING SYSTEMS (CHILLED WATER, BRINE, AND REFRIGERANT)4

40–55 0.22–0.28 100 0.5 0.5 1.0 1.0 1.0Below 40 0.22–0.28 100 0.5 1.0 1.0 1.0 1.5

TABLE 702.5MINIMUM PIPE INSULATION THICKNESS1, 5

[ASHRAE 90.2: TABLE 6.5]

For SI units: 1 cubic foot per minute = 0.00047 m3/s.1 Calculate in accordance with Equation 702.6.1.2 Reference standards:

(A) ACCA Manual J(B) ASHRAE GRP-158

TABLE 702.6.1 VENTILATION AIR

[ASHRAE 90.2: TABLE 6.6.1]

CATEGORY MINIMUMREQUIREMENT CONDITIONS

Mechanical ventilation1 50 ft3/min outdoor air

When summer designinfiltration rate calcu-lated in accordance withreference standard A orB is less than 0.35 ach2

Kitchen exhaust 100 ft3/min intermittent All conditionsBath exhaust intermittent All conditions


priate performance descriptor of HVAC products in accor-dance with federal law or as specified in Table 702.9, as appli-cable. These shall be based on newly produced equipment orcomponents. Manufacturers’ recommended maintenanceinstructions shall be furnished with and attached to the equip-ment. The manufacturer of electric-resistance heating equip-ment shall furnish full-load energy input over the range ofvoltages at which the equipment is intended to operate.[ASHRAE 90.2:6.9]

702.10 Controls.702.10.1 Temperature Control. Each system or eachzone within a system shall be provided with at least onethermostat capable of being set from 55°F (13°C) to 85°F(29°C) and capable of operating the system’s heating andcooling. The thermostat or control system, or both, shallhave an adjustable deadband, the range of which includesa setting of 10°F (-12°C) between heating and coolingwhen automatic changeover is provided. Wall-mountedtemperature controls shall be mounted on an inside wall.[ASHRAE 90.2:6.10.1]

702.10.1.1 Initial Control Setting. The Controlshall initially be set for a maximum heating temper-ature of 70°F (21°C) and a cooling temperature ofnot less than 78°F (26°C).

702.10.2 Ventilation Control. Each mechanicalventilation system (supply, exhaust, or both) shall beequipped with a readily accessible switch or other meansfor shutoff. Manual or automatic dampers installed forthe purpose of isolating outside air intakes and exhaustsfrom the air distribution system shall be designed fortight shutoff. [ASHRAE 90.2:6.10.2]702.10.3 Humidity Control.

702.10.3.1 Heating. If additional energy-consuming equipment is provided for adding mois-ture to maintain specific selected relative humiditiesin spaces or zones, a humidistat shall be provided.This device shall be capable of being set to preventenergy from being used to produce relative humidity

within the space above 30 percent. [ASHRAE90.2:6.10.3.1]702.10.3.2 Cooling. If additional energy-consuming equipment is provided for reducinghumidity, it shall be equipped with controls capableof being set to prevent energy from being used toproduce a relative humidity within the space below50 percent during periods of human occupancy andbelow 60 percent during unoccupied periods.[ASHRAE 90.2:6.10.3.2]

702.10.4 Freeze Protection Systems. Freezeprotection systems, such as heat tracing of outdoor pipingand heat exchangers, including self-regulating heattracing, shall include automatic controls capable of shut-ting off the systems when outdoor air temperatures areabove 40°F (4°C) or when the conditions of the protectedfluid will prevent freezing. Snow- and ice-meltingsystems shall include automatic controls capable of shut-ting off the systems when the pavement temperature isabove 50°F (10°C) and no precipitation is falling and anautomatic or manual control that will allow shutoff whenthe outdoor temperature is above 40°F (4°C) so that thepotential for snow or ice accumulation is negligible.[ASHRAE 90.1:6.4.3.7] 702.10.5 Other Controls. When setback, zoned,humidity and cooling controls and equipment areprovided, they shall be designed and installed in accor-dance with Section 702.10. [ASHRAE 90.2:6.10.3.3]

702.11 Whole House Fans. Whole house exhaust fansshall have insulated louvers or covers which close when thefan is off. Covers or louvers shall have a insulation value ofnot less than R-4.2, and shall be installed in accordance withmanufacturer’s instructions. The attic openings shall be suffi-cient to accommodate the ventilation capacity of the wholehouse fan. The operation of the whole house fan shall beconsidered in determining the adequacy of providing combus-tion air in accordance with the mechanical code. 702.12 Attic Fans. Reserved.702.13 Dampers. Dampers shall be installed to close offoutdoor air inlets and exhaust outlets when the ventilationsystem is not operating.

703.0 Heating, Ventilation, and Air-Conditioning –Other Than Low-Rise Residential Buildings. 703.1 General. The heating, ventilation, and air-condi-tioning in buildings, other than single-family houses, multi-family structures of three stories or fewer above grade, andmodular houses, shall be in accordance with this section.

703.1.1 Scope.703.1.1.1 New Buildings. Mechanical equipmentand systems serving the heating, cooling, or venti-lating, or refrigeration needs of new buildings shallcomply with the requirements of this section asdescribed in Section 703.2. [ASHRAE 90.1:6.1.1.1]703.1.1.2 Additions to Existing Buildings.Mechanical equipment and systems serving theheating, cooling, or ventilating needs of additions to



EQUIPMENTTYPE

SUBCATE-GORY OR

RATING CONDI-TION

MINIMUMEFFICIENCY

TESTPROCEDURE

Ground-water* sourceheat pump

Cooling Mode

11.0 EER @ 70ºFEnt. Water

ISO 13256-111.5 EER @ 50ºFEnt. Water

Heating Mode

3.4 COP @ 70ºFEnt. Water

ISO 13256-13.0 COP @ 50ºFEnt. Water

For SI units: t/ºC = (t/ºF-32)/1.8* Performance for electrically powered equipment with capacity less than

65 000 Btu/h (19.0 kW) when rated in accordance with ARI Standard 325.

TABLE 702.9MINIMUM REQUIREMENTS FOR NON-FEDERALLY COVERED

HVAC EQUIPMENT[ASHRAE 90.2: TABLE 6.9]


existing buildings shall comply with the require-ments of this section as described in Section 703.2.Exception: When HVAC to an addition is providedby existing HVAC systems and equipment, suchexisting systems and equipment shall not be requiredto comply with this supplement. However, any newsystems or equipment installed must comply withspecific requirements applicable to those systemsand equipment. [ASHRAE 90.1:6.1.1.2]703.1.1.3 Alterations to Heating, Ventilating,and Air-Conditioning in Existing Buildings.

703.1.1.3.1 New HVAC equipment as a directreplacement of existing HVAC equipment shallcomply with the specific minimum efficiencyrequirements applicable to that equipment.[ASHRAE 90.1:6.1.1.3.1]703.1.1.3.2 New cooling systems installed toserve previously uncooled spaces shall complywith this section as described in Section 703.2.[ASHRAE 90.1:6.1.1.3.2]703.1.1.3.3 Alterations to existing coolingsystems shall not decrease economizer capa-bility unless the system complies with Section703.5.1. [ASHRAE 90.1:6.1.1.3.3]703.1.1.3.4 New and replacement ductworkshall comply with Section 703.4.4.1 and Section703.4.4.2. [ASHRAE 90.1:6.1.1.3.4]703.1.1.3.5 New and replacement piping shallcomply with Section 703.4.4.1. [ASHRAE90.1: 6.1.1.3.5]Exceptions: Compliance shall not be required:(1) for equipment that is being modified or

repaired but not replaced, provided that suchmodifications, repairs for the following orboth will not result in an increase in theannual energy consumption of the equip-ment using the same energy type.

(2) where a replacement or alteration of equip-ment requires extensive revisions to othersystems, equipment, or elements of abuilding, and such replaced or altered equip-ment is a like-for-like replacement.

(3) for a refrigerant change of existing equip-ment.

(4) for the relocation of existing equipment.(5) for ducts and pipes where there is insuffi-

cient space or access to meet these require-ments.

703.2 Compliance Path(s).703.2.1 Compliance Compliance with Section 703.0shall be achieved by meeting all requirements for Section703.1, General; Section 703.7, Submittals; Section 703.8,Minimum Equipment Efficiency Tables; and either:(1) Section 703.3, Simplified Approach Option for

HVAC Systems.

(2) Section 703.4, Mandatory Provisions; and Section703.5, Prescriptive Path. [ASHRAE 90.1:6.2.1]

Exception: Projects using the Energy Cost BudgetMethod of Section 11 of ASHRAE 90.1, provided suchprojects comply with Section 703.4, the mandatory provi-sions of this section, as a portion of that compliance path.

703.3 Simplified Approach Option for HVACSystems.

703.3.1 Scope. The simplified approach is an optionalpath for compliance when the following conditions aremet:(1) Building is two stories or fewer in height.(2) Gross floor area is less than 25 000 ft2 (2323 m2).(3) Each HVAC system in the building complies with

the requirements listed in Section 703.3.2.[ASHRAE 90.1:6.3.1]

703.3.2 Criteria. The HVAC system must meet all ofthe following criteria:(1) The system serves a single HVAC zone. (2) The equipment must meet the variable flow require-

ments of Section 703.4.3.10.(3) Cooling (if any) shall be provided by a unitary pack-

aged or split-system air conditioner that is either air-cooled or evaporatively cooled with efficiencymeeting the requirements shown in Table 703.8.1(1)(air conditioners), Table 703.8.1(2) (heat pumps), orTable 703.8.1(4) (packaged terminal and room airconditioners and heat pumps) for the applicableequipment category.

(4) The system shall have an air economizer meetingthe requirements of Section 703.5.1.

(5) Heating (if any) shall be provided by a unitary pack-aged or split-system heat pump that meets the appli-cable efficiency requirements shown in Table703.8.1(2) (heat pumps) or Table 703.8.1(4) (pack-aged terminal and room air conditioners and heatpumps), a fuel-fired furnace that meets the appli-cable efficiency requirements shown in Table703.8.1(5) (furnaces, duct furnaces, and unitheaters), an electric resistance heater, or a baseboardsystem connected to a boiler that meets the appli-cable efficiency requirements shown in Table703.8.1(6) (boilers).

(6) The system shall meet the exhaust air energyrecovery requirements of Section 703.5.6.1.

(7) The system shall be controlled by a manualchangeover or dual setpoint thermostat.

(8) If a heat pump equipped with auxiliary internal elec-tric resistance heaters is installed, controls shall beprovided that prevent supplemental heater operationwhen the heating load can be met by the heat pumpalone during both steady-state operation and setbackrecovery. Supplemental heater operation is permittedduring outdoor coil defrost cycles. The heat pumpmust be controlled by either:




(a) A digital or electronic thermostat designed forheat pump use that energizes auxiliary heat onlywhen the heat pump has insufficient capacity tomaintain setpoint or to warm up the space at asufficient rate.

(b) A multistage space thermostat and an outdoor airthermostat wired to energize auxiliary heat onlyon the last stage of the space thermostat and whenoutside air temperature is less than 40°F (4°C).Heat pumps whose minimum efficiency is regu-lated by NAECA and whose HSPF rating bothmeets the requirements shown in Table 703.8.1(2)and includes all usage of internal electric resist-ance heating are exempted from the controlrequirements of this part [Section 703.3.2(7)].

(9) The system controls shall not permit reheat or anyother form of simultaneous heating and cooling forhumidity control.

(10) Systems serving spaces other than hotel/motel guestrooms, and other than those requiring continuousoperation, which have both a cooling or heatingcapacity greater than 15 000 Btu/h (4.4 kW) and asupply fan motor power greater than 3⁄4 horsepower(hp) (0.6 kW), shall be provided with a time clockthat:(a) Can start and stop the system under different

schedules for seven different day-types perweek.

(b) Capable of retaining programming and timesetting during a loss of power for a period of atleast 10 hours.

(c) Includes an accessible manual override thatallows temporary operation of the system for upto two hours.

(d) Capable of temperature setback down to 55°F(13ºC) during off hours.

(e) Capable of temperature setup to 90°F (32ºC)during off hours.

(11) Except for piping within manufacturer’s units,HVAC piping shall be insulated in accordance withTable 703.8.3. Insulation exposed to weather shall besuitable for outdoor service (e.g., protected byaluminum, sheet metal, painted canvas, or plasticcover). Cellular foam insulation shall be protected asabove or painted with a coating that is water retar-dant and provides shielding from solar radiation.

(12) Ductwork and plenums shall be insulated in accor-dance with Table 703.8.2(1) and Table 703.8.2(2)and shall be sealed in accordance with Table703.4.4.2(1).

(13) Construction documents shall require a ducted systemto be air balanced in accordance with industry-accepted procedures.

(14) Outdoor air intake and exhaust systems shall meet therequirements of Section 703.4.3.4.

(15) Where separate heating and cooling equipmentserves the same temperature zone, thermostats shallbe interlocked to prevent simultaneous heating andcooling.

(16) Systems with a design supply air capacity greaterthan 10 000 ft3/min (4719.4 L/s) shall have optimumstart controls.

(17) The system shall comply with the demand controlventilation requirements in Section 703.4.3.9.[ASHRAE 90.1:6.3.2]

703.3.3 Climate Zone Determination. Climatezones identified in this supplement shall be determined inaccordance with Section 5.1.4 of ASHRAE 90.1.Exception: If recorded historical climatic data are avail-able for a construction site, it is permitted to be used todetermine compliance if approved by the AuthorityHaving Jurisdiction.

703.4 Mandatory Provisions.703.4.1 Equipment Efficiencies, Verification, andLabeling Requirements.

703.4.1.1 Minimum Equipment Efficien-cies—Listed Equipment—Standard Ratingand Operating Conditions. Equipment shownin Table 703.8.1(1) through Table 703.8.1(7) shallhave a minimum performance at the specified ratingconditions when tested in accordance with the spec-ified test procedure. Where multiple rating condi-



TABLE 703.3.2703.5.1(3)ELIMINATE REQUIRED ECONOMIZER FOR COMFORT

COOLING BY INCREASING COOLING EFFICIENCY[ASHRAE 90.1: TABLE 6.3.26.5.1c]

Climate Zone Efficiency Improvementa

2a 17%2b 21%3a 27%3b 32%3c 65%4a 42%4b 49%4c 64%5a 49%5b 59%5c 74%6a 56%6b 65%7 72%8 77%

aIf a unit is rated with an IPLV, IEER or SEER then to eliminate therequired air or water economizer, the minimum cooling efficiency ofthe HVAC unit must be increased by the percentage shown. If the HVACunit is only rated with a full load metric like EER or COP cooling thenthese must be increased by the percentage shown.


tions or performance requirements are provided, theequipment shall satisfy all stated requirements,unless otherwise exempted by footnotes in the table.Equipment covered under the Federal Energy PolicyAct of 1992 (EPACT) shall have no minimum effi-ciency requirements for operation at minimumcapacity or other than standard rating conditions.Equipment used to provide water heating functionsas part of a combination system shall satisfy allstated requirements for the appropriate space heatingor cooling category.Tables are as follows:(1) Table 703.8.1(1) – Air Conditioners and

Condensing Units.(2) Table 703.8.1(2) – Heat Pumps.(3) Table 703.8.1(3) – Water-Chilling Packages

(see Section 703.4.1.2.1 for water-cooledcentrifugal water-chilling packages that aredesigned to operate at nonstandard conditions).

(4) Table 703.8.1(4) – Packaged Terminal andRoom Air Conditioners and Heat Pumps.

(5) Table 703.8.1(5) – Furnaces, Duct Furnaces,and Unit Heaters.

(6) Table 703.8.1(6) – Boilers.(7) Table 703.8.1(7) – Heat Rejection Equipment.(8) Table 703.8.1(8) – Heat Transfer Equpment.(9) Table 703.8.1(9) – Variable Refrigerant Flow

Air Conditioners.(10) Table 703.8.1(10) – Variable Refrigerant Flow

Air-to-Air and Applied Heat Pumps.(11) Table 703.8.1(11) – Air Conditioners Serving

Computer Rooms.Furnaces with input ratings of ≥225 000 Btu/h

(66 kW), including electric furnaces, that are notlocated within the conditioned space shall havejacket losses not exceeding 0.75 percent of the inputrating. Air conditioners primarily serving computerrooms and covered by ASHRAE Standard 127 shallmeet the requirements in Table 703.8.1(11). Allother air conditioners shall meet the requirements inTable 703.8.1(1). [ASHRAE 90.1:6.4.1.1]703.4.1.2 Minimum Equipment Efficiencies—Listed Equipment—Nonstandard Conditions.

703.4.1.2.1 Water-Cooled CentrifugalChilling Packages. Equipment not designedfor operation at AHRI Standard 550/590 testconditions of 44°F (7ºC) leaving chilled fluidtemperature and 85°F (29ºC) enteringcondenser-fluid temperature with 3 gallons perminute (gpm) per ton (0.0002 L/s/kg)condenser-fluid flow (and, thus, cannot betested to meet the requirements of Table703.8.1(3)) shall have maximum full-loadkW/ton and NPLV part-load ratings require-ments adjusted using the following equations:

(Equation 703.4.1.2.1)Adjusted maximum full-load kW/ton rating =(full-load kW/ton from Table 703.8.1(3))/KadjAdjusted maximum NPLV rating = (IPLV from Table 703.8.1(3))/Kadj

FLadj = FL/KadjPLVadj = IPLV/Kadj

Kadj = A x B

Where:FL = full-load kW/ton value from

Table 703.8.1(3)FLadj = maximum full-load kW/ton

rating, adjusted for nonstandardconditions

IPLV = IPLV value from Table 703.8.1(3)PLVadj = maximum NPLV rating, adjusted

for nonstandard conditionsA = 0.00000014592 x (LIFT)4 -

0.0000346496 x (LIFT)3 + 0.00314196 x (LIFT)2 - 0.147199 x (LIFT) + 3.9302

B = 0.0015 x LvgEvap + 0.934LIFT = LvgCond - LvgEvapLvgCond = Full-load condenser leaving

fluid temperature (°F)LvgEvap = Full-load evaporator leaving

temperature (°F)

The adjusted full-load and NPLV FLadj andPLVadj values are only applicable for centrifugalchillers meeting all of the following full-loaddesign ranges:(1) Minimum Evaporator Leaving Tempera-

ture: 36°F (2ºC)(2) Maximum Condenser Leaving Tempera-

ture: 115°F (46ºC)(3) LIFT ≥ 20ºF and ≤ 80ºF

20ºF ≤ LIFT ≤ 80ºFManufacturers shall calculate the adjusted

maximum kW/ton and NPLV FLadj andPLVadj before determining whether to label thechiller per Section 703.4.1.5. Compliance with90.1-2007, or -2010, 2013 or both combinationsthereof, shall be labeled on chillers within thescope of the Standard.

Centrifugal chillers designed to operateoutside of these ranges are not covered by thisStandard.. [ASHRAE 90.1:6.4.1.2.1]Example: Path A 600 ton (600 000 kg)centrifugal chiller Table 703.8.1(3) efficiencieseffective 1/1/2015:




Full Load = 0.570 560 kW/tonIPLV = 0.539 500 kW/tonLvgCond = 91.16°FLvgEvap = 42°FLIFT = 91.16 – 42 = 49.16°F (10ºC) Kadj = A x BA = 0.00000014592 x (49.16)4 -

0.0000346496 x (49.16)3 + 0.00314196 x (4916)2 - 0.147199 x(4916) + 3.9302 = 1.0228

B = 0.0015 x 42 + 0.934 = 0.9970Adjusted full loadFLadj = 0.570 560/(1.0228 x 0.9970)

= 0.559 549 kW/tonNPLVadj = 0.539 500/(1.0228 x 0.9970) =0.529 490 kW/ton703.4.1.2.2 Positive Displacement (air-and water-cooled) Chilling Packages.Equipment with an evaporator leaving fluidtemperature higher than 32°F (0°C) and wter-cooled positive displacement chilling packageswith a condenser leaving fluid temperaturebelow 115°F shall show compliance with Table703.8.1(3) when tested or certified with waterat standard rating conditions, per the referencedtest procedure. [ASHRAE 90.1:6.4.1.2.2]

703.4.1.3 Equipment Not Listed. Equipmentnot listed in the tables referenced in Section703.4.1.1 and Section 703.4.1.2 may be used.[ASHRAE 90.1:6.4.1.3]703.4.1.4 Verification of Equipment Efficien-cies. Equipment efficiency information supplied bymanufacturers shall be verified as follows:(1) Equipment covered under EPACT shall comply

with U.S. Department of Energy certificationrequirements.

(2) If a certification program exists for a coveredproduct, and it includes provisions for verifica-tion and challenge of equipment efficiencyratings, then the product shall be listed in thecertification program, or

(3) If a certification program exists for a coveredproduct, and it includes provisions for verifica-tion and challenge of equipment efficiencyratings, but the product is not listed in theexisting certification program, the ratings shallbe verified by an independent laboratory testreport, or

(4) If no certification program exists for a coveredproduct, the equipment efficiency ratings shallbe supported by data furnished by the manu-facturer, or

(5) Where components such as indoor or outdoorcoils from different manufacturers are used, the

system designer shall specify component effi-ciencies whose combined efficiency meets theminimum equipment efficiency requirements inSection 703.4.1.

(6) Requirements for plate type liquid-to-liquidheat exchangers are listed in Table 703.8.1(8).[ASHRAE 90.1:6.4.1.4]

703.4.1.5 Labeling.703.4.1.5.1 Mechanical Equipment.Mechanical equipment that is not covered bythe U.S. National Appliance Energy Conserva-tion Act (NAECA) of 1987 shall carry a perma-nent label installed by the manufacturer statingthat the equipment complies with the require-ments of ASHRAE 90.1. [ASHRAE90.1:6.4.1.5.1]703.4.1.5.2 Packaged Terminal AirConditioners. Nonstandard size packagedterminal air conditioners and heat pumps withexisting sleeves having an external wall openingof less than 16 inches (406 mm) high or lessthan 42 inches (1067 mm) wide and having across-sectional area less than 670 square inches(in2) (0.43226 m2) shall be factory labeled asfollows: Manufactured for nonstandard sizeapplications only: not to be installed in newconstruction projects. [ASHRAE 90.1:6.4.1.5.2]

703.4.2 Calculations.703.4.2.1 Load Calculations. Heating and coolingsystem design loads for the purpose of sizing systemsand equipment shall be determined in accordance withANSI/ASHRAE/ACCA Standard 183-2007, PeakCooling and Heating Load Calculations in BuildingExcept Low-Rise Residential Buildings. [ASHRAE90.1:6.4.2.1]703.4.2.2 Pump Head. Pump differential pressure(head) for the pupose of sizing pumps shall be deter-mined in accordance with generally accepted engi-neering standards and handbooks acceptable to theadopting authority. The pressure drop through eachdevice and pipe segment in the critical circuit at designconditions shall be calculated. [ASHRAE90.1:6.4.2.2]703.4.2.3 System Sizing. Reserved.

703.4.3 Controls.703.4.3.1 Zone Thermostatic Controls.

703.4.3.1.1 General. The supply of heatingand cooling energy to each zone shall be indi-vidually controlled by thermostatic controlsresponding to temperature within the zone. Forthe purposes of Section 703.4.3.1, a dwellingunit shall be permitted to be considered a singlezone. [ASHRAE 90.1:6.4.3.1.1]Exceptions: Independent perimeter systemsthat are designed to offset only building enve-lope loads shall be permitted to serve one or




more zones also served by an interior systemprovided:(1) The perimeter system includes at least one

thermostatic control zone for each buildingexposure having exterior walls facing onlyone orientation for 50 contiguous feet (15 240 mm) or more.

(2) The perimeter system heating and coolingsupply is controlled by a thermostaticcontrol(s) located within the zones(s)served by the system.Exterior walls are considered to have

different orientations if the directions they facediffer by more than 45 degrees (0.79 rad).703.4.3.1.2 Dead Band. Where used tocontrol both heating and cooling, zone thermo-static controls shall be capable of providing atemperature range or dead band of not less than5°F (-15ºC) within which the supply of heatingand cooling energy to the zone is shut off orreduced to a minimum. [ASHRAE 90.1:6.4.3.1.2]Exceptions:(1) Thermostats that require manual changeover

between heating and cooling modes.(2) Special occupancy or special applications

where wide temperature ranges are notacceptable (such as retirement homes,process applications, museums, some areasof hospitals) and are approved by theAuthority Having Jurisdiction.

703.4.3.2 Setpoint Overlap Restriction. Whereheating and cooling to a zone are controlled by sepa-rate zone thermostatic controls located within thezone, means (such as limit switches, mechanicalstops, or, for DDC systems, software programming)shall be provided to prevent the heating setpoint fromexceeding the cooling setpoint minus any applicableproportional band. [ASHRAE 90.1:6.4.3.2]703.4.3.3 Off-Hour Controls. HVAC systemsshall have the off-hour controls required by Section703.4.3.3.1 through Section 703.4.3.3.4. [ASHRAE90.1:6.4.3.3]Exceptions:(1) HVAC systems intended to operate continu-

ously.(2) HVAC systems having a design heating

capacity and cooling capacity less than 15 000Btu/h (4.4 kW) that are equipped with readilyaccessible manual ON/ OFF controls.703.4.3.3.1 Automatic Shutdown. HVACsystems shall be equipped with at least one ofthe following:(1) Controls that can start and stop the system

under different time schedules for sevendifferent day-types per week, are capableof retaining programming and time setting

during loss of power for a period of not lessthan 10 hours, and include an accessiblemanual override, or equivalent function,that allows temporary operation of thesystem for up to 2 hours.

(2) An occupant sensor that is capable of shut-ting the system off when no occupant issensed for a period of up to 30 minutes.

(3) A manually operated timer capable ofbeing adjusted to operate the system for upto 2 hours.

(4) An interlock to a security system that shutsthe system off when the security system isactivated. [ASHRAE 90.1:6.4.3.3.1]

Exception: Residential occupancies shall usecontrols that can start and stop the system undertwo different time schedules per week.703.4.3.3.2 Setback Controls. Heatingsystems located in climate zone 2 through zone8 shall be equipped with controls that have thecapability configured to automatically restart andtemporarily operate the system as required tomaintain zone temperatures above an adjustableheating setpoint adjustable down to 55°F (13ºC)or lower at least 10°F below the occupied heatingsetpoint. Cooling systems located in climatezones 1b, 2b, and 3b shall be equipped withcontrols that have the capability configured toautomatically restart and temporarily operate themechanical cooling system as required to main-tain zone temperatures below an adjustablecooling setpoint adjustable up to 90°F (32ºC) orhigher at least 5°F above occupied coolingsetpoint or to prevent high space humidity levels.[ASHRAE 90.1:6.4.3.3.2]Exception: Radiant floor and ceiling heatingsystems configured with a setback heatingsetpoint at least 4°F below the occupied heatingsetpoint..703.4.3.3.3 Optimum Start Controls. Indi-vidual heating and cooling air distributionsystems with a total design supply air capacityexceeding 10 000 ft3/min (4719.4 L/s), served byone or more supply fans, setback controls andDDC shall have optimum start controls. Thecontrol algorithm shall, as a minimum, be a func-tion of the difference between space temperatureand occupied setpoint and the amount of timeprior to scheduled occupancy. Mass radiant floorslab systems shall incorporate floor temperatureinto the optimum start algorithm. [ASHRAE90.1:6.4.3.3.3]703.4.3.3.4 Zone Isolation. HVAC systemsserving zones that are intended to operate or beoccupied nonsimultaneously shall be dividedinto isolation areas. Zones may be grouped intoa single isolation area provided it does not




exceed 25 000 ft2 (2323 m2) of conditionedfloor area nor include more than one floor. Eachisolation area shall be equipped with isolationdevices capable of automatically shutting offthe supply of conditioned air and outdoor air toand exhaust air from the area. Each isolationarea shall be controlled independently by adevice meeting the requirements of Section703.4.3.3.1, Automatic Shutdown. For centralsystems and plants, controls and devices shallbe provided to allow stable system and equip-ment operation for any length of time whileserving only the smallest isolation area servedby the system or plant. [ASHRAE90.1:6.4.3.3.4]Exceptions: Isolation devices and controls arenot required for the following:(1) Exhaust air and outdoor air connections to

isolation zones when the fan system towhich they connect is 5000 ft3/min (2360L/s) and smaller.

(2) Exhaust airflow from a single isolationzone of less than 10 percent of the designairflow of the exhaust system to which itconnects.

(3) Zones intended to operate continuously orintended to be inoperative only when allother zones are inoperative.

703.4.3.4 Ventilation System Controls.703.4.3.4.1 Stair and Shaft Vents. Stairand elevator shaft vents shall be equipped withmotorized dampers that are capable of beingautomatically closed during normal buildingoperation and are interlocked to open asrequired by fire and smoke detection systems.

[ASHRAE 90.1:6.4.3.4.1]703.4.3.4.2 Shutoff Damper Controls.Both All outdoor air supply intake and exhaustsystems shall be equipped with motorizeddampers that will automatically shut when thesystems or spaces served are not in use. Ventila-tion outdoor air and exhaust/relief dampers shallbe capable of automatically shutting off duringpreoccupancy building warm-up, cool down, andsetback, except when ventilation reduces energycosts (e.g., night purge) or when ventilation mustbe supplied to meet code requirements.[ASHRAE 90.1:6.4.3.4.2]Exceptions:(1) Backdraft gravity (nonmotorized) dampers

are acceptable for exhaust and relief inbuildings less than three stories in heightand for ventilation air intakes and exhaustand relief dampers in buildings of anyheight located in climate zone 1 throughzone 3. Backdraft dampers for ventilationair intakes must be protected from directexposure to wind.

(2) Backdraft gravity (nonmotorized) dampersare acceptable in systems with a designoutdoor air intake or exhaust capacity of300 ft3/min (142.0 L/s) or less.

(3) Dampers are not required in ventilation orexhaust systems serving unconditionedspaces.

(4) Dampers are not required in exhaustsystems serving Type 1 kitchen exhausthoods.

703.4.3.4.3 Damper Leakage. Whereoutdoor air supply and exhaust/relief dampers



VENTILATION AIR INTAKE EXHAUST/RELIEF

CLIMATE ZONE NONMOTORIZED1 MOTORIZED NONMOTORIZED1 MOTORIZED

1, 2any height

–20

–4

–20 4

3any height

–20

–10

–20 10

4, 5b, 5cless than 3 stories3 or more stories

–not allowednot allowed

–1010

–20

not allowed1010

5a, 6, 7, 8less than 3 stories3 or more stories

–not allowednot allowed

–44

–20

not allowed44

For SI units: 1 inch = 25.4 mm, 1 cubic foot per minute = 0.06 L/s, 1 square foot = 0.929 m2, 1 inch water gauge = 0.249 kPa1 Dampers smaller than 24 inches (610 mm) in either dimension shall have leakage of 40 (ft3/min)/ft2 (203 L/s/m2).

TABLE 703.4.3.4.3 MAXIMUM DAMPER LEAKAGE(ft3/min/ft2) at 1.0 in. w.g.

[ASHRAE 90.1: TABLE 6.4.3.4.3]


are required by Section 703.4.3.4, they shallhave a maximum leakage rate as indicated inTable 703.4.3.4.3 when tested in accordancewith AMCA Standard 500. [ASHRAE90.1:6.4.3.4.3]703.4.3.4.4 Ventilation Fan Controls. Fanswith motors greater than 0.75 hp (0.6 kW) shallhave automatic controls complying with Section703.4.3.3.1 that are capable of shutting off fanswhen not required. [ASHRAE 90.1:6.4.3.4.4]Exception: HVAC systems intended to operatecontinuously.703.4.3.4.5 Enclosed Parking GarageVentilation. Heat Enclosed parking garageventilation systems shall automatically detectcontaminant levels and stage fans or modulatefan airflow rates to 50 percent or less of designcapacity provided acceptable contaminant levelsare maintained. [ASHRAE 90.1:6.4.3.4.5]Exceptions:(1) Garages less than 30 000 square feet (2800

m2) with ventilation systems that do notutilize mechanical cooling or mechanicalheating.

(2) Garages that have a garage area to ventila-tion system motor nameplate hp ratio thatexceeds 1500 ft2/hp (186 m2/kW) and do notutilize mechanical cooling or mechanicalheating.

(3) Where not permitted by the AuthorityHaving Jurisdiction.

703.4.3.5 Heat Pump Auxiliary Heat Control.Heat pumps equipped with internal electric resist-ance heaters shall have controls that prevent supple-mental heater operation when the heating load canbe met by the heat pump alone during both steady-state operation and setback recovery. Supplementalheater operation is permitted during outdoor coildefrost cycles. [ASHRAE 90.1:6.4.3.5]Exceptions: Heat pumps whose minimum effi-ciency is regulated by U.S. National ApplianceEnergy Conservation Act (NAECA) and whoseHSPF rating both meets the requirements shown inTable 703.8.1(2) and includes all usage of internalelectric resistance heating.703.4.3.6 Humidifier Preheat. Humidifiers withpreheating jackets mounted in the airstream shall beprovided with an automatic valve to shut off preheatwhen humidification is not required. [ASHRAE90.1:6.4.3.6]703.4.3.76 Humidification and Dehumidifi-cation. Humidity control shall prevent the use offossil fuel or electricity to produce RH above 30percent in the warmest zone served by the humidifi-cation system and to reduce RH below 60 percent inthe coldest zone served by the dehumidification

system. Where a zone is served by a system orsystems with both humidification and dehumidifi-cation capability, means (such as limit switches,mechanical stops, or, for DDC systems, softwareprogramming) shall be provided capable ofpreventing simultaneous operation of humidificationand dehumidification equipment. [ASHRAE90.1:6.4.3.76]Exceptions:(1) Zones served by desiccant systems, used with

direct evaporative cooling in series.(2) Systems serving zones where specific humidity

levels are required, such as museums and hospi-tals, and approved by the Authority HavingJurisdiction or required by accreditation stan-dards and humidity controls are configured tomaintain a deadband of at least 10 percent RHwhere no active humidifcation or dehumidifi-cation takes place.

(3) Systems serving zones where humidity levelsare required to be maintained with precision ofnot more than ±5 percent RH to comply withapplicable codes or accreditation standards oras approved by the Authority Having Jurisdic-tion..

703.4.3.87 Freeze Protection and Snow/IceMelting Systems. Freeze protection systems,such as heat tracing of outdoor piping and heatexchangers, including self-regulating heat tracing,shall include automatic controls capable of shuttingoff the systems when outdoor air temperatures areabove 40°F (4ºC) or when the conditions of theprotected fluid will prevent freezing. Snow- and ice-melting systems shall include automatic controlscapable of shutting off the systems when the pave-ment temperature is above 50°F (10ºC) and noprecipitation is falling and an automatic or manualcontrol that will allow shutoff when the outdoortemperature is above 40°F (4ºC) so that the potentialfor snow or ice accumulation is negligible.[ASHRAE 90.1:6.4.3.87]703.4.3.98 Ventilation Controls for High-Occupancy Areas. Demand control ventilation(DCV) is required for spaces larger than 500 ft2

(46.45 m2) and with a design occupancy for ventila-tion of greater than 40 25 people per 1000 ft2 (93 m2)of floor area and served by systems with one or moreof the following:(1) An air-side economizer.(2) An automatic modulating control of the outdoor

air damper, or(3) A design outdoor airflow greater than 3000

ft3/min (1416.0 L/s). [ASHRAE 90.1:6.4.3.98]Exceptions:(1) Systems with the exhaust air energy recovery

complying with Section 703.5.6.1.




(2) Multiple-zone systems without DDC of indi-vidual zones communicating with a centralcontrol panel.

(3) Systems with a design outdoor airflow less than1200 750 ft3/min (566 L/s).

(4) Spaces where more than 75 percent of the spacedesign outdoor airflow is required for supplyairflow rate minus any makeup or outgoingtransfer air requirement is less than 1200 ft3/min(566 L/s) air that is exhasted from the space ortransfer air that is required for makeup air thatis exhausted from other space(s).

(5) Spaces with one of the following occupancycategories as defined in ASHRAE Standard62.1: correctional cells, daycare sickrooms,science labs, barbers, beauty and nail salons,and bowling alley seating

703.4.3.10 Single Zone Variable-Air-VolumeControls. HVAC systems shall have variable airflowcontrols as follows:(1) Air-handling and fan-coil units with chilled-water

cooling coils and supply fans with motors greaterthan or equal to 5.36 hp (4 kW) shall have theirsupply fans controlled by two-speed motors orvariable-speed drives. At cooling demands lessthan or equal to 50 percent, the supply fancontrols shall be able to reduce the airflow to nogreater than the larger of the following:(a) One half of the full fan speed , or(b) The volume of outdoor air required to meet the

ventilation requirements of ASHRAE 62.1.(2) Effective January 1, 2012, all air-conditioning

equipment and air-handling units with directexpansion cooling and a cooling capacity atAHRI conditions greater than or equal to 110 000Btu/h (32.2 kW) that serve single zones shall havetheir supply fans controlled by two-speed motorsor variable-speed drives. At cooling demands lessthan or equal to 50 percent, the supply fancontrols shall be able to reduce the airflow to nogreater than the larger of the following:

(a) Two-thirds of the full fan speed, or(b) The volume of outdoor air required to meet the

ventilation requirements of ASHRAE 62.1.[ASHRAE 90.1:6.4.3.10]

703.4.3.9 Heating in Vestibules. Heating forvestibules, in accordance with Section 5.4.3.4, andair curtains shall include automatic controls config-ured to shut off the heating system when outdoor airtemperatures are above 45°F. Vestibule heatingsystems shall also be controlled by a thermostat inthe vestibule with a setpoint limited to a maximumof 60°F.Exception: Vestibules with no heating system orthat are tempered with transfer air that would other-wise be exhausted.[ASHRAE 90.1:6.4.3.9]

703.4.3.10 Direct Digital Control (DDC)Requirements. Direct digital control shall berequired as follows. [ASHRAE 90.1:6.4.3.10]

703.4.3.10.1 DDC Applications. DDCshall be provided in the applications and quali-fications listed in Table 6.4.3.10.1.Exception: DDC is not required for systemsusing the simplified approach to compliance inaccordance with Section 6.3. [ASHRAE90.1:6.4.3.10.1]703.4.3.10.2 DDC Controls. Where DDC isrequired by Section 6.4.3.10.1, the DDC systemshall be capable of all of the following, asrequired, to provide the control logic requiredin Section 6.5:a. Monitoring zone and system demand for

fan pressure, pump pressure, heating, andcooling

b. ransferring zone and system demand infor-mation from zones to air distributionsystem controllers and from air distributionsystems to heating and cooling plantcontrollers

c. Automatically detecting those zones andsystems that may be excessively drivingthe reset logic and generate an alarm orother indication to the system operator

d. Readily allowing operator removal ofzone(s) from the reset algorithm

703.4.3.10.3 DDC Display. Where DDC isrequired by Section 6.4.3.10.1 for new build-ings, the DDC system shall be capable oftrending and graphically displaying input andoutput points.

703.4.3.11 Outdoor Heating. Only radiant heatsystems shall be used to provide heat outdoors.Outdoor radiant heating systems shall be providedwith controls that sense the presence of occupantsor other device that automatically shuts down thesystem when no occupants are in the heating area.

703.4.4 HVAC System Construction and Insula-tion. HVAC Ducts shall be constructed in accordancewith provisions contained in the SMACNA HVAC DuctConstruction Standard. HVAC system construction andinsulation shall also comply with Section 703.4.4.1through Section 703.4.4.2.

703.4.4.1 Insulation.703.4.4.1.1 General. Insulation required bythis section shall be installed in accordance withindustry-accepted standards (see InformativeAppendix E of ASHRAE 90.1). These require-ments do not apply to HVAC equipment. Insu-lation shall be protected from damage,including that due to sunlight, moisture, equip-ment maintenance, and wind, but not limited tothe following:




(1) Insulation exposed to weather shall be suit-able for outdoor service (e.g., protected byaluminum, sheet metal, painted canvas, orplastic cover). Cellular foam insulationshall be protected as above or painted witha coating that is water retardant andprovides shielding from solar radiation thatcan cause degradation of the material.

(2) Insulation covering chilled-water piping,refrigerant suction piping, or cooling ductslocated outside the conditioned space shallinclude a vapor retardant located outsidethe insulation (unless the insulation isinherently vapor retardant), all penetrationsand joints of which shall be sealed.[ASHRAE 90.1:6.4.4.1.1]

703.4.4.1.2 Duct and Plenum Insulation.All supply and return ducts and plenumsinstalled as part of an HVAC air distributionsystem shall be thermally insulated in accor-dance with Table 703.8.2(1) and Table703.8.2(2). [ASHRAE 90.1:6.4.4.1.2]Exceptions:(1) Factory-installed plenums, casings, or

ductwork furnished as a part of HVACequipment tested and rated in accordancewith Section 703.4.1.

(2) Ducts or plenums located in heated spaces,semi-heated spaces, or cooled spaces.

(3) For runouts less than 10 feet (3048 mm) inlength to air terminals or air outlets, the ratedR-value of insulation need not exceed R-3.5.

(4) Backs of air outlets and outlet plenumsexposed to unconditioned or indirectlyconditioned spaces with face areas exceeding5 ft2 (0.5 m2) need not exceed R-2; those 5 ft2

(0.5 m2) or smaller need not be insulated.703.4.4.1.3 Piping Insulation. Piping shallbe thermally insulated in accordance withTables 703.8.3 and 703.8.3B. [ASHRAE90.1:6.4.4.1.3]Exceptions:(1) Factory-installed piping within HVAC

equipment tested and rated in accordancewith Section 703.4.1.

(2) Piping that conveys fluids having a designoperating temperature range between 60°F(16ºC) and 105°F (41ºC), inclusive.

(3) Piping that conveys fluids that have notbeen heated or cooled through the use offossil fuels or electricity (such as roof andcondensate drains, domestic cold watersupply, natural gas piping).

(4) Where heat gain or heat loss will not increaseenergy usage (such as liquid refrigerantpiping).

(5) In piping 1 inch (25.4 mm) or less, insula-



TABLE 703.4.3.10 DDC Applications and Qualifications

[ASHRAE 90.1:6.4.3.10.1]Building Status Application Qualifications

New building Air-handling system and all zones served by thesystem

Individual systems supplying more than three zonesand with fan system bhp of 10 hp and larger

New building Chilled-water plant and all coils and terminal unitsserved by the system

Individual plants supplying more than three zones andwith design cooling capacity of 300,000 Btu/h andlarger

New building Hot-water plant and all coils and terminal units servedby the system

Individual plants supplying more than three zones andwith design heating capacity of 300,000 Btu/h andlarger

Alteration or addition Zone terminal unit such as VAV box Where existing zones served by the same airhandling,chilled-water, or hot-water system have DDC

Alteration or addition Air-handling system or fan coil Where existing air-handling system(s) and fancoil(s)served by the same chilled- or hot-water plant haveDDC

Alteration or addition New air-handling system and all new zones served bythe system

Individual systems with fan system bhp of 10 hp andlarger and supplying more than three zones and morethan 75% of zones are new

Alteration or addition New or upgraded chilled-water plant Where all chillers are new and plant design coolingcapacity is 300,000 Btu/h and larger

Alteration or addition New or upgraded hot-water plant Where all boilers are new and plant design heatingcapacity is 300,000 Btu/h and larger


tion is not required for strainers, controlvalves, and balancing valves.

703.4.4.1.4 Sensible Heating Panel Insu-lation. All thermally ineffective panel surfacesof sensible heating panels, including U-bendsand headers, shall be insulated with a minimumof R-3.5. Adjacent envelope insulation countstoward this requirement. [ASHRAE90.1:6.4.4.1.4]703.4.4.1.5 Radiant Floor Heating. Thebottom surfaces of floor structures incorpo-rating radiant heating shall be insulated with aminimum of R-3.5. Adjacent envelope insula-tion counts toward this requirement. [ASHRAE90.1:6.4.4.1.5]Exception: Requirements for heated slab-on-

grade floors incorporating radiant heating are inChapter 5 of ASHRAE 90.1.

703.4.4.2 Ductwork and Plenum Leakage.703.4.4.2.1 Duct Sealing. Ductwork andplenums shall be sealed in accordance with



CLIMATE ZONES COOLING CAPACITY FOR WHICH AN ECONOMIZER IS REQUIRED

1a, 1b No economizer requirement

2a, 2b, 3a, 4a, 5a, 6a3b, 3c, 4b, 4c, 5b, 5c, 6b, 7, 8 ≥54 000 Btu/h

For SI units: 1000 British thermal units per hour = 0.293 kW

CLIMATE ZONES ALLOWED CONTROLTYPES

PROHIBITEDCONTROL TYPES

1b. 2b, 3b, 3c, 4b,4c, 5b, 5c, 6b, 7, 8

Fixed dry bulbDifferential dry bulbElectronic enthalpy1

Differential enthalpyDew-point and dry-bulb temperatures

Fixed enthalpy

1a, 2a. 3a, 4a

Fixed enthalpyElectronic enthalpyDifferential enthalpyDew-point and dry-bulb temperatures

Fixed Dry BulbDifferential dry bulb

5a, 6a

Fixed dry bulbDifferential dry bulbFixed enthalpyElectronic enthalpy1

Differential enthalpyDew-point and dry-bulb temperatures

1 Electronic enthalpy controllers are devices that use a combination ofhumidity and dry-bulb temperature in their switching algorithm.

TABLE 703.5.1.1.3(1)HIGH-LIMIT SHUTOFF CONTROL OPTIONS

FOR AIR ECONOMIZERS [ASHRAE 90.1: TABLE 6.5.1.1.3A]

TABLE 703.5.1(1)MINIMUM FAN-COOLING UNIT SIZE FOR WHICH AN

ECONOMIZER IS REQUIRED FOR COMFORT COOLING[ASHRAE 90.1: TABLE 6.5.1A]

CLIMATE ZONES COOLING CAPACITY FOR WHICH AN ECONOMIZER IS REQUIRED

1a, 1b, 2a, 3a, 4a No economizer requirement2b, 5a, 6a, 7, 8 ≥135 000 Btu/h

3b, 3c, 4b, 4c, 5b, 5c, 6b ≥65 000 Btu/hFor SI units: 1000 British thermal units per hour = 0.293 kW

TABLE 703.5.1(2)MINIMUM FAN-COOLING UNIT SIZE FOR WHICH AN

ECONOMIZER IS REQUIRED FOR COMPUTER ROOMS[ASHRAE 90.1: TABLE 6.5.1B]

SEALLEVEL SEALING REQUIREMENTS*

A

All transverse joints, longitudinal seams, and duct wallpenetrations. Pressure-sensitive tape shall not be usedas the primary sealant, unless it has been certified tocomply with UL-181A or UL-181B by an independenttesting laboratory and the tape is used in accordancewith that certification. [See note.]

B

All transverse joints, longitudinal seams. Pressure-sensi-tive tape shall not be used as the primary sealant, unlessit has been certified to comply with UL-181A or UL-181B by an independent testing laboratory and the tapeis used in accordance with that certification. [See note.]

C Transverse joints only.Note: UL-181A or UL-181B is not applicable to metal-to-metal duct joints.* Longitudinal seams are joints oriented in the direction of airflow. Trans-

verse joints are connections of two duct sections oriented perpendicular toairflow. Duct wall penetrations are openings made by any screw fastener,pipe, rod, or wire. Spiral lock seams in a round or flat oval duct need notbe sealed. All other connections are considered transverse joints, includingbut not limited to spin-ins, taps, and other branch connections, access doorframes and jambs, duct connections to equipment, etc.

DUCT LOCATION

DUCT TYPE

SUPPLYEXHAUST RETURN≤2 in.

w.c.2>2 in.w.c.2

Outdoor A A C AUnconditionedspaces B A C B

Conditioned spaces3 C B B CFor SI unit: 1 inch Water Column = 0.249 kPa1 See Table 703.4.4.2(2) description of seal level.2 Duct design static pressure classification.3 Includes indirectly conditioned spaces such as alum air plenums.

TABLE 703.4.4.2(1)MINIMUM DUCT SEAL LEVEL1

TABLE 703.4.4.2(2)DUCT SEAL LEVELS


Table 703.4.4.2(1) (Table 703.4.4.2(2) providesdefinitions of seal levels), as required to meetthe requirements of Section 703.4.4.2.2 and theSMACNA HVAC Duct Construction Standardor ASHRAE 90.1. 703.4.4.2.2 Duct Leakage Tests. Ductworkthat is designed to operate at static pressures inexcess of 3 inches Water Column (0.75 kPa)and all ductwork located outdoors shall be leak-tested according to the SMACNA HVAC AirDuct Leakage Test Manual. Representativesections totaling no less than 25 percent of thetotal installed duct area for the designated pres-sure class shall be tested. All sections shall beselected by the building owner or the designatedrepresentative of the building owner. Positivepressure leakage testing is acceptable for nega-tive pressure ductwork. The maximumpermitted duct leakage shall be:Lmax = CLP 0.65 (Equation 703.4.4.2.2)

Where:Lmax = maximum permitted leakage in

(ft3/min)/100 square feet (0.05

L/s/m2) duct surface area;CL = 46, duct leakage class, (ft3/min)/100

square feet (0.05 L/s/m2) duct surface area at 1 inch Water Column (0.24 kPa).

P = test pressure, which shall be equal tothe design duct pressure class rating in inchwater column (0.24 kPa) [based on ASHRAE90.1:6.4.4.2.2]

703.4.4.2.2.1 Duct Leakage Testswith Less than 3 inches WaterColumn. Ductwork that is designed tooperate at static pressures less than 3 inchesWater Column (0.75 kPa) located outdoorsand within unconditioned space shall beleak-tested according to the testing proce-dures contained in SMACNA HVAC AirDuct Leakage Test Manual or AssociatedAir Balance Council Procedural StandardsChapter 5 Leakage Testing. Positive pres-sure leakage testing is acceptable for nega-tive pressure ductwork.

703.4.5 Walk-In Coolers and Freezers. Site-assem-



DEVICE TYPE CLIMATE REQUIRED HIGH LIMIT(ECONOMIZER OFF WHEN):

EQUATION DESCRIPTION

Fixed dry bulbtemperature

1b, 2b, 3b, 3c, 4b, 4c, 5b, 5c, 6b, 7, 8, 5a, 6a

TOA > 75°F Outdoor air temperature exceeds 75°F

TOA > 70°F Outdoor air temperature exceeds 70°F

1a, 2a, 3a, 4a TOA > 65°F Outdoor air temperature exceeds 65°F

Differential dry bulbtemperature

lb. 2b, 3b, 3c, 4b, 4c, 5a, 5b, 5c, 6a, 6b, 7, 8 TOA>TRA

Outdoor air temperature exceeds return airtemperature

Fixed enthalpy withfixed dry-bulbtemperature

AllhOA > 28 Btu/lb1

or TOA,> 75°F

Outdoor air enthalpy exceeds 28 Btu/lb ofdry air1 or outdoor air temperature exceeds75°F

Electronic enthalpy All (TOA, RHOA) > A Outdoor air temperature/RH exceeds the"A" setpoint curve2

Differential enthalpywith fixed dry-bulbtemperature

AllhOA > hRAor TOA,> 75°F

Outdoor air enthalpy exceeds return airenthalpy or outdoor air temperature exceeds75°F

Dew-point and dry-bulb temperatures All DPoa>55°F or Toa>75°F Outdoor air dry bulb exceeds 75°F or

outside dew point exceeds 55°F (65 gr/lb)

For SI units: t/ºC = (t/ºF-32)/1.8, 1 British thermal unit per pound = 2326 J/kg1 At altitudes substantially different than sea level, the Fixed Enthalpy limit shall be set to the enthalpy value at 75°F (24ºC) and 50 percent relative

humidity. As an example, at approximately 6000 feet (1829 m) elevation the fixed enthalpy limit is approximately 30.7 Btu/lb (71 408 J/kg).2 Setpoint "A" corresponds to a curve on the psychrometric chart that goes through a point at approximately 75°F (24ºC) and 40 percent relative humidity

and is nearly parallel to dry-bulb lines at low humidity levels and nearly parallel to enthalpy lines at high humidity levels. Devices with selectable ratherthan adjustable setpoints shall be capable of being set within 2°F and 2 Btu/lb of the setpoint listed.

TABLE 703.5.1.1.3(2)HIGH-LIMIT SHUTOFF CONTROL SETTINGS

FOR AIR ECONOMIZERS[ASHRAE 90.1: TABLE 6.5.1.1.3B]


bled or site-constructed walk-in coolers and freezers shallconform to the following requirements:a. Shall be equipped with automatic door closers that

firmly close walk-in doors that have been closed towithin 1 in. of full closure.

Exception: Doors wider than 3 ft 9 in. or taller than 7 ftb. Doorways shall have strip doors (curtains), spring-

hinged doors, or other method of minimizing infil-tration when doors are open.

c. Walk-in coolers shall contain wall, ceiling, and doorinsulation of at least R-25 and walk-in freezers atleast R-32.

Exception: Glazed portions of doors or structuralmembers

d. Walk-in freezers shall contain floor insulation of atleast R-28.

e. Evaporator fan motors that are less than 1 hp andless than 460 V shall use electronically commutatedmotors (brushless direct-current motors) or three-phase motors.

f. Lights shall use light sources with an efficacy of 40lm/W or more, including ballast losses (if any).Light sources with an efficacy of less than 40 lm/W,including ballast losses (if any), may be used inconjunction with a timer or device that turns off thelights within 15 minutes of when the walk-in cooleror walk-in freezer is not occupied by people.

g. Transparent reach-in doors for walk-in freezers, andwindows in walk-in freezer doors, shall be of triple-pane glass, either filled with inert gas or with heat-reflective treated glass.

h. Transparent reach-in doors for walk-in coolers, andwindows in walk-in cooler doors, shall be double-pane glass with heat-reflective treated glass and gasfilled, or they shall be triple-pane glass, either filledwith inert gas or with heat-reflective treated glass.

i. Antisweat heaters without antisweat heater controlsshall have a total door rail, glass, and frame heaterpower draw of 7.1 W/ft2 of door opening for walk-in freezers and 3.0 W/ft2 of door opening for walk-in coolers.

j. Antisweat heater controls shall reduce the energyuse of the antisweat heater as a function of the rela-tive humidity in the air outside the door or to thecondensation on the inner glass pane.

k. Condenser fan motors that are less than 1 hp shalluse electronically commutated motors, permanentsplit capacitor-type motors, or three-phase motors.

l. All walk-in freezers shall incorporate temperature-based defrost termination control with a time limitdefault. The defrost cycle shall terminate first on anupper temperature limit breach and second upon atime limit breach.

Exception: Walk-in coolers and walk-in freezerscombined in a single enclosure greater than 3000 ft2

[ASHRAE 90.1:6.4.5]703.4.6 Refrigerated Display Casea. All refrigerated display cases shall conform to

Section 6.4.1.1 and Tables 6.8.1-1 through 6.8.1-13.b. Lighting in refrigerated display cases and glass

doors installed on walk-in coolers and freezers shallbe controlled by one of the following:1. Automatic time-switch controls to turn off

lights during nonbusiness hours. Timed over-rides for display cases or walk-in coolers andfreezers may be used to turn the lights on for upto one hour and shall automatically time out toturn the lights off.

2. Motion sensor controls on each display case orwalkin door section that reduce lighting powerby at least 50% within three minutes after thearea within the sensor range is vacated.

c. All low-temperature display cases shall incorporatetemperature-based defrost termination control witha timelimit default. The defrost cycle shall terminatefirst on an upper temperature limit breach andsecond upon a time limit breach.

d. Antisweat heater controls shall reduce the energy useof the antisweat heater as a function of the relativehumidity in the air outside the door or to the conden-sation on the inner glass pane. [ASHRAE90.1:6.4.6]

703.5 Prescriptive Path.703.5.1 Economizers. Each cooling system that has afan shall include either an air or water economizermeeting the requirements of Section 703.5.1.1 throughSection 703.5.1.4. [ASHRAE 90.1:6.5.1]Exceptions: Economizers are not required for thesystems listed below. (1) Individual fan-cooling units with a supply capacity

less than the minimum listed in Table 703.5.1(1) forcomfort cooling applications and Table 703.5.1(2)for computer room applications.

(2) Systems that include nonparticulate air treatment asrequired by Section 6.2.1 in ASHRAE 62.1.

(3) In hospitals and ambulatory surgery centers, wheremore than 75 percent of the air designed to besupplied by the system is to spaces that are requiredto be humidified above 35°F (2ºC) dew-pointtemperature to comply with applicable codes oraccreditation standards. In all other buildings, wheremore than 25 percent of the air designed to besupplied by the system is to spaces that are designedto be humidified above 35°F (2ºC) dew-pointtemperature to satisfy process needs. This exceptiondoes not apply to computer rooms.

(4) Systems that include a condenser heat recoverysystem with a minimum capacity as defined inSections 603.5.3.

(5) Systems that serve residential spaces where the




system capacity is less than five times the require-ment listed in Table 703.5.1(1).

(6) Systems that serve spaces whose sensible coolingload at design conditions, excluding transmissionand infiltration loads, is less than or equal to trans-mission and infiltration losses at an outdoor temper-ature of 60°F (16ºC).

(7) Systems expected to operate less than 20 hours perweek.

(8) Where the use of outdoor air for cooling will affectsupermarket open refrigerated casework systems.

(9) For comfort cooling where the cooling efficiencymeets or exceeds the efficiency requirements inTable 703.3.2703.5.1(3).

(10) Systems primarily serving computer rooms where:(a) The total design cooling load of all computer

rooms in the building is less than 3 000 000Btu/h (879 kW) and the building in which theyare located is not served by a centralized chilledwater plant, or

(b) The room total design cooling load is less than600 000 Btu/h (176 kW) and the building inwhich they are located is served by a central-ized chilled water plant, or

(c) The local water authority does not allowcooling towers, or

(d) Less than 600 000 Btu/h (176 kW) of computer

room cooling equipment capacity is beingadded to an existing building

(11) Dedicated systems for computer rooms where aminimum of 75 percent of the design load serves(a) Those spaces classified as an essential facility.(b) Those spaces having a mechanical cooling

design of Tier IV as defined by ANSI/TIA-942.(c) Those spaces classified under NFPA 70 Article

708 - Critical Operations Power Systems (COPS).(d) Those spaces where core clearing and settle-

ment services are performed such that theirfailure to settle pending financial transactionscould present systemic risk as described in “TheInteragency Paper on Sound Practices toStrengthen the Resilience of the US FinancialSystem, April 7, 2003.”

703.5.1.1 Air Economizers.703.5.1.1.1 Design Capacity. Air economizersystems shall be capable of modulating outdoorair and return air dampers to provide up to 100percent of the design supply air quantity asoutdoor air for cooling. [ASHRAE 90.1:6.5.1.1.1]703.5.1.1.2 Control Signal. Economizerdampers shall be capable of being sequencedwith the mechanical cooling equipment andshall not be controlled by only mixed airtemperature. [ASHRAE 90.1:6.5.1.1.2]Exception: The use of mixed air temperaturelimit control shall be permitted for systemscontrolled from space temperature (such assingle-zone systems).703.5.1.1.3 High-Limit Shutoff. All air econ-omizers shall be capable of automaticallyreducing outdoor air intake to the designminimum outdoor air quantity when outdoor airintake will no longer reduce cooling energyusage. High-limit shutoff control types andassociated setpoints for specific climates shallbe chosen from Table 703.5.1.1.3(1). High-limitshutoff control settings for these control typesshall be those listed in Table 703.5.1.1.3(2).[ASHRAE 90.1:6.5.1.1.3]703.5.1.1.4 Dampers. Both rReturn air,exhaust/relief, and outdoor air dampers shall meetthe requirements of Section 703.4.3.4. [ASHRAE90.1:6.5.1.1.4]703.5.1.1.5 Relief of Excess Outdoor Air.Systems shall provide a means to relieve excessoutdoor air during air economizer operation toprevent overpressurizing the building. The reliefair outlet shall be located to avoid recirculationinto the building. [ASHRAE 90.1:6.5.1.1.5]703.5.1.1.6 Sensor Accuracy. Outdoor air,return air, mixed air, and supply air sensors shallbe calibrated within the following accuracies:a. Dry-bulb and wet-bulb temperatures shall



TABLE 703.5.1.2.1 Water Economizer Sizing Dry-Bulb and Wet-Bulb Require-

ments for Computer Rooms [ASHRAE 90.1:6.5.1.2.1]

Zone Evaporative Water Economizer

Dry CoolerWater

Economizer Dry Bulb, °F Wet Bulb, °F Dry Bulb, °F

1 A NR NR

1 B NR NR

2 A 40.0 35.0 30.0

2 B 35.0 30.0 30.0

3 A 40.0 35.0 25.0

3 B 30.0 25.0 25.0

3 C 30.0 25.0 30.0

4 A 40.0 35.0 25.0

4 B 30.0 25.0 25.0

4 C 30.0 25.0 25.0

5 A 40.0 35.0 20.0

5 B 30.0 25.0 20.0

5 C 30.0 25.0 25.0

6 A 35.0 30.0 20.0

6 B 30.0 25.0 20.0

7 30.0 25.0 20.0

8 30.0 25.0 20.0


be accurate to ±2°F over the range of 40°Fto 80°F.

b. Enthalpy and the value of a differentialenthalpy sensor shall be accurate to ±3Btu/lb over the range of 20 to 36 Btu/lb.

c. Relative humidity shall be accurate to ±5%over the range of 20% to 80% RH.[ASHRAE 90.1:6.5.1.1.6]

703.5.1.2 Water Economizers.703.5.1.2.1 Design Capacity. Water econo-mizer systems shall be capable of coolingsupply air by indirect evaporation and providingup to 100 percent of the expected systemcooling load at outdoor air temperatures of 50°F(10ºC) dry bulb/ 45°F (7ºC) wet bulb andbelow. [ASHRAE 90.1:6.5.1.2.1]Exceptions: (1) Systems primarily serving computer rooms

in which 100 percent of the expectedsystem cooling load at 40°F (4ºC) the drybulb/35°F (2ºC) and wet bulb is met withevaporative water economizers listed inTable 703.5.1.2.1 is met with evaporativewater economizers.

(2) Systems primarily serving computer roomswith dry cooler water economizers inwhich satisfy 100 percent of the expectedsystem cooling load at 35°F (2ºC) the drybulb temperatures listed in Table

703.5.1.2.1 is met with dry cooler watereconomizers..

(3) Systems where dehumidification require-ments cannot be met using outdoor airtemperatures of 50°F (10ºC) dry bulb/45°F(7ºC) wet bulb and where 100 percent ofthe expected system cooling load at 45°F(7ºC) dry bulb/40°F (4ºC) wet bulb is metwith evaporative water economizers.

703.5.1.2.2 Maximum Pressure Drop.Precooling coils and water-to-water heatexchangers used as part of a water economizersystem shall either have a water-side pressuredrop of less than 15 feet of water (45 kPa) or asecondary loop shall be created so that the coilor heat exchanger pressure drop is not seen bythe circulating pumps when the system is in thenormal cooling (noneconomizer) mode.[ASHRAE 90.1:6.5.1.2.2]

703.5.1.3 Integrated Economizer Control.Economizer systems shall be integrated with the



DEVICE ADJUSTMENTCREDITS

Fully ducted return and/orexhaust air systems

0.5 in. w.c. (2.15 in w.c. for labo-ratory and vivarium systems)

Return and/or exhaust airflowcontrol devices

0.5 in. w.c.

Exhaust filters, scrubbers, orother exhaust treatment

The pressure drop of devicecalculated at fan system designcondition

Particulate Filtration Credit:MERV 9 through 12

0.5 in. w.c.

Particulate Filtration Credit:MERV 13 through 15

0.9 in. w.c.

Particulate Filtration Credit:MERV 16 and greater and elec-tronically enhanced filters

Pressure drop calculated at 2xclean filter pressure drop at fansystem design condition

Carbon and other gas-phase aircleaners

Clean filter pressure drop atfan system design condition

Biosafety cabinet Pressure drop of device at fansystem design condition

Energy Recovery Device, otherthan Coil Runaround Loop

(2.2 x Energy Recovery Effec-tiveness) - 0.5 in w.c. for eachairstream

Coil Runaround Loop 0.6 in. w.c. for each airstreamEvaporative humidifier/cooler inseries with another cooling coil

Pressure drop of device at fansystem design condition

Sound Attenuation Section 0.15 in. w.c.Exhaust system serving fumehoods

0.35 in. w.c.

Laboratory and vivarium exhaustsystems in high-rise buildings

0.25 in. w.c./100 ft of verticalduct exceeding 75 ft

For SI units: 1 inch water column = 0.249 kPa, 1 foot = 304.8 mm.

TABLE 703.5.3.1.1(2)FAN POWER LIMITATION PRESSURE DROP ADJUSTMENT

[ASHRAE 90.1: TABLE 6.5.3.1-2]

LIMIT CONSTANTVOLUME

VARIABLEVOLUME

Option 1: FanSystem MotorNameplate hp

AllowableNameplateMotor hp

hp ≤CFMS •0.0011

hp ≤CFMS •0.0015

Option 2: FanSystem bhp

Allowable FanSystem bhp

bhp ≤CFMS •0.00094 + A

bhp ≤CFMS •0.0013 + A

For SI units: 1 horsepower = 0.75 kW, 1 cubic foot per minute = 0.47 L/s* Where:

CFMS = the maximum design supply airflow rate to condi-tioned spaces served by the system in cubic feet per minute (0.47 L/s)

hp = the maximum combined motor nameplate horsepower

bhp = the maximum combined fan brake horsepower

A = sum of (PD x CFMD/4131)

Where:

PD = each applicable pressure drop adjustment from Table 703.5.3.1.1(2) in inch water column (0.249 kPa)

CFMD = the design airflow through each applicable device from Table 703.5.3.1.1(2) in cubic feet per minute (0.47 L/s)

TABLE 703.5.3.1.1(1)FAN POWER LIMITATION*

[ASHRAE 90.1: TABLE 6.5.3.1-1]


mechanical cooling system and be capable ofproviding partial cooling even when additionalmechanical cooling is required to meet the remainderof the cooling load.Controls shall not false load themechanical cooling systems by limiting or disablingthe economizer or by any other means, such as hotgas bypass, except at the lowest stage of mechanicalcooling.

Units that include an air econonizer shall complywith the following: .(1) Unit controls shall have the mechanical cooling

capacity control interlocked with the air econo-mizer controls such that the outdoor air damperis at the 100% open position when mechanicalcooling is on, and the outdoor air damper doesnot begin to close to prevent coil freezing dueto minimum compressor run time until theleaving air temperature is less than 45°F.

(2) DX units that control the capacity of themechanical cooling directly based on occupiedspace temperature shall have a minimum of twostages of mechanical cooling capacity per thefollowing effective dates:≥75 000 Btu/h Rated Capacity - Effetive1/1/2014≥65 000 Btu/h Rated Capacity - Effective1/1/2016 [ASHRAE 90.1:6.5.1.3]

703.5.1.4 Effective 1/1/2014, all other DX units,including those that control space temperature bymodulating the airflow to the space, shall complywith the requirements of Table 703.5.1.4. [ASHRAE90.1: 6.5.1.4]703.5.1.45 Economizer Heating SystemImpact. HVAC system design and economizercontrols shall be such that economizer operationdoes not increase the building heating energy useduring normal operation. [ASHRAE 90.1:6.5.1.45]Exception: Economizers on VAV systems that causezone level heating to increase due to a reduction insupply air temperature.703.5.1.6 Economizer HumidificationSystem Impact. Systems with hydronic oolingand humidifcation systems designed to maintaininside humidity at a dew-point temperature greatherthan 35°F shall use a water economizer if an econo-mizer is required by Section 703.5.2.1. [ASHRAE90.1: 6.5.1]

703.5.2 Simultaneous Heating and Cooling Limi-tation.

703.5.2.1 Zone Controls. Zone thermostaticcontrols shall prevent:(1) Reheating.(2) Recooling.(3) Mixing or simultaneously supplying air that has

been previously mechanically heated and airthat has been previously cooled, either by

mechanical cooling or by economizer systems.(4) Other simultaneous operation of heating and

cooling systems to the same zone. [ASHRAE90.1:6.5.2.1]

Exceptions:(1) Zones without DDC for which the volume of

air that is reheated, recooled, or mixed is lessthan the larger of the following:(a) 30 percent of the zone design peak supply

rate. (b) The outdoor airflow rate required to meet

the ventilation requirements of Section 6.2of ASHRAE Standard 62.1 for the zone.

(c) Any higher rate that can be demonstrated,to the satisfaction of the Authority HavingJurisdiction, to reduce overall systemannual energy usage by offsettingreheat/recool energy losses through a reduc-tion in outdoor air intake for the system.

(d) The air flow rate required to comply withapplicable codes or accreditation standards,such as pressure relationships or minimumair change rates.

(2) Zones with DDC that comply with all of thefollowing:(a) The air flow in dead band between heating

and cooling does not exceed the larger ofthe following:(i). 20 percent of the zone design peak

supply rate. (ii) The outdoor air flow rate required to

meet the ventilation requirements ofSection 6.2 of ASHRAE Standard 62.1for the zone.

(iii) Any higher rate that can be demon-strated, to the satisfaction of theAuthority Having Jurisdiction, toreduce overall system annual energyusage by offsetting reheat/recool



TABLE 703.5.1.4 DX Cooling Stage Requirements for

Modulating Airflow Units[ASHRAE 90.1:6.5.1.4]

Rating Capacity, Btu/h

Minimum Numberof Mechanical

Cooling Stages

MinimumCompressor

Displacementa

≥65,000 and <240,000 3 ≤35% of full load

≥240,000 4 ≤25% full load

a. For mechanical cooling stage control that does not use variablecompressor displacement the percent displacement shall be equivalent tothe mechanical cooling capacity reduction evaluated at the full load ratingconditions for the compressor.


energy losses through a reduction inoutdoor air intake.

(iv) The airflow rate required to complywith applicable codes or accreditationstandards, such as pressure relation-ships or minimum air change rates.

(b) The air flow rate that is reheated, recooled,or mixed in peak heating demand shall beless than 50 percent of the zone designpeak supply rate.

(c) Airflow between dead band and fullheating or full cooling shall be modulated.The first stage of heating consists of modu-lating the zone supply air temperaturesetpoint up to a maximum setpoint whilethe airflow is maintained at the dead bandflow rate.

(d) The second stage of heating consists ofmodulating the airflow rate from the deandband flow rate up to the heatingmaximum flow rate.

(3) Laboratory exhaust systems that comply with703.5.7.2.

(4) Zones where not less than 75 percent of theenergy for reheating or for providing warm air inmixing systems is provided from a site-recovered(including condenser heat) or site-solar energysource.703.5.2.1.1 Supply Air TemperatureReheat Limit .Where reheating is permittedby other parts of this supplement, zones thathave both supply and return/exhaust air open-ings greater than 6 feet (1829 mm) above floorshall not supply heating air more than 20°F (-7°C) above the space temperature setpoint. Exceptions:(1) Laboratory exhaust systems that complywith Section 703.5.7.2.

(2) During preoccupancy building warm-upand setback. [ASHRAE 90.1:6.5.2.1.1]

703.5.2.2 Hydronic System Controls. Theheating of fluids in hydronic systems that have beenpreviously mechanically cooled and the cooling offluids that have been previously mechanicallyheated shall be limited in accordance with Section703.5.2.2.1 through Section 703.5.2.2.3. [ASHRAE90.1:6.5.2.2]

703.5.2.2.1 Three-Pipe System. Hydronicsystems that use a common return system forboth hot water and chilled water shall not beused. [ASHRAE 90.1:6.5.2.2.1]703.5.2.2.2 Two-Pipe Changeover System.Systems that use a common distribution system tosupply both heated and chilled water are accept-able provided all of the following are met:(1) The system is designed to allow a dead

band between changeover from one modeto the other of at least 15°F (-9ºC) outdoorair temperature.

(2) The system is designed to operate and isprovided with controls that will allow oper-ation in one mode for not less than 4 hoursbefore changing over to the other mode.

(3) Reset controls are provided that allow heatingand cooling supply temperatures at thechangeover point to be no more than 30°F (-1.1ºC) apart. [ASHRAE 90.1:6.5.2.2.2]

703.5.2.2.3 Hydronic (Water Loop) HeatPump Systems. Hydronic heat pumpsconnected to a common heat pump water loopwith central devices for heat rejection (e.g.,cooling tower) and heat addition (e.g., boiler)shall have the following:(1) Controls that are capable of providing a

heat pump water supply temperature deadband of at least 20°F (-7ºC) between initi-ation of heat rejection and heat addition by



Operating Hours/Year ≤2000 Hours/Year >2000 and ≤ 4400 Hours/year >4400 Hours/Year

Nominal Pipe Size, in. Other Variable Flow/Variable Speed Other Variable Flow/

Variable Speed Other Variable Flow/ Variable Speed

2 1/2 120 180 85 130 68 1103 180 270 140 210 110 1704 350 530 260 400 210 3205 410 620 310 470 250 3706 740 1100 570 860 440 6808 1200 1800 900 1400 700 110010 1800 2700 1300 2000 1000 160012 2500 3800 1900 2900 1500 2300

Maximum Velocity forPipes over 12 14-24 in.

Size8.5 fps 13.0 fps 6.5 fps 9.5 fps 5.0 fps 7.5 fps

TABLE 703.5.4.5PIPING SYSTEM DESIGN MAXIMUM FLOW RATE IN GPM [ASHRAE 90.1: TABLE 6.5.4.56]


the central devices (e.g., tower and boiler).(2) For climate zone 3 through zone 8, if a

closed-circuit tower (fluid cooler) is used,either an automatic valve shall be installedto bypass all but a minimal flow of wateraround the tower (for freeze protection) orlow-leakage positive closure dampers shallbe provided. If an open-circuit tower is useddirectly in the heat pump loop, an automaticvalve shall be installed to bypass all heatpump water flow around the tower. If anopen-circuit tower is used in conjunctionwith a separate heat exchanger to isolate thetower from the heat pump loop, then heatloss shall be controlled by shutting down thecirculation pump on the cooling tower loop.[ASHRAE 90.1:6.5.2.2.3]

Exception: Where a system loop temperatureoptimization controller is used to determine themost efficient operating temperature based onreal-time conditions of demand and capacity,dead bands of less than 20°F (-7ºC) shall be

allowed.703.5.2.3 Dehumidification. Where humidistaticcontrols are provided, such controls shall preventreheating, mixing of hot and cold airstreams, orother means of simultaneous heating and cooling ofthe same airstream. [ASHRAE 90.1:6.5.2.3]Exceptions:(1) The system is capable of reducing supply air

volume to 50 percent or less of the designairflow rate or the minimum outdoor air venti-lation rate specified in ASHRAE Standard 62.1or other applicable federal, state, or local codeor recognized standard, whichever is larger,before simultaneous heating and cooling takesplace.

(2) The individual fan cooling unit has a designcooling capacity of 80 000 65 000 Btu/h (23.4kW) or less and is capable of unloading to 50percent capacity before simultaneous heatingand cooling takes place.

(3) The individual mechanical cooling unit has a



ZONE

% OUTDOOR AIR AT FULL DESIGN AIRFLOW RATE

≥10%and

<20%

≥20%and

<30%

≥30%and

<40%

≥40%and

<50%

≥50%and

<60%

≥60%and

<70%

≥70%and

<80%≥80%

DESIGN SUPPLY FAN AIRFLOW RATE (cfm)3C NR NR NR NR NR NR NR NR

1B, 2B, 3B, 4C, 5C NR ≥19 500 ≥9000 ≥5000 ≥4000 ≥3000 ≥1500 >01A, 2A, 3A, 4B, 5B ≥2500 ≥2000 ≥1000 ≥500 >0 >0 >0 >0

4A, 5A, 6A, 6B, 7, 8 >0 >0 >0 >0 >0 >0 >0 >0

TABLE 703.5.6.1(2)EXHAUST AIR ENERGY RECOVERY REQUIREMENTS FOR VENTILATION

SYSTEMS OPERATING GREATER THAN OR EQUAL TO 8000 HOURS PER YEAR[ASHRAE 90.1: TABLE 6.5.6.1-2]

NR—Not required

ZONE

% OUTDOOR AIR AT FULL DESIGN AIRFLOW RATE

≥10%and

<20%

≥20%and

<30%

≥30%and

<40%

≥40%and

<50%

≥50%and

<60%

≥60%and

<70%

≥70%and

<80%≥80%

DESIGN SUPPLY FAN AIRFLOW RATE (cfm)3B, 3C, 4B, 4C, 5B NR NR NR NR NR NR ≥5000 ≥5000

1B, 2B, 5C NR NR NR NR ≥26 000 ≥12 000 ≥5000 ≥40006B ≥28 000 ≥26 500 ≥11 000 ≥5500 ≥4500 ≥3500 ≥2500 ≥1500

1A, 2A, 3A, 4A, 5A,6A ≥26 000 ≥16 000 ≥5500 ≥4500 ≥3500 ≥2000 ≥1000 >0

7, 8 ≥4500 ≥4000 ≥2500 ≥1000 >0 >0 >0 >0

TABLE 703.5.6.1(1)EXHAUST AIR ENERGY RECOVERY REQUIREMENTS FOR VENTILATION

SYSTEMS OPERATING LESS THAN 8000 HOURS PER YEAR[ASHRAE 90.1: TABLE 6.5.6.1-1]

NR—Not required


design cooling capacity of 40 000 Btu/h (12.0kW) or less. An individual mechanical coolingunit is a single system composed of a fan or fansand a cooling coil capable of providing mechan-ical cooling.

(4) Systems serving spaces where specific humiditylevels are required to satisfy process needs, suchas vivariums, museums, surgical suites; phar-macies; and buildings with refrigeratingsystems, such as supermarkets, refrigeratedwarehouses, and ice arenas. and the buildingincludes site-recovered or site solar energysource that provide energy equal to at least 75percent of the annual energy for reheating or forproviding warm air in mixing systes. Thisexception does not apply to computer rooms.

(5) Not less than 75 percent of the energy forreheating or for providing warm air in mixingsystems is provided from a site-recovered(including condenser heat) or site-solar energysource.

(6) Systems where the heat added to the airstreamis the result of the use of a desiccant system and75 percent of the heat added by the desiccantsystem is removed by a heat exchanger, eitherbefore or after the desiccant system with energyrecovery.

703.5.2.4 Humidification. Systems with hydroniccooling and humidification systems designed tomaintain inside humidity at a dew-point temperaturegreater than 35°F (2ºC) shall use a water economizerif an economizer is required by Section 703.5.1.[ASHRAE 90.1:6.5.2.4]

703.5.2.4.1 Humidifiers with reheating jacketsmounted in the airstream shall be provided withan automatic valve to shut off preheat whenhumidification is not required.

703.5.2.4.2 Humidification system dispersiontube hote surfaces in the airstreams of ducts orair-handling units shall be insulated with aproduct with an insulating value of at lest R-0.5.Exception: Systems where mechanical cooling,including economizer operation, does not occursimultaneously with humidification.

703.5.2.5 Preheat Coils. Preheat coils shall havecontrols that stop their heat output whenevermechanical cooling, including economizer opera-tion, is occurring. [ASHRAE 90.1:6.5.2.5]

703.5.3 Air System Design and Control. EachHVAC system having a total fan system motor nameplatehorsepower (hp) exceeding 5 hp (4.0 kW) shall meet theprovisions of Section 703.5.3.1 through Section703.5.3.4. [ASHRAE 90.1:6.5.3]

703.5.3.1 Fan System Power Limitation.703.5.3.1.1 Each HVAC system at fan systemdesign conditions shall not exceed the allow-able fan system motor nameplate horsepower(Option 1) or fan system brake horsepower(Option 2) as shown in Table 703.5.3.1.1(1).This includes supply fans, return/relief fans,exhaust fans, and fan-powered terminal unitsassociated with systems providing heating orcooling capability. Single zone variable air-volume systems shall comply with the constantvolume fan power limitation. [ASHRAE90.1:6.5.3.1.1]Exceptions:(1) Hospital, vivarium and laboratory systems

that utilize flow control devices on exhaust,return or both to maintain space pressurerelationships necessary for occupant healthand safety or environmental control shalluse variable-volume fan power limitation.

(2) Individual exhaust fans with motor name-plate horsepower of 1 hp (0.75 kW) or less.

703.5.3.1.2 Motor Nameplate Horse-power. For each fan, the selected fan motorshall be no larger than the first available motorsize greater than the brake horsepower (bhp).The fan brake horsepower must be indicated onthe design documents to allow for complianceverification by the code official. [ASHRAE90.1:6.5.3.1.2]Exceptions:(1) For fans less than 6 bhp, where the first

available motor larger than the brake horse-power (bhp) has a nameplate rating within50 percent of the brake horsepower (bhp),the next larger nameplate motor size shallbe selected.

(2) For fans 6 bhp and larger, where the firstavailable motor larger than the brake horse-power (bhp) has a nameplate rating with 30



Type ofHood

Light DutyEquipment

MediumDuty

Equipment

HeavyDuty

Equipment

ExtraHeavy DutyEquipment

Wall-mountedcanopy

140 210 280 385

Singleisland 280 350 420 490

Doubleisland

(per side)175 210 280 385

Eyebrow 175 175 Notallowed

Not allowed

Backshelf/Pass-over 210 210 280 Not

allowed

TABLE 703.5.7.1.3MAXIMUM NET EXHAUST FLOW RATE, CFM PER

LINEAR FOOT OF HOOD LENGTH[ASHRAE 90.1: TABLE 6.5.7.1.3]


percent of the brake horsepower (bhp), thenext larger nameplate motor size shall beselected.

(3) Systems complying with Section703.5.3.1.1.

703.5.3.1.3 Fan Efficiency. Fans shall havea fan efficiency grade (FEG) of 67 or higherbased on manufacturers’ certified data, asdefined by AMCA 205. The total efficiency ofthe fan at the design point of operation shall bewithin 15 percentage points of the maximumtotal efficiency of the fan.Exceptions:1. Single fans with a motor nameplate horse-

power of 5 hp or less2. Multiple fans in series or parallel (e.g., fan

arrays) that have a combined motor name-plate horsepower of 5 hp or less and areoperated as the functional equivalent of asingle fan

3. Fans that are part of equipment listed underSection 6.4.1.1

4. Fans included in equipment bearing a third-party- certified seal for air or energyperformance of the equipment package

5. Powered wall/roof ventilators (PRV)6. Fans outside the scope of AMCA 2057. Fans that are intended to only operate

during emergency conditions. [ASHRAE6.5.3.1.3]

703.5.3.2 VAV Fan Control (IncludingSystems Using Series Fan Power Boxes).

703.5.3.2.1 Part-load Fan Airflow ControlPower Limitation. Individual VAV fans withmotors 10 hp (7.5 kW) and larger shall meet oneof Each cooling system listed in Table703.5.3.2.1 shall be designed to vary the indoorfan airflow as a function of load and shallcomply with the following requirements:(1) The fan shall be driven by a mechanical or

electrical variable-speed drive. DX andchilled-water cooling units that control thecapacity of the mechanical cooling directlybased on space temperature shall have aminimum of two stages of fan control. Lowor minimum speed shall not exceed 66

percent of full speed. At low or minimumspeed, the fan systems hall draw no morethan 40 percent of the fan power at full fanspeed. Low or minimum speed shall beused during periods of low cooling loadand ventilation-only operation.

(2) The fan shall be a vane-axial fan with vari-able-pitch blades. All other units, includingDX cooling units and chilled-water unitsthat control the space temperature bymodulating the airflow to the space, shallhave modulating fan control. Mimimumspeed shall not exceed 50 pers of fullspeed. At minimum speed, the fan systemshall draw no more than 30 percernt of thepower at full fan speed. Low or minimumspeed shall be used during periods of lowcooling load and ventilation-only oopera-tion.

(3) The fan shall have other controls anddevices that will result in fan motordemand of no more than 30 percent ofdesign wattage at 50 percent of design airvolume when static pressure setpointequals one-third of the total design staticpressure, based on manufacturers’ certifiedfan data.Units that include an air-side econ-omizer to meet the requirements of Section703.5.1 shall have a minimum of twospeeds of fan control during economizeroperation.Exceptions:(1) Modulating fan control is not required

for chilled-water and evporativecooling units with <1 hp fan motors ifthe units are not used to provide venti-lation air and the indoor fan cycleswith the load.

(2) If the volume of outdoor air requiredto meet the ventilation requirements ofStandard 62.1 at low speed exceedsthe air that would be delivered at thespeed defined in Setion 703.5.3.2 thenthe minimum speed shall be selectedto provide the required ventilation air.

Exceptions:1. Modulating fan control is not required

for chilled-water and evaporativecooling units with <1 hp fan motors ifthe units are not used to provide venti-lation air and the indoor fan cycleswith the load.

2. If the volume of outdoor air requiredto meet the ventilation requirements ofStandard 62.1 at low speed exceedsthe air that would be delivered at thespeed defined in Section



Rated Capacity Maximum Hot GasBypass Capacity

(percent of total capacity) ≤240,000 Btu/h 5015%>240,000 Btu/h 2510%

For SI units: 1000 British thermal units per hour = 0.293 kW

TABLE 703.5.9HOT GAS BYPASS LIMITATION

[ASHRAE 90.1: TABLE 6.5.9]


703.5.3.2.1(1) or 703.5.3.2.1(2) thenthe minimum speed shall be selectedto provide the required ventilation air.[ASHRAE 90.1:6.5.3.2.1]

703.5.3.2.2 VAV Static Pressure SensorLocation. Static pressure sensors used tocontrol VAV fans shall be placed in a position slocated such that the controller setpoint is nogreater than one-third the total design fan staticpressure, except for systems with zone resetcontrol complying with Section 703.5.3.2.3.1.2inch w.c. If this results in the sensor being locateddownstream of major duct splits, multiplesensors shall be installed in each major branch toensure that static pressure can be maintained ineach. [ASHRAE 90.1:6.5.3.2.2]703.5.3.2.3 VAV Setpoint Reset. Forsystems with DDC of individual zone boxesreporting to the central control panel, static pres-sure setpoint shall be reset based on the zonerequiring the most pressure; i.e., the setpoint isreset lower until one zone damper is nearly wideopen. Controls shall provide the following:(1) Monitor zone damper positions or other

indicator of need for static pressure. (2) Automatically detect those zones that may

be excessively driving the reset logic andgenerate an alarm to the system operator

(3) Readily allow operator removal ofzones(w) from the reset algorithm.[ASHRAE 90.1:6.5.3.2.3]

703.5.3.3 Multiple-zone VAV System Ventila-tion Optimization Control. Multiple-zone VAVsystems with DDC of individual zone boxesreporting to a central control panel shall includemeans to automatically reduce outdoor air intakeflow below design rates in response to changes insystem ventilation efficiency as defined byASHRAE Standard 62.1, Appendix A.Exceptions:(1) VAV systems with zonal transfer fans that recir-

culate air from other zones without directlymixing it with outdoor air, dual-duct dual-fanVAV systems, and VAV systems with fan-powered terminal units.

(2) Systems required to have the exhaust air energyrecovery complying with Section 703.5.6.1.

(3) Systems where total design exhaust airflow ismore than 70 percent of total design outdoor airintake flow requirements. [ASHRAE90.1:6.5.3.3]

703.5.3.4 Supply-Air Temperature ResetControls. Multiple zone HVAC systems mustinclude controls that automatically reset the supply-air temperature in response to representativebuilding loads, or to outdoor air temperature. The

controls shall reset the supply air temperature at least25 percent of the difference between the designsupply-air temperature and the design room airtemperature. Controls that adjust the reset based onzone humidity are allowed. Zones which areexpected to experience relatively constant loads,such as electronic equipment rooms, shall bedesigned for the fully reset supply temperature.[ASHRAE 90.1:6.5.3.4]Exceptions:(1) Climate zones 1a, 2a, and 3a.(2) Systems that prevent re-heating, re-cooling or

mixing of heated and cooled supply air.(3) Systems in which at least 75 percent of the

energy for reheating (on an annual basis) isfrom site recovered or site solar energy sources.

703.5.3.5 Fractional Horsepower FanMotors. Motors for fans that are 1/12 hp or greaterand less than 1 hp shall be electronically-commu-tated motors or shall have a minimum motor effi-ciency of 70% when rated in accordance with DOE10 CFR 431. These motors shall also have the meansto adjust motor speed for either balancing or remotecontrol. Beltdriven fans may use sheave adjustmentsfor airflow balancing in lieu of a varying motorspeed.Exceptions:1. Motors in the airstream within fan-coils and

terminal units that operate only when providingheating to the space served

2. Motors installed in space conditioning equip-ment certified under Section 6.4.1

3. Motors covered by Table 10.8-4 or 10.8-5.[ASHRAE 90.1:6.5.3.5]

703.5.4 Hydronic System Design and Control.[ASHRAE 90.1:6.5.4]

703.5.4.1 Boiler Turndown. Boiler systems withdesign input of at least 1 000 000 Btu/h shall complywith the turndown ratio specified in Table 703.5.4.1. The system turndown requirement shall be metthrough the use of multiple single-input boilers, oneor more modulating boilers, or a combination ofsingle-input and modulating boilers. All boilers shall meet the minimum efficiencyrequirement in Table 703.8.1(6). [ASHRAE90.1:6.5.4.1]703.5.4.12 Hydronic Variable Flow Systems.



TABLE 703.5.4.1 Boiler Turndown

[ASHRAE 90.1: 6.5.4.1]Boiler System Design Input, Btu/h Minimum Turndown Ratio

≥1,000,000 and ≤5,000,000 3 to 1>5,000,000 and ≤10,000,000 4 to 1

>10,000,000 5 to 1


HVAC pumping systems having a total pump systempower exceeding 10 hp (7.5 kW) that include controlvalves designed to modulate or step open and close asa function of load shall be designed for variable fluidflow and shall be capable of reducing pump flow ratesto 50 percent or less of the design flow rate. Individualchilled water pumps serving variable flow systemshaving motors exceeding 5 hp (4.0 kW) shall havecontrols, devices or both (such as variable speedcontrol) that will result in pump motor demand of nomore than 30 percent of design wattage at 50 percentof design water flow. The controls or devices shall becontrolled as a function of desired flow or to maintaina minimum required differential pressure. Differentialpressure shall be measured at or near the most remoteheat exchanger or the heat exchanger requiring thegreatest differential pressure. The differential pressuresetpoint shall be no more than one-hundred and tenpercent of that required to achieve design flow throughthe heat exchanger. Where differential pressure controlis used to comply with this section and DDC controlsare used the setpoint shall be reset downward basedon valve positions until one valve is nearly wide open.[ASHRAE 90.1:6.5.4.12]Exceptions:(1) Systems where the minimum flow is less than

the minimum flow required by the equipmentmanufacturer for the proper operation of equip-ment served by the system, such as chillers, andwhere total pump system power is 75 hp (56.0kW) or less.

(2) Systems that include no more than three controlvalves.

703.5.4.23 Pump Isolation Chiller and BoilerIsolation.703.5.4.3.1 When a chilled-water plant includesmore than one chiller, provisions shall be made sothat the all fluid flow in through the chiller plant canbe is automatically reduced, correspondingly, shutoff when a chiller is shut down. Chillers referred toin this section, piped in series for the purpose ofincreased temperature differential, shall be consid-ered as one chiller. Whrere constant-speed chilled-water or condenser water pumps are used to servemultiple chillers, the number of pumps shall be noless than the number of chillers and staged on andoff with chillers.703.5.4.3.2 When a boiler plant includes more thanone boiler, provisions shall be made so that the flowin through the boiler plant can be is automaticallyreduced, correspondingly, shut off when a boiler isshut down. Whrere constant-speed hot-water pumpsare used to serve multiple boilers, the number ofpumps shall be no less than the number of boilersand staged on and off with boilers. [ASHRAE90.1:6.5.4.23]703.5.4.3 Chilled- and Hot-Water Temperature

Reset Controls. Chilled- and hot-water systemswith a design capacity exceeding 300 000 Btu/h (88kW) supplying chilled or heated water (or both) tocomfort conditioning systems shall include controlsthat automatically reset supply water temperatures byrepresentative building loads (including return watertemperature) or by outdoor air temperature.[ASHRAE 90.1:6.5.4.34]Exceptions:(1) Where the supply temperature reset controls

cannot be implemented without causingimproper operation of heating, cooling, humid-ifying, or dehumidifying systems.

(2) Hydronic systems, such as those required bySection 703.5.4.1 that use variable flow toreduce pumping energy.

703.5.4.4 Hydronic (Water Loop) HeatPumps and Water-Cooled Unitary Air-Condi-tioners. [ASHRAE 90.1:6.5.4.45]

703.5.4.4.1 Each hydronic heat pump andwater-cooled unitary air-conditioner shall havea two-position automatic valve interlocked toshut off water flow when the compressor is off.[ASHRAE 90.1:6.5.4.45.1]Exception: Units employing water economizers.703.5.4.4.2 Hydronic heat pumps and water-cooled unitary air-conditioners having a totalpump system power exceeding 5 hp (4.0 kW)shall have controls, devices or both (such asvariable speed control) that will result in pumpmotor demand of not more than 30 percent ofdesign wattage at 50 percent of design waterflow. [ASHRAE 90.1: 6.5.4.45.2]

703.5.4.5 Pipe Sizing. All chilled-water andcondenser-water piping shall be designed such thatthe design flow rate in each pipe segment shall notexceed the values listed in Table 703.5.4.56 for theappropriate total annual hours of operation. Pipe sizeselections for systems that operate under variableflow conditions (e.g., modulating two-way controlvalves at coils) and that contain variable-speed pumpmotors are allowed to be made from the “VariableFlow/Variable Speed” columns. All others shall bemade from the “Other” columns. [ASHRAE 90.1:6.5.4.56]Exception:(1) Design flow rates exceeding the values in Table

703.5.4.56 are allowed in specific sections ofpipe if the pipe in question is not in the criticalcircuit at design conditions and is not predictedto be in the critical circuit during more than 30percent of operating hours.

(2) Piping systems that have equivalent or lowertotal pressure drop than the same systemconstructed with standard weight steel pipe withpiping and fittings sized per Table 703.5.4.56.




703.5.5 Heat Rejection Equipment.703.5.5.1 General. Section 703.5.5 applies to heatrejection equipment used in comfort cooling systemssuch as air-cooled condensers, dry coolers open-circuit cooling towers, closed-circuit cooling towers,and evaporative condensers. [ASHRAE90.1:6.5.5.1]Exception: Heat rejection devices whose energyusage is included in the equipment efficiency ratingslisted in Table 703.8.1(1) through Table 703.8.1(4).703.5.5.2 Fan Speed Control.

703.5.5.2.1 Each fan powered by a motor of7.5 hp (6.0 kW) or larger shall have the capa-bility to operate that fan at two-thirds of fullspeed or less and shall have controls that auto-matically change the fan speed to control theleaving fluid temperature or condensing temper-ature/pressure of the heat rejection device.[ASHRAE 90.1:6.5.5.2.1]Exceptions:(1) Condenser fans serving multiple refrigerant

circuits.(2) Condenser fans serving flooded

condensers.(3) Installations located in climate zone 1 and

zone 2.(4) Up to one-third of the fans on a condenser

or tower with multiple fans, where the leadfans comply with the speed control require-ment.

703.5.5.2.2 Multicell heat rejection equipmentwith variable-speed fan drives shall a. operate the maximum number of fans

allowed that comply with the manufac-turer’s requirements for all system compo-nents and

b. control all fans to the same fan speedrequired for the instantaneous cooling duty,as opposed to staged (on/off) operation.Minimum fan speed shall comply with theminimum allowable speed of the fan drivesystem per the manufacturer’s recommen-dations. [ASHRAE 90.1:6.5.5.2.2]

703.5.5.3 Limitation on Centrifugal FanOpen-Circuit Cooling Towers. Centrifugal fanopen-circuit cooling towers with a combined ratedcapacity of 1100 gallons per minute (gpm) (69.4 L/s)or greater at 95°F (35ºC) condenser water return, 85°F(29ºC) condenser water supply, and 75°F (24ºC)outdoor air wet-bulb temperature shall meet theenergy efficiency requirement for axial fan open-circuit cooling towers listed in Table 703.8.1(7).Exception: Open-circuit cooling towers that areducted (inlet or discharge) or require external soundattenuation. [ASHRAE 90.1:6.5.5.3]

703.5.5.4 Tower Flow Turndown. Open-circuitcooling towers used on water-cooled chiller systemsthat are configured with multiple- or variable-speedcondenser water pumps shall be designed so that allopen-circuit cooling tower cells can be run in parallelwith the larger ofa. the flow that is produced by the smallest pump at

its minimum expected flow rate orb. 50% of the design flow for the cell. [ASHRAE

90.1:6.5.5.4]703.5.6 Energy Recovery.

703.5.6.1 Exhaust Air Energy Recovery. Eachfan system shall have an energy recovery systemwhen the system’s supply air flow rate exceeds thevalue listed in Table 703.5.6.1 based on the climatezone and percentage of outdoor air flow rate atdesign conditions. Table 703.5.6.1(1) shall be usedfor all ventilation systems that operate less than 8000hours per year, and Table 703.5.6.1(2) shall be usedfor all ventilation systems that operate 8000 or morehours per year.

Energy recovery systems required by thissection shall have not less than 50 percent recoveryeffectiveness. Fifty percent energy recovery effec-tiveness shall mean a change in the enthalpy of theoutdoor air supply equal to 50 percent of the differ-ence between the outdoor air and return airenthalpies at design conditions. Provision shall bemade to bypass or control the energy recoverysystem to permit air economizer operation asrequired by Section 703.5.1.1. [ASHRAE90.1:6.5.6.1]Exceptions:(1) Laboratory systems meeting Section 703.5.7.2.(2) Systems serving spaces that are not cooled and

that are heated to less than 60°F (16ºC).(3) Systems exhausting toxic, flammable, paint,

corrosive fumes, or dust.(4) Commercial kitchen hoods used for collecting

and removing grease vapors and smoke.(5) Where more than 60 percent of the outdoor air

heating energy is provided from site-recoveredor site-solar energy.

(6) Heating energy recovery in climate zone 1 andzone 2.

(7) Cooling energy recovery in climate zones 3c,4c, 5b, 5c, 6b, 7, and 8.

(8) Where the largest source of air exhausted at asingle location at the building exterior is less than75 percent of the design outdoor air flow rate.

(9) Systems requiring dehumidification thatemploy energy recovery in series with thecooling coil.

(10) Systems expected to operate less than 20 hoursper week at the outdoor air percentage covered




by Table 703.5.6.1(1).703.5.6.2 Heat Recovery for Service WaterHeating.

703.5.6.2.1 Condenser heat recovery systemsshall be installed for heating or preheating ofservice hot water provided all of the followingare true:(1) The facility operates 24 hours a day.(2) The total installed heat rejection capacity

of the water-cooled systems exceeds 6 000000 Btu/h (1758 kW) of heat rejection.

(3) The design service water heating loadexceeds 1 000 000 Btu/h (293 kW).[ASHRAE 90.1:6.5.6.2.1]

703.5.6.2.2 The required heat recovery systemshall have the capacity to provide the smallerof:(1) 60 percent of the peak heat rejection load at

design conditions, or(2) Preheat of the peak service hot water draw

to 85ºF (30ºC).Exceptions: (1) Facilities that employ condenser heat

recovery for space heating with a heatrecovery design exceeding 30 percent ofthe peak water-cooled condenser load atdesign conditions.

(2) Facilities that provide 60 percent of theirservice water heating from site-solar orsite-recovered energy or from othersources. [ASHRAE 90.1:6.5.6.2.2]

703.5.7 Exhaust Systems.703.5.7.1 Kitchen Exhaust Systems.

703.5.7.1.1 Replacement air introduced directlyinto the hood cavity of kitchen exhaust hoodsshall not exceed 10 percent of the hood exhaustairflow rate. [ASHRAE 90.1:6.5.7.1.1]703.5.7.1.2 Conditioned supply air delivered toany space with a kitchen hood shall not exceedthe greater of:(1) The supply flow required to meet the space

heating or cooling load(2) The hood exhaust flow minus the available

transfer air from adjacent spaces. Availabletransfer air is that portion of outdoor venti-lation air not required to satisfy otherexhaust needs, such as restrooms, and notrequired to maintain pressurization of adja-cent spaces. [ASHRAE 90.1:6.5.7.1.2]

703.5.7.1.3 If a kitchen/dining facility has atotal kitchen hood exhaust airflow rate greaterthan 5000 ft3/min (2360 L/s) then each hoodshall have an exhaust rate that complies withTable 703.5.7.1.3. If a single hood, or hoodsection, is installed over appliances with different

duty ratings, then the maximum allowable flowrate for the hood or hood section shall not exceedthe Table 703.5.7.1.3 values for the highest appli-ance duty rating under the hood or hood section.Refer to ASHRAE Standard 154 for definitionsof hood type, appliance duty, and net exhaustflow rate. Exception: At least 75 percent of all thereplacement air is transfer air that would other-wise be exhausted. [ASHRAE 90.1:6.5.7.1.3]703.5.7.1.4 If a kitchen/dining facility has atotal kitchen hood exhaust airflow rate greaterthan 5000 ft3/min (2360 L/s) then it shall haveone of the following: (1) At least 50 percent of all replacement air is

transfer air that would otherwise beexhausted.

(2) Demand ventilation system(s) on at least75 percent of the exhaust air. Such systemsshall be capable of at least 50 percentreduction in exhaust and replacement airsystem airflow rates, including controlsnecessary to modulate airflow in responseto appliance operation and to maintain fullcapture and containment of smoke, effluentand combustion products during cookingand idle.

(3) Listed energy recovery devices with asensible heat recovery effectiveness of notless than 40 percent on at least 50 percentof the total exhaust airflow. [ASHRAE90.1:6.5.7.1.4]

703.5.7.1.5 Performance Testing. Anapproved field test method shall be used to eval-uate design air flow rates and demonstrateproper capture and containment performance ofinstalled commercial kitchen exhaust systems.Where demand ventilation systems are utilizedto meet Section 703.5.7.1.4, additional perform-ance testing shall be required to demonstrateproper capture and containment at minimumairflow. [ASHRAE 90.1:6.5.7.1.5]

703.5.7.2 Laboratory Exhaust Systems.Buildings with laboratory exhaust systems having atotal exhaust rate greater than 5000 ft3/min (2360L/s) shall include at least one of the followingfeatures:(1) VAV laboratory exhaust and room supply

systems capable of reducing exhaust andmakeup air flow rates and/or incorporate a heatrecovery system to precondition makeup airfrom laboratory exhaust that shall meet thefollowing:

A + Bx(E/M)≥50%




Where:A = Percentage that the exhaust and makeup air

flow rates can be reduced from design condi-tions.

B = Percentage sensible recovery effectivness.E = Exhaust airflow rate through the heat

recovery device at design conditions.M = Makeup air flow rate of the system at design

conditions.(2) VAV laboratory exhaust and room supply

systems that are required to have minimumcirculation rates to comply with code or accred-itation standards shall be capable of reducingzone exhaust and makeup air flow rates to theregulated minimum circulation values, or theminimum required to maintain pressurizationrelationship requirements. Non regulated zonesshall be capable of reducing exhaust andmakeup air flow rates to 50 percent of the zonedesign values, or the minimum required to main-tain pressurization relationship requirements.

(3) Direct makeup (auxiliary) air supply equal to atleast 75 percent of the exhaust rate, heated nowarmer than 2°F (-17ºC) below room setpoint,cooled to no cooler than 3°F (-16ºC) above roomsetpoint, no humidification added, and no simul-taneous heating and cooling used for dehumidi-fication control. [ASHRAE 90.1: 6.5.7.2]

703.5.7.3 Grease Removal Devices. Reserved.703.5.8 Radiant Heating Systems.

703.5.8.1 Heating Unenclosed Spaces. Radiantheating shall be used when heating is required forunenclosed spaces. [ASHRAE 90.1:6.5.8.1]Exception: Loading docks equipped with air curtains.703.5.8.2 Heating Enclosed Spaces. Radiantheating systems that are used as primary or supple-mental enclosed space heating must be in confor-mance with the governing provisions of thesupplement, including, but not limited to, thefollowing:(1) Radiant hydronic ceiling or floor panels (used

for heating or cooling).(2) Combination or hybrid systems incorporating

radiant heating (or cooling) panels.(3) Radiant heating (or cooling) panels used in

conjunction with other systems such as VAV orthermal storage systems. [ASHRAE90.1:6.5.8.2]

703.5.9 Hot Gas Bypass Limitation. Coolingsystems shall not use hot gas bypass or other evaporatorpressure control systems unless the system is designedwith multiple steps of unloading or continuous capacitymodulation. The capacity of the hot gas bypass shall belimited as indicated in Table 703.5.9 for VAV units andsing-zone VAV units. Hot gas bypass shall not be used

on constant-volume units. [ASHRAE 90.1:6.5.9]Exception: Unitary packaged systems with coolingcapacities not greater than 90 000 Btu/h (26.4 kW).703.5.10 Door Switches. Any conditioned space witha door, including doors with more than one-half glass,opening to the outdoors shall be provided with controlsthat, when any such door is open, a. disable mechanical heating or reset the heating

setpoint to 55°F or lower within five minutes of thedoor opening and

b. disable mechanical cooling or reset the coolingsetpoint to 90°F or greater within five minutes of thedoor opening. Mechanical cooling may remainenabled if outdoor air temperature is below spacetemperature.

Exceptions:1. Building entries with automatic closing devices2. Any space without a thermostat3. Alterations to existing buildings4. Loading docks [ASHRAE 90.1:6.5.10]

6.5.11 Refrigeration Systems. Refrigeration systemsthat are comprised of refrigerated display cases, walk-incoolers, or walk-in freezers connected to remotecompressors, remote condensers, or remote condensingunits shall meet the requirements of Sections 6.5.11.1through 6.5.11.2.Exception: Systems utilizing transcritical refrigerationcycle or ammonia refrigerant

703.5.11.1 Condensers Serving Refrigera-tion Systems. Fan-powered condensers shallconform to the following requirements:a. Design saturated condensing temperatures for

air-cooled condensers shall be less than or equalto the design drybulb temperature plus 10°F forlow-temperature refrigeration systems and lessthan or equal to the design drybulb temperatureplus 15°F for medium-temperature refrigerationsystems.1. Saturated condensing temperature for

blend refrigerants shall be determinedusing the average of liquid and vaportemperatures as converted from thecondenser drain pressure.

b. Condenser fan motors that are less than 1 hpshall use electronically commutated motors,permanent split capacitor-type motors, or three-phase motors.

c. All condenser fans for air-cooled condensers,evaporatively cooled condensers, and air- orwater-cooled fluid coolers or cooling towersshall incorporate one of the following contin-uous variable-speed fan-control approaches and




shall reduce fan motor demand to no more than30% of design wattage at 50% of design airvolume:1. Refrigeration system condenser control for

aircooled condensers shall use variablesetpoint control logic to reset thecondensing temperature setpoint inresponse to ambient dry-bulb temperature.

2. Refrigeration system condenser control forevaporatively cooled condensers shall usevariable setpoint control logic to reset thecondensing temperature setpoint inresponse to ambient wet-bulb temperature.

d. Multiple fan condensers shall be controlled inunison.

e. The minimum condensing temperature setpointshall be no greater than 70°F.

703.5.11.2 Compressor Systems. Refrigera-tion compressor systems shall conform to thefollowing requirements:a. Compressors and multiple-compressor systems

suction groups shall include control systemsthat use floating suction pressure control logicto reset the target suction pressure temperaturebased on the temperature requirements of theattached refrigeration display cases or walk-ins.

Exceptions:1. Single-compressor systems that do not have

variable capacity capability2. Suction groups that have a design saturated

suction temperature equal to or greater than30°F, suction groups that comprise the highstage of a two-stage or cascade system, orsuction groups that primarily serve chillers forsecondary cooling fluids.

b. Liquid subcooling shall be provided for all low-temperature compressor systems with a designcooling capacity equal to or greater than100,000 Btu/h with a design saturated suctiontemperature equal to or less than –10°F. Thesubcooled liquid temperature shall be controlledat a maximum temperature setpoint of 50°F atthe exit of the subcooler using eithercompressor economizer (interstage) ports or aseparate compressor suction group operating ata saturated suction temperature equal to orgreater than 18°F.1. Subcooled liquid lines are subject to the

insulation requirements of Table 6.8.3-2.c. All compressors that incorporate internal or

external crankcase heaters shall provide ameans to cycle the heaters off duringcompressor operation. [ASHRAE90.1:6.5.11.2]

703.6 Alternative Compliance Path (Not Used).[ASHRAE 90.1:6.6]703.7 Submittals.

703.7.1 General. The Authority Having Jurisdictionshall require submittal of compliance documentation andsupplemental information in accordance with Section703.7.1.1 through Section 703.7.1.3.

703.7.1.1 Construction Details. Compliancedocuments shall show all the pertinent data andfeatures of the building, equipment, and systems insufficient detail to permit a determination of compli-ance by the building official and to indicate compli-ance with the requirements of this supplement.[ASHRAE 90.1:4.2.2.1]703.7.1.2 Supplemental Information. Supple-mental information necessary to verify compliancewith this supplement, such as calculations, worksheets,compliance forms, vendor literature, or other data, shallbe made available when required by the AuthorityHaving Jurisdiction. [ASHRAE 90.1:4.2.2.2] 703.7.1.3 Manuals. Operating and maintenanceinformation shall be provided to the building owner.This information shall include, but not be limited to,the information specified Section 703.7.1.3.1 andSection 703.7.3.2. [ASHRAE 90.1:4.2.2.3]

703.7.1.3.1 Manuals Required Informa-tion. Construction documents shall require thatan operating manual and maintenance manualbe provided to the building owner. The manualsshall include, at a minimum, the following:(1) Submittal data stating equipment rating and

selected options for each piece of equip-ment requiring maintenance.

(2) Operation manuals and maintenance manualsfor each piece of equipment requiring main-tenance. Required routine maintenanceactions shall be clearly identified.

(3) Names and addresses of at least one quali-fied service agency.

(4) A complete narrative of how each system isintended to operate. [ASHRAE90.1:4.2.2.38.7.2]

703.7.2 Labeling of Material and Equipment.Materials and equipment shall be labeled in a mannerthat will allow for determination of their compliance withthe applicable provisions of this supplement. [ASHRAE90.1:4.2.3]703.7.3 Completion Requirements. The followingrequirements are mandatory provisions and are neces-sary for compliance with this supplement. [ASHRAE90.1:6.7.2]

703.7.3.1 Drawings. Construction documents shallrequire that, within 90 days after the date of systemacceptance, record drawings of the actual installationbe provided to the building owner or the designated




representative of the building owner. Record draw-ings shall include, as a minimum, the location andperformance data on each piece of equipment, generalconfiguration of duct and pipe distribution systemincluding sizes, and the terminal air or water designflow rates. [ASHRAE 90.1:6.7.2.1]703.7.3.2 Manuals. Construction documents shallrequire that an operating manual and a maintenancemanual be provided to the building owner or thedesignated representative of the building ownerwithin 90 days after the date of system acceptance.These manuals shall be in accordance with industry-accepted standards (see Informative Appendix E ofASHRAE 90.1) and shall include, at a minimum, thefollowing:(1) Submittal data stating equipment size and

selected options for each piece of equipmentrequiring maintenance.

(2) Operation manuals and maintenance manuals foreach piece of equipment requiring maintenance,except equipment not furnished as part of theproject. Required routine maintenance actionsshall be clearly identified.

(3) Names and addresses of at least one serviceagency.

(4) HVAC controls system maintenance and cali-bration information, including wiring diagrams,schematics, and control sequence descriptions.Desired or field-determined setpoints shall bepermanently recorded on control drawings atcontrol devices or, for digital control systems,in programming comments.

(5) A complete narrative of how each system isintended to operate, including suggestedsetpoints. [ASHRAE 90.1:6.7.2.2]

703.7.3.3 System Balancing.703.7.3.3.1 General. Construction docu-ments shall require that all HVAC systems bebalanced in accordance with generally acceptedengineering standards (see informativeAppendix E of ASHRAE 90.1). Constructiondocuments shall require that a written balancereport be provided to the building owner or thedesignated representative of the building ownerfor HVAC systems serving zones with a totalconditioned area exceeding 5000 ft2 (465.0 m2).[ASHRAE 90.1:6.7.2.3.1]703.7.3.3.2 Air System Balancing. Airsystems shall be balanced in a manner to firstminimize throttling losses. Then, for fans withfan system power greater than 1 hp (0.75 kW),fan speed shall be adjusted to meet design flowconditions. [ASHRAE 90.1:6.7.2.3.2]703.7.3.3.3 Hydronic System Balancing.Hydronic systems shall be proportionatelybalanced in a manner to first minimize throttling

losses; then the pump impeller shall be trimmedor pump speed shall be adjusted to meet designflow conditions. [ASHRAE 90.1:6.7.2.3.3]Exceptions: Impellers need not be trimmed norpump speed adjusted.(1) For pumps with pump motors of 10 hp (7.5

kW) or less.(2) When throttling results in no greater than 5

percent of the nameplate horsepower draw,or 3 hp (2.2 kW), whichever is greater, abovethat required if the impeller was trimmed.

703.7.3.4 System Commissioning. HVACcontrol systems shall be tested to ensure thatcontrol elements are calibrated, adjusted, and inproper working condition. For projects larger than50 000 ft2 (4645.2 m2) conditioned area, exceptwarehouses and semiheated spaces, detailedinstructions for commissioning HVAC systemsshall be provided by the designer in plans and spec-ifications. [ASHRAE 90.1:6.7.2.4]

703.7.3.4.1 Minimum Level of Commis-sion. Commissioning shall be performed forHVAC systems in accordance with Level 1,Basic Commissioning of the SMACNA HVACSystems Commissioning Manual. (SeeAppendix C for additional information onHVAC system commissioning).

703.8 Minimum Equipment Efficiency Tables.[ASHRAE 90.1:6.8]

703.8.1 Minimum Efficiency Requirement ListedEquipment—Standard Rating and OperatingConditions. [ASHRAE 90.1:6.8.1]703.8.2 Duct Insulation Tables. [ASHRAE 90.1:6.8.2]703.8.3 Pipe Insulation Tables. [ASHRAE 90.1:6.8.3]

704.0 Solar Energy Systems. Solar energy systems shallbe installed in accordance with the Uniform Solar EnergyCode.

705.0 Geothermal Systems.705.1 General. Geothermal systems that use the earth orbody of water as a heat source or sink for heating or coolingshall comply with Section 705.1.1 through Section 705.1.4.

705.1.1 Design, Installation and Testing. Geot-hermal systems shall be designed by a registered designprofessional. The geothermal system design, installationand testing shall comply with CSA C448, and the appli-cable requirements for hydronic piping systems of themechanical code. 705.1.2 Pipe Materials. Unless otherwise approvedby the Authority Having Jurisdiction, underground andsubmerged pipe used in geothermal systems shall bepolyethylene manufactured from resin compound PE




3408 or PE 4710 that complies with ASTM D3350 witha cell classification of 345564 or 345434. Pipe shallcomply with ASTM Standard D 3035 or CSA StandardB137.1. Polyethylene fittings shall comply with therequirements in ASTM D3261, ASTM D2683, ASTMF1055 or CSA Standard B137.1. Joints and connectionsof underground and submerged polyethylene piping shallbe heat fused or electrofused. All other pipe and fittingsshall comply with the applicable requirements forhydronic piping systems in the mechanical code.705.1.3 Marking. Geothermal piping systems shall haveuppercase lettering, with the words “GEOTHERMAL”or “GEO.” Additional, the piping shall not be markedwith the word “potable,” or the letters “P” or “PW.” 705.1.4 Heat Pump Approval. Water source heatpumps used in conjunction with geothermal heatexchangers shall be listed and labeled for use in suchsystems and shall be designed for the minimum andmaximum design water temperature.






EQUIPMENT TYPE SIZE CATEGORY HEATING SECTIONTYPE

SUBCATEGORY ORRATING

CONDITIONMINIMUM EFFICIENCY1 TEST PROCEDURE2

Air conditioners, air cooled <65 000 Btu/h3 All

Split System 13.0 SEER

AHRI 210/240

Single Package 13.0 SEER (before 1/1/2015)14 SEER (as of 1/1/2015)

Small duct high velocity, aircooled <65 000 Btu/h3 All Split System 11.0 SEER

Through-the-wall, aircooled ≤30 000 Btu/h3 All


Single Package 12.0 SEER

Air conditioners, air cooled

≥65 000 Btu/hand <135 000Btu/h

Electric resist-ance (or none)

Split system andsingle package

11.2 EER 11.4 IEER (before 1/1/2016)12.9 IEER (AS OF 1/1/2016)

AHRI340/360

All other Split system andsingle package

11.0 EER 11.2 IEER ()before 1/1/2016)12.7 IEER (as of 1/1/2016)

≥135 000 Btu/hand <240 000Btu/h



11.0 EER11.2 IEER (before 1/1/2016)12.4 IEER (as of 1/1/2016)


10.8 EER 11.0 IEER (before 1/1/2016)12.2 IEER (as of 1/1/2016)

≥240 000 Btu/hand <760 000Btu/h






≥760 000 Btu/h






TABLE 703.8.1(1)ELECTRONICALLY OPERATED UNITARY AIR CONDITIONERS AND CONDENSING UNITS –

MINIMUM EFFICIENCY REQUIREMENTS[ASHRAE 90.1: TABLE 6.8.1A]







Air conditioners, watercooled

<65 000 Btu/h All Split system andsingle package

12.1 EER12.3 IEER

AHRI210/240

≥65 000 Btu/hand <135 000Btu/h



11.5 EER (before 6/1/2011)12.1 EER (as of 6/1/2011)11.7 IEER (before 6/1/2011)12.3 IEER (as of 6/1/2011before 1/1/2016)13.9 IEER (as of 1/1/2016)

AHRI340/360


11.3 EER (before 6/1/2011)11.9 EER (as of 6/1/2011)11.5 IEER (before 6/1/2011)12.1 IEER (as of 6/1/2011before of 1/1/2016)13.9 IEER (as of 1/1/2016)

≥135 000 Btu/hand <240 000Btu/h

Electric Resist-ance (or none)


11.0 EER (before 6/1/2011)12.5 EER (as of 6/1/2011before 1/1/2016))11.2 IEER (before 6/1/2011)12.5 IEER (as of 6/1/2011before 1/1/2016)13.9 IEER (as of 1/1/2016)


10.8 EER (before 6/1/2011)12.3 EER (before 6/1/2011)11.0 IEER (before 6/1/2011)12.5 IEER (before 6/1/2011before 1/1/2016)13.7 IEER (as of 1/1/2016)

≥240 000 Btu/hand <760 000Btu/h



11.0 EER (before 6/1/2011)12.4 EER (as of 6/1/201111.1 IEER (before 6/1/2011)12.6 IEER (as of 6/1/2011before 1/1/2016)13.6 IEER (as of 1/1/2016)


10.8 EER (before 6/1/2011)12.2 EER (as of 6/1/2011)10.9 IEER (before 6/1/2011)12.4 IEER (as of 6/1/2011before 1/1/2016)13.4 IEER (as of 1/1/2016)

≥760 000 Btu/h



11.0 EER (before 6/1/2011)12.2 EER (as of 6/1/2011_11.1 IEER (before 6/1/2011)12.4 IEER (as of 6/1/2011before 1/1/2016)13.5 IEER (as of 1/1/2016)


10.8 EER (before 6/1/2011)12.0 EER (as of 6/1/2011_10.9 IEER (before 6/1/2011)12.2 IEER (as of 6/1/2011before 1/1/2016)13.3 IEER (as of 1/1/2016)

TABLE 703.8.1(1) (continued)ELECTRONICALLY OPERATED UNITARY AIR CONDITIONERS AND CONDENSING UNITS –








Air conditioners, evapora-tively cooled

<65 000 Btu/hc All Split system andsingle package

12.1 EER12.3 IEER

AHRI210/240

≥65 000 Btu/hand <135 000Btu/h



11.5 EER (before 6/1/2011)12.1 EER (as of 6/1/2011)11.7 IEER (before 6/1/2011)12.3 IEER (as of 6/1/2011)

AHRI 340/360All other Split system and

single package


≥135 000 Btu/hand <240 000Btu/h



11.0 EER (before 6/1/2011)12.0 EER (as of 6/1/2011_11.2 IEER (before 6/1/2011)12.2 IEER (as of 6/1/2011)



AHRI 340/360

≥240 000 Btu/hand <760 000Btu/h





10.8 EER (before 6/1/2011)12.2 11.7 EER (as of6/1/2011)10.9 IEER (before 6/1/2011)11.9 IEER (as of 6/1/2011)

≥760 000 Btu/h






Condensing units, air cooled ≥135 000 Btu/h – –

10.1 EER (before 6/1/2011)10.5 EER (as of 6//1/2011)11.4 IEER (before 6/1/2011)11.8 IEER (as of 6/1/2011)

AHRI365

Condensing units, watercooled ≥135 000 Btu/h – –


Condensing units, water orevaporatively cooled ≥135 000 Btu/h – –


For SI units: 1000 British thermal units per hour = 0.293 kW1 IPLVs and part-load rating conditions are only applicable to equipment with capacity modulation.2 Section 12 of ASHRAE 90.1 contains a complete specification of the referenced test procedure including the referenced year version of the test procedure. 3 Single-phase, air-cooled air conditioners <65 000 Btu/h (19.05 kW) are regulated by NAECA. SEER values are those set by NAECA.

TABLE 703.8.1(1) (continued)ELECTRONICALLY OPERATED UNITARY AIR CONDITIONERS AND CONDENSING UNITS –






SUBCATEGORYOR RATING CONDITION

MINIMUM EFFICIENCY1 TEST PROCEDURE2

Air cooled(cooling mode) <65 000 Btu/h3 All

Split System 13.0 SEER (before 1/1/2015)14 SEER (as of 1/1/2015)

AHRI210/240

Single Package 13.0 SEER (before 1/1/2015)14 SEER (as of 1/1/2015)

Through-the-wall (aircooled, cooling mode) ≤30 000 Btu/h3 All


Single Package 12.0 SEER

Small duct highvelocity, air cooled <65 000 btu/h3 All Split System 11.0 SEER

Air cooled(cooling mode)

≥65 000 Btu/h and<135 000 Btu/h

Electric resistance(or none)


11.0 EER 11.2 IEER (before 1/12016)12.2 IEER (as of 1/1/2016)

AHRI340/360



≥135 000 Btu/hand <240 000Btu/h






≥240 000 Btu/h






Water source to air,water loop (coolingmode)

<17 000 Btu/h All 86°F enteringwater 11.212.2 EER

ISO 13256-1

≥17 000 Btu/h and<65 000 Btu/h All 86°F entering

water 12.0 13.0 EER

≥65 000 Btu/h and<135 000 Btu/h All 86°F entering

water 12.0 13.0 EER

Water to air, Ground-water (cooling mode) <135 000 Btu/h All 59°F entering

water 16.2 18.0 EER

Brine to air, Groundsource loop (coolingmode)

<135 000 Btu/h All 77°F enteringwater 13.4 14.1 EER ISO 13256-1

Water-to-water, waterloop (cooling mode) <135 000 Btu/h All 86°F entering

water 10.6 EER

ISO 13256-2

Water to waterGroundwater (coolingmode)

<135 000 Btu/h All 59°F enteringwater 16.3 EER

Brine to water groundsource (cooling mode) <135 000 Btu/h All 77°F entering

water 12.1 EER

TABLE 703.8.1(2)ELECTRONICALLY OPERATED UNITARY AND APPLIED HEAT PUMPS—

MINIMUM EFFICIENCY REQUIREMENTS[ASHRAE 90.1: TABLE 6.8.1B]





SUBCATEGORYOR RATING CONDITION

MINIMUM EFFICIENCY1 TEST PROCEDURE2

Air cooled (heatingmode)

<65 000 Btu/h3

(cooling capacity)

– Split system 7.7 HSPF (before 1/1/2015)8.2 HSPF (as of 1/1/2015)

AHRI 210/240

– Single package 7.7 HSPF (before 1/1/2015)8.0 HSPF (as of 1/1/2015)

Through-the-wall, (aircooled, heating mode)

≤30 000 Btu/h3

(cooling capacity)

– Split system 7.4 HSPF

– Single package 7.4 HSPF Small duct highvelocity, air cooled(heating mode)

<65 000 Btu/h3 – Split system 6.8 HSPF

Air cooled(heating mode)

≥65 000 Btu/h and<135 000 Btu/h(cooling capacity)

–

47°F db/43°F wboutdoor air 3.3 COPH

AHRI 340/360


135 000 Btu/h(cooling capacity)

47°F db/43°F wboutdoor air 3.2 COPH17°F db/15°F wboutdoor air 2.05 COPH

Water source to air,water loop (heatingmode

<135 000 Btu/h(cooling capacity) – 68°F entering

water 4.23 COPH

ISO 13256-1

Water to air Ground-water source(heating mode)


water 3.67 COPH

Brine to air GroundSource loop (heatingmode)


water 3.12 COPH

Water sourcewater to water waterloop (heating mode)


water 3.7 COPH

Groundwater sourcewater to water ground-water (heating mode)


water 3.1 COPH

ISO 13256-2Brine to water Groundsource loop brine towater (heating mode)


water 2.5 COPH

For SI units: 1000 British thermal units per hour = 0.293 kW, t/ºC = (t/ºF-32)/1.81 IPLVs and part-load rating conditions are only applicable to equipment with capacity modulation.2 Section 12 of ASHRAE 90.1 contains a complete specification of the referenced test procedure including the referenced year version of the test procedure. 3 Single-phase air-cooled heat pumps <65 000 Btu/h (19.05 kW) are regulated by NAECA, SEER, and HSPF values are those set by NAECA.

TABLE 703.8.1(2) (continued)ELECTRONICALLY OPERATED UNITARY AND APPLIED HEAT PUMPS—

MINIMUM EFFICIENCY REQUIREMENTS[ASHRAE 90.1: TABLE 6.8.1B]




Effective 1/1/2010 Effective 1/1/2015

EQUIPMENT TYPE SIZECATEGORY UNITS PATH A PATH B PATH A PATH B

TESTPROCEDURE3

Air-Cooled Chillers

<150 tonsEER

(Btu/W)

≥9.562 FLNA4

≥10.100 FL ≥9.700 FL

AHRI 550/590

≥12.500 IPLV ≥13.700 IPLV ≥15.800 IPLV

≥150 tons≥9.562 FL

NA4≥10.100 FL ≥9.700 FL

≥12.750 IPLV ≥14.000 IPLV ≥16.100 IPLV

Air cooled, withoutcondenser, electrically oper-ated

All capacities EER(Btu/W)

Air-cooled chillers without condensers must be rated withmatching condensers and comply with the air-cooled chiller effi-

ciency requirements.

Water cooled, electricallyoperated, reciprocating All capacities kW/ton Reciprocating units must comply with water-cooled positive

displacement efficiency requirements.

Water cooled, electricallyoperated, positive displace-ment

<75 tons

kW/ton

≤0.780 FL ≤0.800 FL ≤0.750 FL ≤0.780 FL

≤0.630 IPLV ≤0.600 IPLV ≤0.600 IPLV ≤0.500 IPLV

≥75 tons and <150 tons≤0.775 FL ≤0.790 FL ≤0.720 FL ≤0.750 FL





≤0.540 IPLV ≤0.490 IPLV ≤0.520 IPL ≤0.410 IPLV

≥600 tons ≤0.620 FL ≤0.639 FL ≤0.560 FL ≤0.585 FL


Water cooled, electricallyoperated, centrifugal

<150 tons

kW/ton

≤0.634 FL ≤0.639 FL ≤0.610 FL ≤0.695 FL








≥600 tons≤0.570 FL ≤0.590 FL ≤0.560 FL ≤0.585 FL

≤0.539 IPLV ≤0.400 IPLV ≤0.500 IPLV ≤0.380 IPLVAir-cooled absorption singleeffect All capacities COP ≥0.600 FL NA4 ≥0.600 FL NA4

AHRI 560

Water-cooled absorptionsingle effect All capacities COP ≥0.700 FL NA4 ≥0.700 FL NA4

Absorption double effect,indirect-fired All capacities COP

≥1.000 FLNA4

≥1.000 FLNA4

≥1.050 IPLV ≥1.050 IPLV

Absorption double effectdirect-fired All capacities COP

≥1.000 FLNA4

≥1.000 FLNA4

≥1.000 IPLV ≥1.000 IPLV

For SI units: 1 ton = 1000 kg, t/ºC = (t/ºF-32)/1.81 The centrifugal chiller equipment requirements after shall be adjustedment per 703.4.1.2 do not apply to chillers where the design leaving evaporator

temperature is <36°F (2.2ºC) and are only applicable for the range of conditions listed here. The requirements do not apply to positive displacementchillers with design leaving fluid temperatures ≤32ºF (0ºC). The requirements do not apply to absorption chillers with design leaving fluid temperatures<40°F (4ºC). for air-cooled, water-cooled positive displacmeent and absorption chillers are at standard rating conditions defined in the reference testprocedure.

2 Compliance with this supplement can be obtained by meeting the minimum requirements of Path A or Path B. However, both the full load and IPLV mustbe met to fulfill the requirements of Path A or Path B.

3 Section 12 of ASHRAE 90.1 contains a complete specification of the referenced test procedure, including the referenced year version of the test procedure.4 NA means that this requirement is not applicable and cannot for path B, and only Path B can be used for compliance.5 NR means that there are no minimum requirements for this category FL is the full-load performance requirements, and IPLV is for the part-load perform-

ance requirements..

TABLE 703.8.1(3) WATER CHILLING PACKAGES—EFFICIENCY REQUIREMENTS1,2,5

[ASHRAE 90.1: TABLE 6.8.1C]




EQUIPMENT TYPE SIZE CATEGORY(INPUT)

SUBCATEGORY ORRATING CONDITION MINIMUM EFFICIENCY

TESTPROCEDURE1

PTAC (cooling mode) Standard Size All capacities 95°F db outdoor air

12.5 13.8 - (0.213 x Cap/ l 000)3

EER (before 10/8/2012 1/1/2015)13.8 14.0 - (0.300 x Cap/1000)3

EER (as of 1/1/2015)

ARI 310/380

PTAC (cooling mode) Nonstandard Size2 All capacities 95°F db outdoor air 10.9 - (0.213 x Cap/1000)3 EER

PTHP (cooling mode) Standard Size All capacities 95°F db outdoor air

12.3 - (0.213 x Cap/1000)3 EER (before 10/8/2012)14.0 - (0.300 x Cap/1000)3

EER (as of 10/8/2012)

PTHP (cooling mode) Nonstandard Size2 All capacities 95°F db outdoor air 10.8 - (0.213 x Cap/1000)3 EER

PTHP (heating mode) Standard Size All capacities -

3.2 - (0.026 x Cap/1000)3 COPH(before 10/8/2012)3.7 - (0.052 x Cap/1000)3

COPH (as of 10/8/2012)

PTHP (heating mode) Nonstandard Size2 All capacities - 2.9 - (0.026 x Cap/1000)3 COPH

SPVAC (cooling mode)

<65 000 Btu/h 95°F db/75°F wboutdoor air 9.0 10.0 EER

AHRI 390

≥65 000 Btu/h and<135 000 Btu/h

95°F db/75°F wboutdoor air 8.9 10.0 EER

≥135 000 Btu/h and<240 000 Btu/h


SPVHP (cooling mode)

<65 000 Btu/h 95°F db/75°F wboutdoor air 9.0 10.0 EER

≥65 000 Btu/h and<135 000 Btu/h


≥135 000 Btu/h and<240 000 Btu/h


SPVHP (heating mode)

<65 000 Btu/h 47°F db/43°F wboutdoor air 3.0 COPH

≥65 000 Btu/h and<135 000 Btu/h


≥135 000 Btu/h and<240 000 Btu/h

47°F db/43°F wboutdoor air 2.9 3.0 COPH

Room air conditioners, with louveredsides

<6000 Btu/h – 9.7 SEER ANSI/AHAMRAC-1

≥6000 Btu/h and<8000 Btu/h – 9.7 EER

≥8000 Btu/h and<14 000 Btu/h – 9.8 EER

≥14 000 Btu/h and<20,000 Btu/h – 9.7 SEER

≥20 000 Btu/h – 8.5 EER

SPVAC (cooling mode), nonweatherizedspace constrained

≤30 000 Btu/h 95°F db/75°F wboutdoor air 9.2 EER AHRI 390

>30 000 Btu/h and≤36 000 Btu/h

95°F db/75°F wboutdoor air 9.0 EER

TABLE 703.8.1(4)ELECTRICALLY OPERATED PACKAGED TERMINAL AIR CONDITIONERS, PACKAGED TERMINAL HEAT PUMPS, SINGLE-

PACKEDAGED VERTICAL AIR CONDITIONERS, SINGLE-PACKAGE VERTICAL HEAT PUMPS, ROOM AIR CONDITIONERS, ANDROOM AIR CONDITIONER HEAT PUMPS—MINIMUM EFFICIENCY REQUIREMENTS

[ASHRAE 90.1: TABLE 6.8.1D]




Room air conditioner, casement only All capacities – 8.7 EER ANSI/AHAMRAC-1Room air conditioner, casement-slider All capacities – 9.5 EER

For SI units: 1000 British thermal units per hour = 0.293 kW, t/ºC = (t/Fº-32)/1.81 Section 12 of ASHRAE 90.1 contains a complete specification of the referenced test procedure, including the referenced year version of the test procedure.2 Nonstandard Size units must be factory labeled as follows: "MANUFACTURED FOR NONSTANDARD SIZE APPLICATIONS ONLY; NOT TO BE

INSTALLED IN NEW STANDARD PROJECTS." Nonstandard size efficiencies apply only to units being installed in existing sleeves having an externalwall opening of less than 16 inch (406 mm) high or less than 42 inch (1067 mm) wide and having a cross-sectional area less than 670 square inches (0.432m2).

3 Cap means the rated cooling capacity of the product in Btu/h (kW). If the unit's capacity is less than 7000 Btu/h (2.05 kW). use 7000 Btu/h (2.05 kW) in thecalculation. If the unit's capacity is greater than 15 000 Btu/h (4.4 kW), use 15 000 Btu/h (4.4 kW) in the calculation.

TABLE 703.8.1(4) (continued)ELECTRICALLY OPERATED PACKAGED TERMINAL AIR CONDITIONERS, PACKAGED TERMINAL SINGLE-PACKED VERTICAL AIRCONDITIONERS, SINGLE-PACKAGE VERTICAL HEAT PUMPS, ROOM AIR CONDITIONERS, AND ROOM AIR CONDITIONER HEAT

PUMPS—MINIMUM EFFICIENCY REQUIREMENTS[ASHRAE 90.1: TABLE 6.8.1D]

EQUIPMENT TYPE SIZE CATEGORY(INPUT)

SUBCATEGORY ORRATING CONDITION MINIMUM EFFICIENCY

TESTPROCEDURE1

SPVHP (cooling mode), nonweatherizedspace constrained

30 000 Btu/h 95°F db/75°F wboutdoor air 9.2 EER

AHRI 390

>30 000 Btu/h and≤36 000 Btu/h

95°F db/75°F wboutdoor air 9.0 EER

SPVHP (heating mode), nonweatherizedspace constrained

≤30 000 Btu/h 47°F db/43°F wboutdoor air 3.0 COPH

>30 000 Btu/h and≤36 000 Btu/h


Room air conditioners, without louveredsides <8000 Btu/h – 9.0 EER

ANSI/AHAMRAC-1

≥8000 Btu/h and <20 000 Btu/h – 8.5 EER

≥20 000 Btu/h – 8.5 EER

Room air-conditioner heat pumps withlouvered sides

<20 000 Btu/h – 9.0 EER

≥20 000 Btu/h – 8.5 EER

Room air conditioner heat pumps withoutlouvered sides

<14 000 Btu/h – 8.5 EER

≥14 000 Btu/h – 8.0 EER




EQUIPMENT TYPE SIZE CATEGORY (INPUT) SUBCATEGORY OR RATINGCONDITION MINIMUM EFFICIENCY TEST PROCEDURE1

Warm-air furnace, gas-fired

<225 000 Btu/hMaximum capacity3

78% AFUE or 80% Et2, 4

DOE 10 CFR Part 430 orSection 2.39, Thermal Effi-ciency, of CSA Z21.47

≥225 000 Btu/h 80% Et4 Section 2.39, Thermal Effi-

ciency, of CSA Z21.47

Warm-air furnace, oil-fired<225 000 Btu/h

Maximum capacity378% AFUE or 80% Et

2, 4DOE 10 CFR Part 430 orSection 42, Combustion, ofUL 727

≥225 000 Btu/h 81% Et4 Section 42, Combustion,

UL 727Warm-air duct furnaces,gas-fired All capacities Maximum capacity3 80% Ec

5 Section 2.10, Efficiency, ofCSA Z83.8

Warm-air unit heaters, gas-fired All capacities Maximum capacity3 80% Ec

5, 6 Section 2.10, Efficiency, ofCSA Z83.8

Warm-air unit heaters, oil-fired All capacities Maximum capacity3 80% Ec

5, 6 Section 40, Combustion, ofUL 731

For SI units: 1000 British thermal units per hour = 0.293 kW.1 Section 12 of ASHRAE 90.1 contains a complete specification of the referenced test procedure, including the referenced year version of the test procedure.2 Combination units not covered by NAECA (three-phase power or cooling capacity greater than or equal to 65 000 Btu/h (19.05 kW) shall be permitted to

comply with either rating.3 Compliance of multiple firing rate units shall be at the maximum firing rate. 4 Et = thermal efficiency. Units must also include an interrupted or intermittent ignition device (IID), have jacket losses not exceeding 0.75 percent of the input

rating, and have either power venting or a flue damper. A vent damper is an acceptable alternative to a flue damper for those furnaces where combustion airis drawn from the conditioned space.

5 Ec = combustion efficiency (100 percent less flue losses). See test procedure for detailed discussion.6 As of August 8, 2008, according to the Energy Policy Act of 2005, units must also include an interrupted or intermittent ignition device (IID) and have either

power venting or an automatic flue damper.

TABLE 703.8.1(5)WARM-AIR FURNACES AND COMBINATION WARM-AIR FURNACES/AIR-CONDITIONING UNITS,

WARM-AIR DUCT FURNACES AND UNIT HEATERS[ASHRAE 90.1: TABLE 6.8.1E]




EQUIPMENT TYPE1 SUBCATEGORY ORRATING CONDITION

SIZE CATEGORY(INPUT)

MINIMUM EFFICIENCY2, 3

EFFICIENCY AS OF3/2/2010

(Date three yearsafter ASHRAE

Board Approval)

EFFICIENCY AS OF3/2/2020

(Date thirteen yearsafter ASHRAE

Board Approval)

TEST PROCEDURE

Boilers, hot water

Gas-fired

<300 000 Btu/h6,7 80% AFUE 80% AFUE 80% AFUE 10 CFR Part 430≥300 000 Btu/hand ≤2 500 000Btu/h4

75% Et 80% Et 80% Et 10 CFR Part 431

>2 500 000 Btu/h1 80% Ec 82% Ec 82% Ec

Oil-fired5

<300 000 Btu/h7 80% AFUE 80% AFUE 80% AFUE 10 CFR Part 430≥300 000 Btu/hand ≤2 500 000Btu/h4

78% Et 82% Et 82% Et 10 CFR Part 431

>2 500 000 Btu/h1 83% Ec 84% Ec 84% Ec

Boilers, steam

Gas-fired <300 000 Btu/h6 7580% AFUE 75% AFUE 7580% AFUE 10 CFR Part 430

Gas-fired – all,except naturaldraft

≥300 000 Btu/hand ≤2 500 000Btu/h4

75% Et 79% Et 79% Et

10 CFR Part 431>2 500 000 Btu/h1 80% Ec 79% Et 79% Et

Gas-fired – naturaldraft

≥300 000 Btu/hand ≤2 500 000Btu/h4

75% Et 77% Et 79% Et

>2 500 000 Btu/h1 80% Ec 77% Et 79% Et

Oil-fired5

<300 000 Btu/h 8082% AFUE 80% AFUE 8082% AFUE 10 CFR Part 430≥300 000 Btu/hand ≤2 500 000Btu/h4

78% Et 81% Et 81% Et 10 CFR Part 431

>2 500 000 Btu/h1 83% Ec 81% Et 81% EtFor SI units: 1000 British thermal units per hour = 0.293 kW.1 These requirements apply to boilers with rated input of 8 000 000 Btu/h (2344 kW) or less that are not packaged boilers and to all packaged boilers. Minimum

efficiency requirements for boilers cover all capacities of packaged boilers.2 Ec = combustion efficiency (100 percent less flue losses). See reference document for detailed information.3 Et = thermal efficiency. See reference document for detailed information.4 Maximum capacity – minimum and maximum ratings as provided for and allowed by the unit's controls.5 Includes oil-tired (residual).6 Boilers shall not be equipped with a constant burning pilot light. 7 A boiler not equipped with a tankless domestic water heating coil shall be equipped with an automatic means for adjusting the temperature of the water such

that an inremental change in inferred heat load produces a corresponding incremental change in the temperature of the water supplied.

TABLE 703.8.1(6)GAS- AND OIL-FIRED BOILERS, MINIMUM EFFICIENCY REQUIREMENTS

[ASHRAE 90.1: TABLE 6.8.1F]




EQUIPMENT TYPETOTAL SYSTEM HEATREJECTION CAPACITYAT RATED CONDITIONS

SUBCATEGORY OR RATING CONDITION8

PERFORMANCEREQUIRED1,2,3,4,6,7 TEST PROCEDURE4, 5

Propeller or axial fan open-circuit cooling towers All

95°F entering water85°F leaving water75°F entering wb

≥ 3840.2 gpm/hp CTI ATC-105 and CTI STD-201

Centrifugal fan open-circuitcooling towers All


≥ 20.0 gpm/hp CTI ATC-105 and CTI STD-201

Propeller or axial fan closed-circuit cooling towers All


≥14.0 gpm/hp CTI ATC-105S andCTI STD-201

Centrifugal fan closed-circuitcooling towers All

102°F entering water 90°F leaving water 75°F entering wb

≥7.0 gpm/hp CTI ATC-105S andCTI STD-201

Propeller or axial fan evapo-rartive condensers All

R-507A test fluid165°F entering gas temperature105°F condensing temperature75°F entering wb

≥157 000 Btu/h·hp CTI ATC-106

Propeller or axial fan evapo-rative condensers All

Ammonia test fluid140°F entering gas temperature96.3°F condensing temperature75°F entering wb


Centrifugal fan evaporativecondensers All

R-507A test fluid165°F entering gas temperature105°F condensing temperature75°F entering wb


Centrifugal fan evaporativecondensers All

Ammonia test fluid140°F entering gas temperature96.3°F condensing temperature75°F entering wb


Air-cooled condensers All

125°F condensing temperatureR-22 test fluid190°F entering gas temperature15°F subcooling 95°F entering db

≥176 000 Btu/h·hp AHRI 460

For SI units: t/ºC = (t/ºF-32)/1.8, 1 gallon per minute per horsepower = 0.085 L/s/kW, 1000 British thermal units per hour = 0.293 kW, 1 horsepower = 0.75kW.1 For purposes of this table, open-circuit cooling tower performance is defined as the water flow rating at the thermal rating condition listed in Table 703.8.1(7)

divided by the fan motor nameplate rating power.2 For purposes of this table, closed-circuit cooling tower performance is defined as the process water flow rating of the tower at the thermal rating condition

listed in Table 703.8.1(7) divided by the sum of the fan motor nameplate power and the integral spray pump motor nameplate power.3 For purposes of this table, air-cooled condenser performance is defined as the heat rejected from the refrigerant divided by the fan motor nameplate power. 4 Section 12 of ASHRAE 90.1 contains a complete specification of the referenced test procedure, including the referenced year version of the test procedure.5 The efficiencies and test procedures for both open- and closed-circuit cooling towers are not applicable to hybrid cooling towers that contain a combination

of separate wet and dry heat exchange sections. The certification requirements do not apply to field-erected cooling towers.6 All cooling towers shall comply with the minimum efficiency listed in the table fro that specific type of tower with the capacity effect of any project-specific

accessories and/or options inlcuded in the capacity of the cooling tower. 7 For purposes of this table, evaporative condenser performance is defined as the heat rejected at the specified rating condition in the table, divided by the sum

of the fan motor nameplate power and the integral spray pump nameplate power.8 Requirments for evaporative condensers are listed with ammonia (R-717) and R-507A as test fluids in the table. Evaporative condensers intended for use with

halocarbon refrigerants other than R-507A must meet the minimum efficiency requirements listed above with R-507A as the test fluid.

TABLE 703.8.1(7)PERFORMANCE REQUIREMENTS FOR HEAT REJECTION EQUIPMENT

[ASHRAE 90.1: TABLE 6.8.1G]




EQUIPMENT TYPE SUBCATEGORYMINIMUM

EFFICIENCY1TEST

PROCEDURE2

Liquid-to-liquid heat exchangers Plate type NR AHRI 400

1 NR = No Requirement2 Section 12 of ASHRAE 90.1 contains complete specification of the referenced test procedure, including the referenced year version of the test procedure.

TABLE 703.8.1(8)HEAT TRANSFER EQUIPMENT[ASHRAE 90.1: TABLE 6.8.1H]


SUB-CATEGORY ORRATING

CONDITIONMINIMUM EFFICIENCY TEST

PROCEDURE

VRF Air ConditionersAir Cooled

<65 000 Btu/h ALL VRF Multi-splitSystem 13.0 SEER

AHRI 1230

≥65 000 Btu/h and <135 000 Btu/h

Electric Resistance(or none)

VRF Multi-splitSystem

11.2 EER12.2 IEER13.1 IEER (as of 7/1/2012)

≥135 000 Btu/h and <240 000 Btu/h

Electric Resistance(or none)



≥240 000 Btu/h Electric Resistance(or none)



For SI units: 1000 British thermal units per hour = 0.293 kW.

TABLE 703.8.1(9)ELECTRICALLY OPERATED VARIABLE-REFRIGERANT-FLOW AIR CONDITIONERS—

MINIMUM EFFICIENCY REQUIREMENTS[ASHRAE 90.1: TABLE 6.8.1I]




EQUIPMENT TYPE SIZE CATEGORYHEATINGSECTION

TYPESUB-CATEGORY OR RATING CONDITION MINIMUM EFFICIENCY TEST

PROCEDURE

VRF Air Cooled,(cooling mode)

<65 000 Btu/h ALL VRF Multi-split System 13.0 SEER

AHRI 1230

≥65 000 Btu/h and <135 000 Btu/h

ElectricResistance(or none)

VRF Multi-split System11.0 EER12.3 IEER12.9 IEER (as of 7/1/2012)

≥65 000 Btu/h and <135 000 Btu/h


VRF Multi-split Systemwith Heat Recovery

10.8 EER12.1 IEER12.7 IEER (as of 7/1/2012

≥135 000 Btu/h and<240 000 Btu/h



≥135 000 Btu/h and<240 000 Btu/h




≥240 000 Btu/hElectricResistance(or none)


≥240 000 Btu/hElectricResistance(or none)



VRF Water Source(cooling mode)

<65 000 Btu/h ALL VRF Multi-split Systems86ºF entering water 12.0 EER

AHRI 1230

<65 000 Btu/h ALLVRF Multi-split Systemswith Heat Recovery 86ºFentering water

11.8 EER

≥65 000 Btu/h and <135 000 Btu/h ALL VRF Multi-split Systems

86ºF entering water 12.0 EER

≥65 000 Btu/h and <135 000 Btu/h ALL

VRF Multi-split Systemswith Heat Recovery 86ºFentering water

11.8 EER

≥135 000 Btu/h ALL VRF Multi-split Systems86ºF entering water 10.0 EER

≥135 000 Btu/h ALLVRF Multi-split Systemswith Heat Recovery 86ºFentering water

9.8 EER

VRF GroundwaterSource (cooling mode)

<135 000 Btu/h ALL VRF Multi-split System59ºF entering water 16.2 EER

AHRI 1230<135 000 Btu/h ALLVRF Multi-split Systemwith Heat Recovery 59ºFentering water

16.0 EER

≥135 000 Btu/h ALL VRF Multi-split System59ºF entering water 13.8 EER

TABLE 703.8.1(10)ELECTRICALLY OPERATED VARIABLE-REFRIGERANT-FLOW AIR-TO-AIR AND APPLIED HEAT PUMPS—

MINIMUM EFFICIENCY REQUIREMENTS[ASHRAE 90.1: TABLE 6.8.1J]




EQUIPMENT TYPE SIZE CATEGORYHEATINGSECTION

TYPESUB-CATEGORY OR RATING CONDITION MINIMUM EFFICIENCY TEST

PROCEDURE

VRF GroundwaterSource (cooling mode)

≥135 000 Btu/h ALLVRF Multi-split Systemwith Heat Recovery 59ºFentering water

13.6 EER

AHRI 1230

<135 000 Btu/h ALL VRF Multi-split System77ºF entering water 13.4 EER

<135 000 Btu/h ALLVRF Multi-split Systemwith Heat Recovery 77ºFentering water

13.2 EER

≥135 000 Btu/h ALL VRF Multi-split System77ºF entering water 11.0 EER

≥135 000 Btu/h ALLVRF Multi-split Systemwith Heat Recovery 77ºFentering water

10.8 EER

VRF Air Cooled(heating mode)

<65 000 Btu/h(cooling capacity) — VRF Multi-split System 7.7 HSPF

AHRI 1230≥65 000 Btu/h and<135 000 Btu/h —

VRF Multi-split System47ºF db/43ºF wb outdoor air 3.3 COPH

17ºF db/15ºF wb outdoor air 2.25 COPH

≥135 000 Btu/h(cooling capacity) —

VRF Multi-split System47ºF db/43ºF wb outdoor air 3.2 COPH

17ºF db/15ºF wb outdoor air 2.05 COPH

VRF Water Source(heating mode)

<135 000 Btu/h(cooling capacity) — VRF Multi-split System

68ºF entering water 4.2 COPHAHRI 1230

≥135 000 Btu/h(cooling capacity) — VRF Multi-split System

68ºF entering water 3.9 COPH

VRF GroundwaterSource (heating mode)





VRF Ground Source(heating mode)





TABLE 703.8.1(10) (continued)ELECTRICALLY OPERATED VARIABLE REFRIGERANT FLOW AIR-TO-AIR AND APPLIED HEAT PUMPS—

MINIMUM EFFICIENCY REQUIREMENTS[ASHRAE 90.1: TABLE 6.8.1J]

For SI units: 1000 British thermal units per hour = 0.293 kW.




EQUIPMENT TYPE NET SENSIBLE COOLING CAPACITY1MINIMUM

SCOP-1272 EFFICIENCY DOWN-FLOW UNITS/UPFLOW UNITS

TESTPROCEDURE

Air Conditioners, aircooled

<65 000 Btu/h≥65 000 Btu/h and < 240 000 Btu/h

≥240 000 Btu/h

2.20 / 2.092.10 / 1.991.90 / 1.79

ANSI/ASHRAE 127

Air Conditioners, watercooled

<65 000 Btu/h≥65 000 Btu/h and < 240 000 Btu/h

≥240 000 Btu/h

2.60 / 2.492.50 / 2.392.40 / 2.29

ANSI/ASHRAE 127

Air Conditioners, watercooled with fluid econo-

mizer

<65 000 Btu/h≥65 000 Btu/h and <240 000 Btu/h

≥240 000 Btu/h

2.55 / 2.442.45 / 2.342.35 / 2.24

ANSI/ASHRAE 127

Air Conditioners, glycolcooled (rated at 40%

propylene glycol)


≥240 000 Btu/h

2.50 / 2.392.15 / 2.042.10 / 1.99

ANSI/ASHRAE 127

Air Conditioners, glycolcooled (rated at 40%

propylene glycol) withfluid economizer


≥240 000 Btu/h

2.45 / 2.342.10 / 1.992.05 / 1.94

ANSI/ASHRAE 127

1 Net sensible cooling capacity: The total gross cooling capacity less the latent cooling less the energy to the air movement system. (Total Gross - latent -Fan Power)

2 Sensible coefficient of performance (SCOP-127): a ratio calculated by dividing the net sensible cooling capacity in watts by the total power input in watts(excluding re-heaters and humidifiers) at conditions defined in ASHRAE Standard 127. The net sensible cooling capacity is the gross sensible capacityminus the energy dissipated into the cooled space by the fan system.

TABLE 703.8.1(11)AIR CONDITIONERS AND CONDENSING UNITS SERVING COMPUTER ROOMS

[ASHRAE 90.1: TABLE 6.8.1K]

TABLE 703.8.1(12) Commercial Refrigerator and Freezers

[ASHRAE 90.1:6.8.1-12]Equipment Type Application Energy Use Limits, kWh/day Test Procedure

Refrigerator with solid doors

Holding temperature

0.10 × V + 2.04

AHRI 1200

Refrigerator with transparent doors 0.12 × V + 3.34Freezers with solid doors 0.40 × V + 1.38

Freezers with transparent doors 0.75 × V + 4.10Refrigerators/freezers with solid doors the greater of 0.12 × V + 3.34 or 0.70

Commercial refrigerators Pulldown 0.126 × V + 3.51V = the chiller or frozen compartment volume (ft3) as defined in Association of Home Appliance Manufacturers Standard HRF-1.




TABLE 703.8.1(13) Commercial Refrigeration—Minimum Efficiency Requirements

[ASHRAE 90.1:6.8.1-13]Equipment Type Energy Use Limits

as of 1/1/2012b,c,kWh/day

Test ProcedureEquipment

ClassaFamily Code Operating Mode Rating Temperature

VOP.RC.M Vertical open Remote condensing Medium temperature 0.82 × TDA + 4.07

AHRI 1200

SVO.RC.M Semivertical open Remote condensing Medium temperature 0.83 × TDA + 3.18HZO.RC.M Horizontal open Remote condensing Medium temperature 0.35 × TDA + 2.88VOP.RC.L Vertical open Remote condensing Low temperature 2.27 × TDA + 6.85HZO.RC.L Horizontal open Remote condensing Low temperature 0.57 × TDA + 6.88VCT.RC.M Vertical transparent door Remote condensing Medium temperature 0.22 × TDA + 1.95VCT.RC.L Vertical transparent door Remote condensing Low temperature 0.56 × TDA + 2.61SOC.RC.M Service over counter Remote condensing Medium temperature 0.51 × TDA + 0.11VOP.SC.M Vertical open Self contained Medium temperature 1.74 × TDA + 4.71SVO.SC.M Semivertical open Self contained Medium temperature 1.73 × TDA + 4.59HZO.SC.M Horizontal open Self contained Medium temperature 0.77 × TDA + 5.55HZO.SC.L Horizontal open Self contained Low temperature 1.92 × TDA + 7.08VCT.SC.I Vertical transparent door Self contained Ice cream 0.67 × TDA + 3.29VCS.SC.I Vertical solid door Self contained Ice cream 0.38 × V + 0.88HCT.SC.I Horizontal transparent door Self contained Ice cream 0.56 × TDA + 0.43SVO.RC.L Semivertical open Remote condensing Low temperature 2.27 × TDA + 6.85VOP.RC.I Vertical open Remote condensing Ice cream 2.89 × TDA + 8.7SVO.RC.I Semivertical open Remote condensing Ice cream 2.89 × TDA + 8.7HZO.RC.I Horizontal open Remote condensing Ice cream 0.72 × TDA + 8.74VCT.RC.I Vertical transparent door Remote condensing Ice cream 0.66 × TDA + 3.05

HCT.RC.M Horizontal transparent door Remote condensing Medium temperature 0.16 × TDA + 0.13HCT.RC.L Horizontal transparent door Remote condensing Low temperature 0.34 × TDA + 0.26HCT.RC.I Horizontal transparent door Remote condensing Ice cream 0.4 × TDA + 0.31

VCS.RC.M Vertical solid door Remote condensing Medium temperature 0.11 × V + 0.26VCS.RC.L Vertical solid door Remote condensing Low temperature 0.23 × V + 0.54VCS.RC.I Vertical solid door Remote condensing Ice cream 0.27 × V + 0.63

HCS.RC.M Horizontal solid door Remote condensing Medium temperature 0.11 × V + 0.26HCS.RC.L Horizontal solid door Remote condensing Low temperature 0.23 × V + 0.54HCS.RC.I Horizontal solid door Remote condensing Ice cream 0.27 × V + 0.63HCS.RC.I Horizontal solid door Remote condensing Ice cream 0.27 × V + 0.63SOC.RC.L Service over counter Remote condensing Low temperature 1.08 × TDA + 0.22SOC.RC.I Service over counter Remote condensing Ice cream 1.26 × TDA + 0.26VOP.SC.L Vertical open Self contained Low temperature 4.37 × TDA + 11.82VOP.SC.I Vertical open Self contained Ice cream 5.55 × TDA + 15.02SVO.SC.L Semivertical open Self contained Low temperature 4.34 × TDA + 11.51SVO.SC.I Semivertical open Self contained Ice cream 5.52 × TDA + 14.63HZO.SC.I Horizontal open Self contained Ice cream 2.44 × TDA + 9.0SOC.SC.I Service over counter Self contained Ice cream 1.76 × TDA + 0.36HCS.SC.I Horizontal solid door Self contained Ice cream 0.38 × V + 0.88

a. Equipment class designations consist of a combination (in sequential order separated by periods (AAA).(BB).(C)) of the following: (AAA)—An equip-ment family code (VOP = vertical open, SVO = semivertical open, HZO = horizontal open, VCT = vertical transparent doors, VCS = vertical solid doors,HCT = horizontal transparent doors, HCS = horizontal solid doors, and SOC = service over counter); (BB)—An operating mode code (RC = remotecondensing and SC = self contained); and (C)—A rating temperature code (M = medium temperature [38°F], L = lowtemperature [0°F], or I = ice creamtemperature [15°F]). For example, “VOP.RC.M” refers to the “vertical open, remote condensing, medium temperature” equipment class.

b. V is the volume of the case (ft) as measured in AHRI Standard 1200, Appendix C.

c. TDA is the total display area of the case (ft) as measured in AHRI Standard 1200, Appendix D.




CLIMATE ZONE

Duct Location

EXTERIOR VENTILATEDATTIC

UNVENTEDATTIC ABOVEINSULATED

CEILING

UNVENTEDATTIC WITH

ROOFINSULATION1

UNCONDI-TIONED SPACE2

INDIRECTLYCONDITIONED

SPACE3BURIED

HEATING ONLY DUCTS1, 2 none None none none none none none3 R-3.5 none none none none none none4 R-3.5 none none none none none none5 R-6 R-3.5 none none none none R-3.56 R-6 R-6 R-3.5 none none none R-3.57 R-8 R-6 R-6 none R-3.5 none R-3.58 R-8 R-8 R-6 none R-6 none R-6

COOLING ONLY DUCTS1 R-6 R-6 R-8 R-3.5 R-3.5 none R-3.52 R-6 R-6 R-6 R-3.5 R-3.5 none R-3.53 R-6 R-6 R-6 R-3.5 R-1.9 none none4 R-3.5 R-3.5 R-6 R-1.9 R-1.9 none none

5.6 R-3.5 R-1.9 R-3.5 R-l.9 R-1.9 none none7, 8 R-1.9 R- I .9 R-1.9 R-I.9 R-1.9 none none

RETURN DUCTS1 to 8 R-3.5 R-3.5 R-3.5 none none none none

1 Insulation R-values, measured in [Btu∙inch/(h∙ft2∙ºF)], are for the insulation as installed and do not include film resistance. The required minimum thick-nesses do not consider water vapor transmission and possible surface condensation. Where exterior walls are used as plenum walls. wall insulation shall beas required by the most restrictive condition of Section 703.4.4.2 or Section 5 of ASHRAE 90.1. Insulation resistance measured on a horizontal plane in accor-dance with ASTM C518 at a mean temperature of 75°F (24ºC) at the installed thickness.

2 Includes crawlspaces, both ventilated and nonventilated.3 Includes return air plenum, with of without exposed roofs above.

TABLE 703.8.2(1)MINIMUM DUCT INSULATION R-VALUE1, COOLING AND HEATING ONLY SUPPLY DUCTS AND RETURN DUCTS

[ASHRAE 90.1: TABLE 6.8.2A]




CLIMATE ZONE

DUCT LOCATION

EXTERIOR VENTILATEDATTIC

UNVENTED ATTICABOVE

INSULATEDCEILING

UNVENTEDATTIC WITH

ROOFINSULATION1

UNCONDITIONEDSPACE2

INDIRECTLYCONDITIONED

SPACE3BURIED

SUPPLY DUCTS1 R-6 R-6 R-8 R-3.5 R-3.5 none R-3.52 R-6 R-6 R-6 R-3.5 R-3.5 none R-3.53 R-6 R-6 R-6 R-3.5 R-3.5 none R-3.54 R-6 R-6 R-6 R-3.5 R-3.5 none R-3.55 R-6 R-6 R-6 R-1.9 R-3.5 none R-3.56 R-8 R-6 R-6 R-1.9 R-3.5 none R-3.57 R-8 R-6 R-6 R-1.9 R-3.5 none R-3.58 R-8 R-8 R-8 R-1.9 R-6 none R-6

RETURN DUCTS1 to 8 R-3.5 R-3.5 R-3.5 none none none none

TABLE 703.8.2(2)MINIMUM DUCT INSULATION R-VALUE1,

COMBINED HEATING AND COOLING SUPPLY DUCTS AND RETURN DUCTS[ASHRAE 90.1: TABLE 6.8.2B]

1 Insulation R-values measured in [Btu∙inch/(h∙ft2∙ºF)], are for the insulation as installed and do not include film resistance. The required minimum thicknessesdo not consider water vapor transmission and possible surface condensation. Where exterior walls are used as plenum walls, wall insulation shall be asrequired by the most restrictive condition of Section 703.4.4.2 or Section 5 of ASHRAE 90.1. Insulation resistance measured on it horizontal plane in accor-dance with ASTM C518 at a mean temperature of 75ºF (24ºC) at the installed thickness.

2 Includes crawlspaces, both ventilated and nonventilated.3 Includes return air plenums wilt or without exposed roofs above.




INSULATION CONDUCTIVITY NOMINAL PIPE SIZE OR TUBE SIZE (inches)FLUID OPERATING

TEMPERATURE RANGE (ºF)AND USAGE

CONDUCTIVITYBtu•inch/(h•ft2•°F)

Mean Rating Temperature°F <1 1 to <1-1/2 1-1/2 to <4 4 to <8 ≥8

INSULATION THICKNESS (inches)

40ºF - 60ºF 021 - 0.27 75 0.5 0.5 1.0 1.0 1.0<40ºF 0.20 - 0.26 50 0.5 1.0 1.0 1.0 1.5

For SI units: t/ºC=(t/ºF-32)/1.8, 1 inch = 25 mm, 1 British thermal unit = 1055 J.1 For insulation outside the stated conductivity range, the minimum thickness (T) shall be determined as follows: T = r{(1 + t/r)K/k – 1}

Where:T = minimum insulation thickness (inches).r = actual outside radius of pipe (inches).t = insulation thickness listed in this table for applicable fluid temperature and pipe size.K = conductivity of alternate material at mean rating temperature indicated for the applicable fluid temperature [Btu∙inch/(h∙ft2∙ºF)].k = the upper value of the conductivity range listed in this table for the applicable fluid temperature.

2 These thicknesses are based on energy efficiency considerations only. Issues such as water, vapor permeability or surface condensation sometimes requirevapor retarders or additional insulation.

3 For direct-buried cooling system piping, insulation is not required.4 The table is based on steel pipe. Non-metallic pipes schedule 80 thickness or less shall use the table values. For other non-metallic pipes having thermal resist-

ance greater than that of steel pipe, reduced insulation thicknesses are permitted if documentation is provided showing that the pipe with the proposed insula-tion has no more heat transfer per foot than a steel pipe of the same size with the insulation thickness shown in the table.

TABLE 703.8.3BMINIMUM PIPE INSULATION THICKNESS

COOLINGSYSTEMS (CHILLED WATER, BRINE, AND REFRIGERANT)1,2,3

[ASHRAE 90.1: TABLE 6.8.3B]

INSULATION CONDUCTIVITY NOMINAL PIPE SIZE OR TUBE SIZE (inches)FLUID OPERATING

TEMPERATURE RANGE (ºF)AND USAGE

CONDUCTIVITYBtu•inch/(h•ft2•°F)

Mean Rating Temperature°F <1 1 to <1-1/2 1-1/2 to <4 4 to <8 ≥8

INSULATION THICKNESS (inches)

>350ºF 0.32 - 0.34 250 4.5 5.0 5.0 5.0 5.0251ºF - 350ºF 0.29 - 0.32 200 3.0 4.0 4.5 4.5 4.5201ºF - 250ºF 0.27 - 0.30 150 2.5 2.5 2.5 3.0 3.0141ºF -200ºF 0.25 - 0.29 125 1.5 1.5 2.0 2.0 2.0105ºF - 140ºF 0.22 - 0.28 100 1.0 1.0 1.5 1.5 1.5

For SI units: t/ºC=(t/ºF-32)/1.8, 1 inch = 25 mm, 1 British thermal unit = 1055 J.1 For insulation outside the stated conductivity range, the minimum thickness (T) shall be determined as follows: T = r{(1 + t/r)K/k – 1}

Where:T = minimum insulation thickness (inches).r = actual outside radius of pipe (inches).t = insulation thickness listed in this table for applicable fluid temperature and pipe size.K = conductivity of alternate material at mean rating temperature indicated for the applicable fluid temperature [Btu∙inch/(h∙ft2∙ºF)].k = the upper value of the conductivity range listed in this table for the applicable fluid temperature.

2 These thicknesses are based on energy efficiency considerations only. Additional insulation is sometimes required relative to safety issues/surface temperature.3 For piping smaller than 1 1/2 inches (38 mm) and located in partitions within conditioned spaces, reduction of these thicknesses by 1 inch shall be permitted

(before thickness adjustment required in footnote 1) but not to thicknesses below 1 inch (25 mm).4 For direct-buried heating and hot water system piping, reduction of these thicknesses by 1 1/2 inch (38 mm) shall be permitted (before thickness adjustment

required in footnote 1) but not to thicknesses below 1 inch (25 mm).5 The table is based on steel pipe. Non-metallic pipes schedule 80 thickness or less shall use the table values. For other non-metallic pipes having thermal resist-

ance greater than that of steel pipe, reduced insulation thicknesses are permitted if documentation is provided showing that the pipe with the proposed insula-tion has no more heat transfer per foot than a steel pipe of the same size with the insulation thickness shown in the table.

TABLE 703.8.3AMINIMUM PIPE INSULATION THICKNESS

HEATING AND HOT WATER SYSTEMS1,2,3,4

(STEAM, STEAM CONDENSATE, HOT WATER HEATING AND DOMESTIC WATER SYSTEMS)[ASHRAE 90.1: TABLE 6.8.3A]


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