CODES

ADOPTS WITH AMENDMENTS:

2018 Uniform Mechanical Code

Heads up: There are no suggested sections in this chapter.
Heads up: There are no amended sections in this chapter.
The provisions contained in this appendix are not mandatory unless specifically adopted by a state agency, or referenced in the adopting ordinance.

CALIFORNIA MECHANICAL CODE - MATRIX ADOPTION TABLE
APPENDIX E - SUSTAINABLE PRACTICES
(Matrix Adoption Tables are non-regulatory, intended only as an aid to the code user. See Chapter 1 for state agency authority and building applications.)
Adopting agency BSC BSC-CG SFM HCD DSA OSHPD BSCC DPH AGR DWR CEC CA SL SLC
1 2 1-AC AC SS SS/CC 1 1R 2 3 4 5
Adopt entire chapter
Adopt entire chapter as
amended (amended
sections listed below)
Adopt only those sections
that are listed below
Chapter / Section
This state agency does not adopt sections identified with the following symbol:
The Office of the State Fire Marshal's adoption of this chapter or individual sections is applicable to structures regulated by other state agencies pursuant to Section 1.11.0.
The purpose of this appendix is to provide a comprehensive set of technically sound provisions that encourage sustainable practices and works towards enhancing the design and construction of mechanical systems that result in a positive long-term environmental impact. This appendix is not intended to circumvent the health, safety, and general welfare requirements of this code.
For the purposes of this code, the definitions shall apply to this appendix.

     No attempt is made to define ordinary words, which are used in accordance with their established dictionary meanings, except where a word has been used loosely, and it is necessary to define its meaning as used in this appendix to avoid misunderstanding.

     The definitions of terms are arranged alphabetically according to the first word of the term.
Cycles of concentration equals the specific conductance of the water in the cooling tower basin divided by the combined flow-weighted average specific conductance of the makeup water(s) to the cooling tower.
Includes pipe, tubing, rods, and wire. Screws and other fasteners are not considered to be ductwork penetrations.
A joint program of the U.S. Environmental Protection Agency and the U.S. Department of Energy. Energy Star is a voluntary program designed to identify and promote energy-efficient products and practices.
Renewable energy generated by deep-earth.
The total heating output of a heat pump during its normal annual usage period for heating in British thermal units (Btu) (kW•h) divided by the total electric energy input during the same period. [ASHRAE 90.1:3.2]
A single-number figure of merit expressing cooling part-load EER efficiency for commercial unitary air-conditioning and heat pump equipment on the basis of weighted operation at various load capacities for the equipment. [ASHRAE 90.1:3.2]
A single-number figure of merit based on part-load EER, COP, or kW/ton expressing part-load efficiency for air-conditioning and heat pump equipment on the basis of weighted operation at various load capacities for the equipment. [ASHRAE 90.1:3.2]
Connections of two duct sections oriented perpendicular to airflow.
The upkeep of property or equipment by the owner of the property in accordance with the requirements of this appendix.
Filter minimum efficiency reporting value, in accordance with ASHRAE 52.2.
Indoor spaces used for presentations and training, including classrooms and conference rooms.
A system of hot water supply and return piping with shutoff valves, balancing valves, circulating pumps, and a method of controlling the circulating system.
Joints oriented in the direction of airflow.
The total cooling output of an air conditioner during its normal annual usage period for cooling in Btu (kW•h) divided by the total electric energy input during the same period in Btu (kW•h). [ASHRAE 90.1:3.2]
Mechanical systems covered by this appendix shall be installed in accordance with this code, other applicable codes, and the manufacturer's installation and operating instructions.
Where permits are required, the Authority Having Jurisdiction shall have the authority to require contractors, installers, or service technicians to demonstrate competency. Where determined by the Authority Having Jurisdiction, the contractor, installer or service technician shall be licensed to perform such work.
It shall be unlawful for a person to cause, suffer, or permit the disposal of liquid wastes, in a place or manner, except through and by means of an approved drainage system, installed and maintained in accordance with the provisions of the plumbing code.
Equipment and appliances, used to receive or discharge liquid wastes or sewage, shall be connected to the drainage system of the building or premises in accordance with the requirements of the plumbing code and this appendix.
An abandoned system or part thereof covered under the scope of this appendix shall be disconnected from remaining systems, drained, plugged, and capped in an approved manner.
The provisions of this section establish the means of conserving potable and nonpotable water used in and around a building.
A water meter shall be required for buildings connected to a public water system, including municipally supplied reclaimed (recycled) water. In other than single-family houses, multi-family structures not exceeding three stories above grade, and modular houses, a separate meter or submeter shall be installed in the following locations:
  1. The makeup water supply to cooling towers, evaporative condensers, and fluid coolers.
  2. The makeup water supply to one or more boilers collectively exceeding 1000000 British thermal units per hour (Btu/h) (293 kW).
  3. The water supply to a water-using process where the consumption exceeds 1000 gallons per day (gal/d) (0.0438 L/s), except for manufacturing processes.
  4. The makeup water supply to an evaporative cooler having an air flow exceeding 30000 cubic feet per minute (ft3/min) (14.1584 m3/s).
A means of communicating water consumption data from submeters to the water consumer shall be provided.
Meters and submeters shall be accessible.
Once-through cooling using potable water is prohibited.
Cooling towers and evaporative coolers shall be equipped with makeup water and blow down meters, conductivity controllers, and overflow alarms. Cooling towers shall be equipped with efficiency drift eliminators that achieve drift reduction to 0.002 percent of the circulated water volume for counterflow towers and 0.005 percent for cross-flow towers.
Not less than 5 cycles of concentration is required for air-conditioning cooling tower makeup water having a total hardness of less than 11 grains per gallon (gr/gal) (188 mg/L) expressed as calcium carbonate. Not less than 3.5 cycles of concentration is required for air-conditioning cooling tower makeup water having a total hardness equal to or exceeding 11 gr/gal (188 mg/L) expressed as calcium carbonate.

Exception: Air-conditioning cooling tower makeup water having discharge conductivity range not less than 7 gr/gal (120 mg/L) to 9 gr/gal (154 mg/L) of silica measured as silicon dioxide.
Evaporative cooling systems shall use 3.5 gallons (13.2 L) or less of water per ton-hour (kW•h) of cooling where system controls are set to maximum water use. Water use expressed in maximum water use per ton-hour (kW•h) of cooling, shall be marked on the device and included in the product user manual, product information literature, and manufacturer's installation instructions. Water use information shall be readily available at the time of code compliance inspection.
Cooling systems shall be equipped with an overflow alarm to alert building owners tenants or maintenance personnel where the water refill valve continues to allow water to flow into the reservoir where the reservoir is full. The alarm shall have a sound pressure level rating of not less than 85 dBa measured at a distance of 10 feet (3048 mm).
Cooling systems shall automatically cease pumping water to the evaporation pads where airflow across evaporation pads ceases.
A water quality management system (either timer or water quality sensor) shall be provided. Where timers are used, the time interval between discharge of reservoir water shall be set to 6 or more hours of cooler operation. Where water quality sensors are used, the discharge of reservoir water shall be set for 800 ppm or more of total dissolved solids (TDS). Continuous discharge or continuous bleed systems shall not be installed.
Discharge water shall be reused where applications exist on site. Where a nonpotable water source system exists on site, evaporative cooler discharge water shall be collected and discharged to the collection system.

Exception: Where the reservoir water affects the quality of the nonpotable water supply making the nonpotable water unusable for its intended purposes.
Where discharge water is not recovered for reuse, the sump overflovv line shall not be directly connected to a drain. Where the discharge water is discharged into a sanitary drain, an air gap of not less than 6 inches (152 mm) shall be provided between the termination of the discharge line and the drain opening. The discharge line shall terminate in a location that is visible to the building owner, tenants, or maintenance personnel.
Where approved for use by the water or wastewater utility and the Authority Having Jurisdiction, reclaimed (recycled), or onsite treated nonpotable water shall be permitted to be used for industrial and commercial cooling or air-conditioning.
A drift eliminator shall be utilized in a cooling system, utilizing alternate sources of water, where the aerosolized water is capable of coming in contact with employees or members of the public.
A biocide shall be used to treat the cooling system recirculation water where the recycled water is capable of coming in contact with employees or members of the public.
The provisions of this section shall establish the means of enhancing energy efficiency associated with mechanical systems in a building.
The heating, ventilating, air-conditioning, for single-family houses, multi-family structures not exceeding three stories above grade, and modular houses shall be in accordance with Section E502.2 through Section E502.12. The heating, ventilation, and air-conditioning system of other buildings shall be in accordance with Section E503.0.
This section shall regulate only equipment using single-phase electric power, air conditioners, and heat pumps with rated cooling capacities less than 65000 British thermal units per hour (Btu/h) (19 kW), warm air furnaces with rated heating capacities less than 225000 Btu/h (66 kW), boilers less than 300000 Btu/h (88 kW) input, and heating-only heat pumps with rated heating capacities less than 65000 Btu/h (19 kW). [ASHRAE 90.2:6.2]
Heating, ventilating, and air-conditioning systems and equipment that do not fall under the requirements of Section E502.0 shall be in accordance with the applicable requirements of Section E503.0.
The air distribution system design, including outlet grilles, shall provide a means for balancing the air distribution system unless the design procedure provides a system intended to operate within plus or minus 10 percent of design air quantities. [ASHRAE 90.2:6.3]
Balancing dampers shall be installed in branch ducts, and the axis of the damper shall be installed parallel to the direction of airflow in the main duct.
Ducts shall be sized, installed, and tested in accordance with Section E502.4.1 through Section E502.4.4.
Portions of the air distribution system installed in or on buildings for heating and cooling shall be R-8. Where the mean outdoor dew-point temperature in a month exceeds 60°F (16°C), vapor retarders shall be installed on conditioned-air supply ducts. Vapor retarders shall have a water vapor permeance not exceeding 0.5 perm [2.87 E-11 kg/(Pa•s•m2)] where tested in accordance with Procedure A in ASTM E96.

     Insulation shall not be required where the ducts are within the conditioned space. [ASHRAE 90.2:6.4]
Joints, seams, and penetrations of duct systems shall be made airtight by means of mastics, gasketing, or other means in accordance with this code. Register penetrations shall be sealed to the wall or floor assemblies. Where HVAC duct penetrates a conditioned space, the duct penetration shall be sealed to the wall or floor assembly to prevent leakage into an unconditioned space.
For systems with a duct or air handler outside of the conditioned space, a duct leakage test shall be performed in accordance with Section E502.4.3.1.
Ductwork shall be tested to the maximum permitted leakage in 1 cubic foot per minute (ft3/min) per 100 square feet [0.0001 (m3/s)/m2] of duct surface area in accordance with SMACNA HVAC Air Duct Leakage Test Manual. Register penetrations shall be sealed during the test. The test shall be conducted with a pressure differential of 0.1 inch water gauge (0.02 kPa) across the tested system.
Duct systems shall be sized in accordance with ACCA Manual D or other methods approved by the Authority Having Jurisdiction with the velocity in the main duct not to exceed 1000 feet per minute (ft/min) (5.08 m/s) and the velocity in the secondary branch duct not to exceed 600 ft/min (3.048 m/s).
HVAC system piping installed to serve buildings and within buildings shall be thermally insulated in accordance with Table E502.5. [ASHRAE 90.2:6.5]

TABLE E502.5
MINIMUM PIPE INSULATIONTHICKNESS1, 5
[ASHRAE 90.2:TABLE 6.5]
INSULATION CONDUCTIVITY NOMINAL PIPE DIAMETER (inches)
FLUID DESIGN OPERATING TEMPERATURE RANGE (°F) Btu•inch/(h•ft2•°F) MEAN RATING TEMPERATURE(°F) <1 1 T0 11/4 11/2 TO 31/2 4 T0 6 EQUAL TO OR GREATER THAN 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 2.0
141-200 0.25-0.29 125 1.0 1.0 1.0 1.5 1.5
105-140 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 1.0
Below 40 0.2 2-0.28 100 0.5 1.0 1.0 1.0 1.5
For SI Units: °C = (°F-32)/1.8, 1 British thermal unit inch per hoursquare foot degree Fahrenheit = [0.1 W/(m•K)], 1 inch = 25 mm
Notes:
  1. 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) (mm).
    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•in/(h•ft2 •°F)] [W/(m•K)].
    k = the upper value of the conductivity range listed in this table for the applicable fluid temperature.
  2. 2 These thicknesses are based on energy efficiency considerations only. Additional insulation is sometimes required relative to safety issues/surface temperature.
  3. 3 Piping insulation is not required between the control valve and coil on run-outs where the control valve is located within 4 feet (1219 mm) of the coil and the pipe size is 1 inch (25 mm) or less.
  4. 4 These thicknesses are based on energy efficiency considerations only. Issues such as water vapor permeability or surface condensation sometimes require vapor retarders, additional insulation or both.
  5. 5 For piping exposed to outdoor air, increase insulation thickness by 1/2 of an inch (12.7 mm). The outdoor air is defined as any portion of insulation that is exposed to outdoor air. For example, attic spaces and crawlspaces are considered exposed to outdoor air.
The building shall be designed to have the capability to provide the ventilation air specified in Table E502.6. Mechanical ventilation shall be calculated in accordance with Equation E502.6. [ASHRAE 90.2:6.6.1]

Mechanical Ventilation = [(0.35 - Summer) x Volume] / 60 (Equation E502.6)

Where:
Mechanical Ventilation = required mechanical ventilation rate to supplement summer infiltration, cfm (m3/s)
Summer = summer design infiltration rate, ACH
Volume = volume of conditioned space, ft3 (m3)


TABLE E502.6
VENTILATION AIR
[ASHRAE 90.2:TABLE 6.6.1]
CATEGORY MINIMUM REQUIREMENT CONDITIONS
Mechanical ventilation1 50 ft3/min outdoor air Where summer design infiltration rate calculated in accordance with reference standard (a) or (b) is less than 0.35 ACH2.
Kitchen exhaust 100 ft3/min intermittent All conditions
Bath exhaust intermittent All conditions
For SI units: 1 cubic foot per minute = 0.00047 m3/s
Notes:
  1. 1 Calculate in accordance with Equation E502.6.
  2. 2 Reference standards:
    1. ACCA Manual J
    2. ASHRAE GRP-158
Combustion air for fossil fuel heating equipment shall comply with this code or with one of the following:
  1. Natural gas and propane heating equipment, NFPA 54
  2. Oil heating equipment, NFPA 31
  3. Solid fuel burning equipment, NFPA 211 [ASHRAE 90.2:6.6.2]
Electric heating systems shall be installed in accordance with the following requirements. [ASHRAE 90.2:6.7]
Where wall, floor, or ceiling electric-resistance heating units are used, the structure shall be zoned and heaters installed in each zone in accordance with the heat loss of that zone. Where living and sleeping zones are separate, the number of zones shall be not less than two. Where two or more heaters are installed in one room, they shall be controlled by one thermostat. [ASHRAE 90.2:6.7.1]
Where electric central warm air heating is to be installed, an electric heat pump or an off-peak electric heating system with thermal storage shall be used.

Exceptions:
  1. Electric resistance furnaces where the ducts are located inside the conditioned space, and not less than two zones are provided where the living and sleeping zones are separate.
  2. Packaged air-conditioning units with supplemental electric heat. [ASHRAE 90.2:6.7.2]
Bath ceiling units providing a combination of heat, light, or ventilation shall be provided with controls permitting separate operation of the heating function. [ASHRAE 90.2:6.8]
HVAC system equipment and system components shall be furnished with the input(s), the output(s), and the value of the appropriate performance descriptor of HVAC products in accordance with federal law or in accordance with Table E502.9, as applicable. These shall be based on newly produced equipment or components. Manufacturer's instructions shall be furnished with and attached to the equipment. The manufacturer of electric-resistance heating equipment shall furnish full-load energy input over the range of voltages at which the equipment is intended to operate. [ASHRAE 90.2:6.9]

TABLE E502.9
MINIMUM REQUIREMENTS FOR NON-FEDERALLY COVERED HVAC EQUIPMENT
[ASHRAE 90.2:TABLE 6.9]
EQUIPMENT TYPE SUBCATEGORY OR RATING CONDITION MINIMUM EFFICIENCY TEST PROCEDURE
Groundwater source heat pump* Cooling Mode 11.0 EER at 70°F Ent. Water ARI 325
11.5 EER at 50°F Ent. Water
Heating Mode 3.4 COP at 70°F Ent. Water
3.0 COP at 50°F Ent. Water
Unitary A/C Water cooled split system 9.3 EER at 85°F Ent. Water ARI 210/240
8.3 IPLV at 75°F Ent. Water
Evaporatively cooled split system 9.3 EER at 95°F Out. Amb.
8.5 IPLV at 80°F Out. Amb.
For SI units: °C = (°F-32)/1.8
* Performance for electrically powered equipment with capacity less than 65 000 Btu/h (19 kW) where rated in accordance with ARI 325.
Each system or each zone within a system shall be provided with not less than one thermostat capable of being set from 55°F (13°C) to 85°F (29°C) and capable of operating the system's heating and cooling. The thermostat or control system, or both, shall have an adjustable dead-band, the range of which includes a setting of 10°F (6°C) between heating and cooling where automatic changeover is provided. Wall-mounted temperature controls shall be mounted on an inside wall. [ASHRAE 90.2:6.10.1]
The control shall initially be set for a maximum heating temperature of 70°F (21°C) and a cooling temperature of not less than 78°F (26°C).
Each mechanical ventilation system (supply, exhaust, or both) shall be equipped with a readily accessible switch or other means for shutoff. Manual or automatic dampers installed for the purpose of isolating outside air intakes and exhausts from the air distribution system shall be designed for tight shutoff. [ASHRAE 90.2:6.10.2]
Where additional energy-consuming equipment is provided for adding moisture to maintain specific selected relative humidities in spaces or zones, a humidistat shall be provided. This device shall be capable of being set to prevent energy from being used to produce relative humidity within the space above 30 percent. [ASHRAE 90.2:6.10.3.1]
Where additional energy-consuming equipment is provided for reducing humidity, it shall be equipped with controls capable of being set to prevent energy from being used to produce a relative humidity within the space below 50 percent during periods of human occupancy and below 60 percent during unoccupied periods. [ASHRAE 90.2:6.10.3.2]
Freeze protection systems, such as heat tracing of outdoor piping and heat exchangers, including self-regulating heat tracing, shall include automatic controls capable of and configured to shut off the systems where outdoor air temperatures are above 40°F (4°C) or where the conditions of the protected fluid will prevent freezing. Snow- and ice-melting systems shall include automatic controls capable of and configured to shut off the systems where the pavement temperature is above 50°F (10°C) and no precipitation is falling and an automatic or manual control that will allow shutoff where the outdoor temperature is above 40°F (4°C) so that the potential for snow or ice accumulation is negligible. [ASHRAE 90.1:6.4.3.7]
Where setback, zoned, humidity and cooling controls and equipment are provided, they shall be designed and installed in accordance with Section E502.10 through Section E502.10.3.1. [ASHRAE 90.2:6.10.3.3]
Whole house exhaust fans shall have insulated louvers or covers which close where the fan is off. Covers or louvers shall have an insulation value of not less than R-4.2, and shall be installed in accordance with the manufacturer's installation instructions. The attic openings shall be sufficient to accommodate the ventilation capacity of the whole house fan. The operation of the whole house fan shall be considered in determining the adequacy of providing combustion air in accordance with this code.
Dampers shall be installed to close off outdoor air inlets and exhaust outlets where the ventilation system is not operating.
The heating, ventilation, and air-conditioning in buildings, other than single-family houses, multi-family structures of not more than three stories above grade, and modular houses, shall be in accordance with Section E503.0.
Mechanical equipment and systems serving the heating, cooling, ventilating, or refrigeration needs of new buildings shall be in accordance with the requirements of this section as described in Section E503.2. [ASHRAE 90.1:6.1.1.1]
Mechanical equipment and systems serving the heating, cooling, ventilating, or refrigeration needs of additions to existing buildings shall be in accordance with the requirements of this section as described in Section E503.2.

Exception: Where HVACR to an addition is provided by existing HVACR systems and equipment, such existing systems and equipment shall not be required to be in accordance with this appendix. A new system or equipment installed shall be in accordance with specific requirements applicable to those systems and equipment. [ASHRAE 90.1:6.1.1.2]
New cooling systems installed to serve previously uncooled spaces shall be in accordance with this section as described in Section E503.2. [ASHRAE 90.1:6.1.1.3.2]
Alterations to existing cooling systems shall not decrease economizer capability unless the system is in accordance with Section E503.5 through Section E503.5.4.1. [ASHRAE 90.1:6.1.1.3.3]
New and replacement ductwork shall comply with Section E503.4.7.1 through Section E503.4.7.2.1. [ASHRAE 90.1:6.1.1.3.4]
New and replacement piping shall comply with Section E503.4.7.1.

Exceptions:
  1. For equipment that is being modified or repaired but not replaced, provided that such modifications or repairs will not result in an increase in the annual energy consumption of the equipment using the same energy type.
  2. Where a replacement or alteration of equipment requires extensive revisions to other systems, equipment, or elements of a building, and such replaced or altered equipment is a like-for-like replacement.
  3. For a refrigerant change of existing equipment.
  4. For the relocation of existing equipment.
  5. For ducts and piping where there is insufficient space or access to comply with these requirements. [ASHRAE 90.1:6.1.1.3.5]
Section E503.0 shall be achieved in accordance with the requirements of Section E503.1.1 through Section E503.1.3.4, Section E503.6, Section E503.7, and one of the following:
  1. Section E503.3 and Section E503.3.1
  2. Section E503.4
  3. Section E503.4 and Section E503.8 [ASHRAE 90.1:6.2.1]
Projects using the energy cost budget method in accordance with ASHRAE 90.1 shall comply with Section E503.4, the mandatory provisions of this section, as a portion of that compliance path. [ASHRAE 90.1:6.2.2]
The simplified approach shall be an optional path for compliance where the following conditions are met:
  1. The building is not more than two stories in height.
  2. Gross floor area is less than 25 000 square feet (2322.6 m2).
  3. The HVAC system in the building is in accordance with the requirements listed in Section E503.3.1. [ASHRAE 90.1:6.3.1]
The HVAC system shall comply with the following criteria:
  1. The system serves a single HVAC zone.
  2. The equipment shall comply with the variable flow requirements of Section E503.5.6.2.
  3. Cooling (where any) shall be provided by a unitary packaged or split-system air conditioner that is either air-cooled or evaporatively cooled, with efficiency that is in accordance with the requirements shown in Table E503.7.1(1), Table E503.7.1(2), or Table E503.7.1(4) for the applicable equipment category.
  4. The system shall have an air economizer in accordance with Section E503.5 and Section E503.4.6.13.
  5. Heating (where any) shall be provided by a unitary packaged or split-system heat pump that is in accordance with the applicable efficiency requirements shown in Table E503.7.1(2) or Table E503.7.1(4), a fuel-fired furnace that is in accordance with the applicable efficiency requirements shown in Table E503.7.1(5), an electric resistance heater, or a baseboard system connected to a boiler that is in accordance with the applicable efficiency requirements shown in Table E503.7.1(6).
  6. The system shall comply with the exhaust air energy recovery requirements in accordance with Section E503.5.10.
  7. The system shall be controlled by a manual changeover or dual setpoint thermostat.
  8. Where a heat pump equipped with auxiliary internal electric resistance heaters is installed, controls shall be provided that prevent supplemental heater operation where the heating load is capable of being met by the heat pump alone during both steady-state operation and setback recovery. Supplemental heater operation shall be permitted during outdoor coil defrost cycles. The heat pump shall be controlled in accordance with one of the following:
    1. A digital or electronic thermostat designed for heat pump use that energizes auxiliary heat where the heat pump has insufficient capacity to maintain setpoint or to warm up the space at a sufficient rate.
    2. A multistage space thermostat and an outdoor air thermostat wired to energize auxiliary heat on the last stage of the space thermostat and where outdoor air temperature is less than 40°F (4°C).

      Exceptions: Heat Pumps that comply with the following:
      1. Have a minimum efficiency regulated by NAECA.
      2. In accordance with the requirements shown in Table E503.7.1(2).
      3. Include all usage of internal electric resistance heating.
  9. The system controls shall not permit reheat or other form of simultaneous heating and cooling for humidity control.
  10. Systems serving spaces other than hotel or motel guest rooms, and other than those requiring continuous operation, which have both a cooling or heating capacity more than 15 000 Btu/h (4.4 kW) and a supply fan motor power more than 0.75 horsepower (hp) (0.56 kW), shall be provided with a time clock that is in accordance with the following:
    1. Can start and stop the system under different schedules for seven different day-types per week.
    2. Is capable of retaining programming and time setting during a loss of power for a period of not less than 10 hours.
    3. Includes an accessible manual override that allows temporary operation of the system for up to 2 hours.
    4. Is capable of and configured with temperature setback down to 55°F (13°C) during off hours.
    5. Is capable of and configured with temperature setup to 90°F (32°C) during off hours.
  11. Except for piping within manufacturer's units, HVAC piping shall be insulated in accordance with Table E503.7.3(1) and Table E503.7.3(2). Insulation exposed to weather shall be suitable for outdoor service (e.g., protected by aluminum, sheet metal, painted canvas, or plastic cover). Cellular foam insulation shall be protected as above or painted with a coating that is water retardant and provides shielding from solar radiation.
  12. Ductwork and plenums shall be insulated in accordance with Table E503.7.2 and shall be sealed in accordance with Section E503.4.7.2.
  13. Construction documents shall require a ducted system to be air balanced in accordance with industry-accepted procedures.
  14. Outdoor air intake and exhaust systems shall comply with Section E503.4.6.4 through Section E503.4.6.5.
  15. Where separate heating and cooling equipment serves the same temperature zone, thermostats shall be interlocked to prevent simultaneous heating and cooling.
  16. Systems with a design supply air capacity more than 10000 ft3/min (4.7195 m3/s) shall have optimum start controls.
  17. The system shall comply with the demand control ventilation requirements of Section E503.4.6.9 and the ventilation design requirements of Section E503.5.6.6.
  18. The system shall comply with the door switch requirements of Section E503.5.14. [ASHRAE 90.1:6.3.2]
Climate zones identified in this appendix shall be determined in accordance with ASHRAE 90.1. For locations in the United States and its territories, the assigned climate zone and, where required, the assigned climate zone letter shall be in accordance with ASHRAE 169.

Exception: Where recorded historical climatic data are available for a construction site, it is permitted to be used to determine compliance where approved by the Authority Having Jurisdiction. [ASHRAE 90.1:5.1.4.1]
Equipment shown in Table E503.7.1(1) through Table E503.7.1(16) shall have a minimum performance at the specified rating conditions where tested in accordance with the specified test procedure. Where multiple rating conditions or performance requirements are provided, the equipment shall satisfy the stated requirements unless otherwise exempted by footnotes in the table. Equipment covered under the Federal Energy Policy Act of 1992 (EPACT) shall have no minimum efficiency requirements for operation at minimum capacity or other than standard rating conditions. Equipment used to provide service water heating functions as part of a combination system shall satisfy the stated requirements for the appropriate space heating or cooling category.

Tables are as follows:
  1. Table E503.7.1(1), "Electrically Operated Unitary Air Conditioners and Condensing Units-Minimum Efficiency Requirements"
  2. Table E503.7.1(2), "Electrically Operated Unitary and Applied Heat Pumps-Minimum Efficiency Requirements"
  3. Table E503.7.1(3), "Water-Chilling Packages-Efficiency Requirements" (See Section E503.4.1 for water-cooled centrifugal water-chilling packages that are designed to operate at nonstandard conditions.)
  4. Table E503.7.1(4), "Electrically Operated Packaged Terminal Air Conditioners, Packaged Terminal Heat Pumps, Single-Package Vertical Air Conditioners, Single-Package Vertical Heat Pumps, Room Air Conditioners, and Room Air Conditioner Heat Pumps-Minimum Efficiency Requirements"
  5. Table E503.7.1(5), "Warm-Air Furnaces and Combination Warm-Air Furnaces/Air-Conditioning Units, Warm-Air Duct Furnaces, and Unit Heaters-Minimum Efficiency Requirements" Heating, Ventilating, and Air Conditioning
  6. Table E503.7.1(6), "Gas- and Oil-Fired Boilers-Minimum Efficiency Requirements"
  7. Table E503.7.1(7), "Performance Requirements for Heat-Rejection Equipment"
  8. Table E503.7.1(8), "Heat Transfer Equipment"
  9. Table E503.7.1(9), "Electrically Operated Variable-Refrigerant-Flow Air Conditioners-Minimum Efficiency Requirements"
  10. Table E503.7.1(10), "Electrically Operated Variable-Refrigerant-Flow and Applied Heat Pumps-Minimum Efficiency Requirements"
  11. Table E503.7.1(11), "Air Conditioners and Condensing Units Serving Computer Rooms"
  12. Table E503.7.1(12), "Commercial Refrigerators and Freezers-Minimum Efficiency Requirements"
  13. Table E503.7.1(13), "Commercial Refrigeration-Minimum Efficiency Requirements"
  14. Table E503.7.1(14), "Vapor-Compression-Based Indoor Pool Dehumidifiers-Minimum Efficiency Requirements"
  15. Table E503.7.1(15), "Electrically Operated DX-DOAS Units, Single-Package and Remote Condenser, without Energy Recovery-Minimum Efficiency Requirements"
  16. Table E503.7.1(16), "Electrically Operated DX-DOAS Units, Single-Package and Remote Condenser, with Energy Recovery-Minimum Efficiency Requirements" [ASHRAE 90.1:6.4.1.1]
Equipment not designed for operation in accordance with AHRI 550/590 test conditions of 44°F (7°C) leaving chilled fluid temperature and 2.4 gallons per minute per ton (gpm/ton) (0.00015 L/s/kg) evaporator fluid flow and 85°F (29°C) entering condenser-fluid temperature with 3.0 gpm/ton (0.00018 L/s/kg) condenser-fluid flow shall have maximum full-load kW/ton (FL) and part-load rating requirements adjusted in accordance with Equation E503.4.1(1) through Equation E503.4.1(3):

FLadj = FL/Kadj [Equation E503.4.1(1)]

PLVadj = IPLV/Kadj [Equation E503.4.1(2)]

Kadj = A × B [Equation E503.4.1(3)]

Where:
FL = full-load kW/ton value from Table E503.7.1(3)
FLadj = maximum full-load kW/ton rating, adjusted for nonstandard conditions
IPLV = IPLV value from Table E503.7.1(3)
IPLVadj = maximum NPLV rating, adjusted for non-standard conditions
A = 0.00000014592 × (LIFT)4 - 0.0000346496 × (LIFT)3 + 0.00314196 × (LIFT)2 0.147199 × (LIFT) + 3.9302
B = 0.0015 × LvgEvap + 0.934
LIFT = LvgCond - LvgEvap
LvgCond = Full-load condenser leaving fluid temperature (°F)
LvgEvap = Full-load evaporator leaving temperature (°F)


     The FLadj and PLVadj values shall only be applicable for centrifugal chillers in accordance with the following full-load design ranges:
  1. Minimum Evaporator Leaving Temperature: 36°F (2°C)
  2. Maximum Condenser Leaving Temperature: 115°F (46°C)
  3. LIFT is not less than 20°F (-6°C) and not more than 80°F (27°C)
     Manufacturers shall calculate the FLadj and PLVadj before determining whether to label the chiller in accordance with Section E503.4.4. Chillers that are in accordance with ASHRAE 90.1 shall be labeled on chillers in accordance with the scope of ASHRAE 90.1.

     Centrifugal chillers designed to operate outside of these ranges shall not be covered under this appendix.

Example: Path A, 600 ton (600000 kg) centrifugal chiller Table E503.7.1(3) efficiencies.

F = 0.560 kW/ton
IPLV = 0.500 kW/ton
LvgCond = 91.16°F
LvgEvap = 42°F
LIFT = 91.16°F - 42°F = 49.16°F
Kadj = A × B
A = 0.00000014592 × (49.16)4 - 0.0000346496 × (49.16)3 + 0.00314196 × (49.16)2 - 0.147199 × (49.16) + 3.9302 = 1.0228
B = 0.0015 × 42 + 0.934 = 0.9970
FLajd = 0.560/(1.0228 x 0.9970) = 0.549 kW/ton
PLVadj = 0.500/(1.0228 x 0.9970) = 0.490 kW/ton [ASHRAE 90.1:6.4.1.2.1]
For SI units: 1 metric ton = 1000 kg, 1000 British thermal units per hour = 0.293 kW, 1 gallon per minute = 0.06 L/s, °C = (°F-32)/1.8
Equipment with an evaporator leaving fluid temperature more than 32°F (0°C) and water-cooled positive displacement chilling packages with a condenser leaving fluid temperature less than 115°F (46°C) shall be in accordance with Table E503.7.1(3) where tested or certified with water at standard rating conditions, in accordance with the referenced test procedure. [ASHRAE 90.1:6.4.1.2.2]
Equipment not listed in the tables referenced in Section E503.4 and Section E503.4.1 shall be permitted to be used. [ASHRAE 90.1:6.4.1.3]
Equipment efficiency information supplied by manufacturers shall be verified in accordance with one of the following:
  1. Equipment covered under EPACT shall be in accordance with U.S. Department of Energy certification requirements.
  2. Where a certification program exists for a covered product, and it includes provisions for verification and challenge of equipment efficiency ratings, then the product shall be listed in the certification program.
  3. Where a certification program exists for a covered product, and it includes provisions for verification and challenge of equipment efficiency ratings, but the product is not listed in the existing certification program, the ratings shall be verified by an independent laboratory test report.
  4. Where no certification program exists for a covered product, the equipment efficiency ratings shall be supported by data furnished by the manufacturer.
  5. Where components such as indoor or outdoor coils from different manufacturers are used, the system designer shall specify component efficiencies whose combined efficiency is in accordance with the minimum equipment efficiency requirements in Section E503.4 through Section E503.4.4.1.
  6. Requirements for plate-type liquid-to-liquid heat exchangers are listed in Table E503.7.1(8). [ASHRAE 90.1:6.4.1.4]
Mechanical equipment that is not covered by the U.S. National Appliance Energy Conservation Act (NAECA) of 1987 shall carry a permanent label installed by the manufacturer stating that the equipment is in accordance with the requirements of ASHRAE 90.1. [ASHRAE 90.1:6.4.1.5.1]
Nonstandard-size packaged terminal air conditioners and heat pumps with existing sleeves having an external wall opening of less than 16 inches (406 mm) high or less than 42 inches (1067 mm) wide and having a cross-sectional area less than 670 square inches (0.432 m2) shall be factory labeled in accordance with the following:

"Manufactured for nonstandard-size applications only: not to be installed in new construction projects." [ASHRAE 90.1:6.4.1.5.2]
Heating and cooling system design loads for the purpose of sizing systems and equipment shall be determined in accordance with ASHRAE/ACCA 183. [ASHRAE 90.1:6.4.2.1]
Pump differential pressure (head) for the purpose of sizing pumps shall be determined in accordance with generally accepted engineering standards and handbooks acceptable to the Authority Having Jurisdiction. The pressure drop through each device and pipe segment in the critical circuit at design conditions shall be calculated. [ASHRAE 90.1:6.4.2.2]
The supply of heating and cooling energy to each zone shall be individually controlled by thermostatic controls responding to temperature within the zone. For the purposes of Section E503.4.6, a dwelling unit shall be permitted to be considered a single zone.

Exceptions: Independent perimeter systems that are designed to offset only building envelope loads shall be permitted to serve one or more zones also served by an interior system provided:
  1. the perimeter system includes not less than one thermostatic control zone for each building exposure having walls facing only one orientation for 50 contiguous feet (15240 mm) or more and
  2. the perimeter system heating and cooling supply is controlled by thermostatic controls located within the zones served by the system.
     Exterior walls and semiexterior walls are considered to have different orientations where the exposures they face differ by more than 45 degrees (0.79 rad). [ASHRAE 90.1:6.4.3.1.1]
Where used to control both heating and cooling, zone thermostatic controls shall be capable of and configured to provide a temperature range or dead band of not less than 5°F (3°C) within which the supply of heating and cooling energy to the zone is shut off or reduced to a minimum.

Exceptions:
  1. Thermostats that require manual changeover between heating and cooling modes.
  2. Special occupancy or special applications where wide temperature ranges are not acceptable (such as retirement homes, process applications, museums, some areas of hospitals) and are approved by the Authority Having Jurisdiction. [ASHRAE 90.1:6.4.3.1.2]
Where heating and cooling to a zone are controlled by separate zone thermostatic controls located within the zone, means (such as limit switches, mechanical stops, or, for DDC systems, software programming) shall be provided to prevent the heating setpoint from exceeding the cooling setpoint minus any applicable proportional band. [ASHRAE 90.1:6.4.3.2]
HVAC systems shall have the off-hour controls required by Section E503.4.6.3.1 through Section E503.4.6.3.4.

Exceptions:
  1. HVAC systems intended to operate continuously.
  2. HVAC systems having a design heating capacity and cooling capacity less than 15 000 Btu/h (4.4 kW) that are equipped with readily accessible manual ON/OFF controls. [ASHRAE 90.1:6.4.3.3]
HVAC systems shall be equipped with not less than one of the following:
  1. Controls that can start and stop the system under different time schedules for seven different day-types per week, are capable of retaining programming and time setting during loss of power for a period of not less than 10 hours, and include an accessible manual override, or equivalent function, that allows temporary operation of the system for up to 2 hours.
  2. An occupant sensor that is capable of shutting the system off where no occupant is sensed for a period of up to 30 minutes.
  3. A manually operated timer capable of being adjusted to operate the system for up to 2 hours.
  4. An interlock to a security system that shuts the system off where the security system is activated.
Exception: Residential occupancies shall be permitted to use controls that can start and stop the system under two different time schedules per week. [ASHRAE 90.1:6.4.3.3.1]
Heating systems shall be equipped with controls capable of and configured to automatically restart and temporarily operate the system as required to maintain zone temperatures above an adjustable heating setpoint of not less than 10°F (6°C) below the occupied heating setpoint. Cooling systems shall be equipped with controls capable of and configured to automatically restart and temporarily operate the mechanical cooling system as required to maintain zone temperatures below an adjustable cooling setpoint of not less than 5°F (3°C) above the occupied cooling setpoint or to prevent high space humidity levels.

Exception: Radiant heating systems capable of and configured with a setback heating setpoint at not less than 4°F (2°C) below the occupied heating setpoint. [ASHRAE 90.1:6.4.3.3.2]
Individual heating and cooling systems with setback controls and DDC shall have optimum start controls. The control algorithm shall, as a minimum, be a function of the difference between space temperature and occupied setpoint, the outdoor temperature, and the amount of time prior to scheduled occupancy. Mass radiant floor slab systems shall incorporate floor temperature into the optimum start algorithm. [ASHRAE 90.1:6.4.3.3.3]
HVAC systems serving zones that are intended to operate or be occupied nonsimultaneously shall be divided into isolation areas. Zones shall be permitted to be grouped into a single isolation area provided it does not exceed 25 000 square feet (2322.6 m2) of conditioned floor area and does not include more than one floor. Each isolation area shall be equipped with isolation devices capable of and configured to automatically shut off the supply of conditioned air and outdoor air to and exhaust air from the area. Each isolation area shall be controlled independently by a device meeting the requirements of Section E503.4.6.3.1. For central systems and plants, controls and devices shall be provided to allow stable system and equipment operation for any length of time while serving only the smallest isolation area served by the system or plant.

Exceptions: Isolation devices and controls are not required for the following:
  1. Exhaust air and outdoor air connections to isolation zones where the fan system to which they connect is not more than 5000 ft3/min (2.3597 m3/s).
  2. Exhaust airflow from a single isolation zone of less than 10 percent of the design airflow of the exhaust system to which it connects.
  3. Zones intended to operate continuously or intended to be inoperative only when all other zones are inoperative. [ASHRAE 90.1:6.4.3.3.4]
Stair and elevator shaft vents shall be equipped with motorized dampers that are capable of and configured to automatically close during normal building operation and are interlocked to open as required by fire and smoke detection systems. [ASHRAE 90.1:6.4.3.4.1]
Outdoor air intake and exhaust systems shall be equipped with motorized dampers that will automatically shut when the systems or spaces served are not in use. Ventilation outdoor air and exhaust or relief dampers shall be capable of and configured to automatically shut off during preoccupancy building warm-up, cooldown, and setback, except when ventilation reduces energy costs or when ventilation shall be supplied to comply with the code requirements.

Exceptions:
  1. Backdraft gravity (nonmotorized) dampers shall be permitted for exhaust and relief in buildings less than three stories in height and for ventilation air intakes and exhaust and relief dampers in buildings of any height located in Climate Zones 0, 1, 2 and 3. Back-draft dampers for ventilation air intakes shall be protected from direct exposure to wind.
  2. Back-draft gravity (nonmotorized) dampers shall be permitted in systems with a design outdoor air intake or exhaust capacity of 300 ft3/min (0.142 m3/s) or less.
  3. Dampers shall not be required in ventilation or exhaust systems serving unconditioned spaces.
  4. Dampers shall not be required in exhaust systems serving Type 1 kitchen exhaust hoods. [ASHRAE 90.1:6.4.3.4.2]
Where outdoor air supply, and exhaust or relief dampers are required in Section E503.4.6.4, they shall have a maximum leakage rate in accordance with Table E503.4.6.4.2 where tested in accordance with AMCA 500D. [ASHRAE 90.1:6.4.3.4.3]

TABLE E503.4.6.4.2
MAXIMUM DAMPER LEAKAGE
(cubic foot per minute per square foot) at 1.0 in. w.g
[ASHRAE 90.1:TABLE 6.4.3.4.3]
VENTILATION AIR INTAKE EXHAUST/RELIEF
CLIMATE ZONE NONMOTORIZED* MOTORIZED NONMOTORIZED* MOTORIZED
0, 1, 2
any height
-
20
-
4
-
20
-
4
3
any height
-
20
-
10
-
20
-
10
4, 5b, 5c
less than 3 stories
3 or more stories
-
not allowed
not allowed
-
10
10
-
20
not allowed
-
10
10
5a, 6, 7, 8
less than 3 stories
3 or more stories
-
not allowed
not allowed
-
4
4
-
20
not allowed
-
4
4
For SI units: 1 cubic foot per minute = 0.00047 m3/s, 1 square foot = 0.0929 m2, 1 inch water gauge = 0.249 kPa
*   Dampers smaller than 24 inches (610 mm) in either dimension shall be permitted to have leakage of 40 ft3/min per square foot [0.203 (m3/s)/m2].
Fans with motors more than 0.75 hp (0.56 kW) shall have automatic controls in accordance with Section E503.4.6.3.1 that are capable of and configured to shut off fans when not required.

Exception: HVAC systems intended to operate continuously. [ASHRAE 90.1:6.4.3.4.4]
Enclosed parking garage ventilation systems shall automatically detect contaminant levels and stage fans or modulate fan airflow rates to 50 percent or less of design capacity, provided acceptable contaminant levels are maintained.

Exceptions:
  1. Garages not more than 30000 square feet (2787.09 m2) with ventilation systems that do not utilize mechanical cooling or mechanical heating.
  2. Garages that have a garage area to ventilation system motor nameplate hp ratio that exceeds 1500 square feet per horsepower (ft2/hp) (186.8 m2/kW) and do not utilize mechanical cooling or heating.
  3. Where not permitted by the Authority Having Jurisdiction. [ASHRAE 90.1:6.4.3.4.5]
Heat pumps equipped with internal electric resistance heaters shall have controls that prevent supplemental heater operation where the heating load is capable of being met by the heat pump alone during both steady-state operation and setback recovery. Supplemental heater operation shall be permitted during outdoor coil defrost cycles.

Exception: Heat pumps whose minimum efficiency is regulated by U.S. National Appliance Energy Conservation Act (NAECA) and whose ratings are in accordance with the requirements shown in Table E503.7.1(2) and includes the use of an internal electric resistance heating. [ASHRAE 90.1:6.4.3.5]
Humidity control shall prevent the use of fossil fuel or electricity to produce relative humidity (RH) more than 30 percent in the warmest zone served by the humidification system and to reduce the RH valve to less than 60 percent in the coldest zone served by the dehumidification system. Where a zone is served by a system or systems with both humidification and dehumidification capability, means (such as limit switches, mechanical stops, or, for DDC systems, software programming) shall be provided capable of preventing simultaneous operation of humidification and dehumidification equipment.

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 hospitals, and approved by the Authority Having Jurisdiction or required by accreditation standards and humidity controls are configured to maintain a deadband of not less than 10 percent RH where no active humidification or dehumidification takes place.
  3. Systems serving zones where humidity levels are required to be maintained with precision of not more than ± 5 percent RH to comply with applicable codes or accreditation standards or as approved by the Authority Having Jurisdiction. [ASHRAE 90.1:6.4.3.6]
Freeze protection systems, such as heat tracing of outdoor piping and heat exchangers, including self-regulating heat tracing, shall include automatic controls capable of and configured to shut off the systems when outdoor air temperatures are more than 40°F (4°C) or when the conditions of the protected fluid will prevent freezing. Snow and ice melting systems shall include automatic controls capable of and configured to shut off the systems when the pavement temperature is more than 50°F (10°C) and no precipitation is falling, and an automatic or manual control that will allow shutoff when the outdoor temperature is more than 40°F (4°C) so that the potential for snow or ice accumulation is negligible. [ASHRAE 90.1:6.4.3.7]
Demand control ventilation (DCV) shall be required for spaces that are more than 500 square feet (46.45 m2) and with a design occupancy for ventilation of not less than 25 people per 1000 square feet (92.9 m2) of floor area and served by systems with one or more of the following:
  1. Air-economizer.
  2. Automatic modulating control of outdoor air damper
  3. Design outdoor airflow more than 3000 ft3/min (1.4158 m3/s).
Exceptions:
  1. Systems with exhaust air energy recovery in accordance with Section E503.5.10.
  2. Multiple-zone systems without DDC of individual zones communicating with a central control panel.
  3. Systems with a design outdoor airflow less than 750 ft3/min (0.3540 m3/s).
  4. Spaces where more than 75 percent of the space design outdoor airflow is required for makeup air that is exhausted from the space or transfer air that is required for makeup air that is exhausted from other spaces.
  5. Spaces with one of the following occupancy categories in accordance with Chapter 4 or ASHRAE 62.1: correctional cells, daycare sickrooms, science labs, barbers, beauty and nail salons, and bowling alley seating. [ASHRAE 90.1:6.4.3.8]
Radiant heat systems shall be used to provide heat outdoors. Outdoor radiant heating systems shall be provided with controls that sense the presence of occupants or other device that automatically shuts down the system where no occupants are in the heating area.
Heating for vestibules and for air curtains with integral heating shall include automatic controls capable of and configured to shut off the heating system when outdoor air temperatures are more than 45°F (7.2°C) Vestibule heating and cooling systems shall be controlled by a thermostat in the vestibule capable of and configured to limit heating to a maximum of 60°F (15.5°C) and cooling to a minimum of 85°F (29.4°C).

Exception: Heating or cooling provided by site-recovered energy or by transfer air that would otherwise be exhausted. [ASHRAE 90.1:6.4.3.9]
Direct digital control shall be required in accordance with Section E503.4.6.12.1 through Section E503.4.6.12.3. [ASHRAE 90.1:6.4.3.10]
DDC shall be provided in the applications and qualifications in accordance with Table E503.4.6.12.1.

Exception: DDC is not required for systems using the simplified approach to compliance in accordance with Section E503.3. [ASHRAE 90.1:6.4.3.10.1]

TABLE E503.4.6.12.1
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 the system Individual systems supplying more than three zones and with fan system bhp of 10 hp or more
New building Chilled-water plant and all coils and terminal units served by the system Individual plants supplying more than three zones and with design cooling capacity of 300000 Btu/h or more
New building Hot-water plant and all coils and terminal units served by the system Individual plants supplying more than three zones and with design heating capacity of 300000 Btu/h or more
Alteration or addition Zone terminal unit such as VAV box Where existing zones served by the same air-handling, chilled-water, or hot-water system have DDC
Alteration or addition Air-handling system or fan coil Where existing air-handling system(s) and fan-coil (s) served by the same chilled or hot-water plant have DDC
Alteration or addition New air-handling system and all new zones served by the system Individual systems with fan system bhp of 10 hp or more and supplying more than three zones and more than 75 percent of zones are new
Alteration or addition New or upgraded chilled-water plant Where all chillers are new and plant design cooling capacity is 300000 Btu/h or more
Alteration or addition New or upgraded hot-water plant Where all boilers are new and plant design heating capacity is 300000 Btu/h or more
For SI units: 1000 British thermal units = 0.293 kW, 1 horsepower = 0.746 kW
Where DDC is required by Section E503.4.6.12.1, the DDC system shall be capable of and configured with all of the following, as required, to provide the control logic required in Section E503.5:
  1. Monitoring zone and system demand for fan pressure, pump pressure, heating, and cooling.
  2. Transferring zone and system demand information from zones to air distribution system controllers and from air distribution systems to heating and cooling plant controllers.
  3. Automatically detecting those zones and systems that are capable of excessively driving the reset logic and generate an alarm or other indication to the system operator.
  4. Readily allowing operator removal of zone(s) from the reset algorithm. [ASHRAE 90.1:6.4.3.10.2]
Where DDC is required in accordance with Section E503.4.6.12.1 for new buildings, the DDC system shall be capable of trending and graphically displaying input and output points. [ASHRAE 90.1:6.4.3.10.3]
Air-cooled direct-expansion cooling units listed in Tables E503.7.1(1) and E503.7.1(2), where an air economizer is installed in accordance with Section E503.5, shall include a fault detection and diagnostics (FDD) system complying with the following:
  1. The following temperature sensors shall be permanently installed to monitor system operation:
    1. Outdoor air
    2. Supply air
    3. Return air, where required for economizer control
  2. The system shall have the capability of displaying the value of each sensor.
  3. The FDD system or unit controls shall be capable of and configured to provide system status by indicating the following:
    1. Free cooling available
    2. Economizer enabled
    3. Compressor enabled
    4. Heating enabled
    5. Mixed-air low-limit cycle active
  4. The FDD system or unit controls shall have provisions to manually initiate each operating mode so that the operation of compressors, economizers, fans, and the heating system can be independently tested and verified.
  5. The FDD system shall be capable of and configured to detect the following faults:
    1. Air temperature sensor failure/fault
    2. Not economizing when the unit should be economizing
    3. Economizing when the unit should not be economizing
    4. Damper not modulating
    5. Excess outdoor air
  6. The FDD system shall be capable of and configured to report faults to a fault management application or DDC system accessible by operating or service personnel, or annunciated locally on zone thermostats. [ASHRAE 90.1:6.4.3.12]
HVAC Ducts shall be constructed in accordance with provisions contained in the SMACNA HVAC Duct Construction Standard. HVAC system construction and insulation shall comply with Section E503.4.7.1 and Section E503.4.7.2.
Insulation required by this section shall be installed in accordance with industry-accepted standards. These requirements shall not apply to HVAC equipment. Insulation shall be protected from damage, including that due to sunlight, moisture, equipment maintenance, and wind, but not limited to the following:
  1. Insulation exposed to weather shall be suitable for outdoor service (e.g., protected by aluminum, sheet metal, painted canvas, or plastic cover). Cellular foam insulation shall be protected as above or painted with a coating that is water retardant and provides shielding from solar radiation that is capable of causing degradation of the material.
  2. Insulation covering chilled-water piping, refrigerant suction piping, or cooling ducts located outside the conditioned space shall include a vapor retardant located outside the insulation (unless the insulation is inherently vapor retardant), penetrations and joints of which shall be sealed. [ASHRAE 90.1:6.4.4.1.1]
Supply and return ducts and plenums installed as part of an HVAC air distribution system shall be thermally insulated in accordance with Table E503.7.2.

Exceptions:
  1. Factory-installed plenums, casings, or ductwork furnished as a part of HVAC equipment tested and rated in accordance with Section E503.4 through Section E503.4.4.1.
  2. Ducts or plenums located in heated spaces, semi-heated spaces, or cooled spaces.
  3. For run outs less than 10 feet (3048 mm) in length to air terminals or air outlets, the rated R-value of insulation shall not be required to exceed R-3.5.
  4. Backs of air outlets and outlet plenums exposed to unconditioned or indirectly conditioned spaces with face areas exceeding 5 square feet (0.5 m2) shall not be required to exceed R-2; those not exceeding 5 square feet (0.5 m2) shall not be required to be insulated. [ASHRAE 90.1:6.4.4.1.2]
Piping shall be thermally insulated in accordance with Table E503.7.3(1) and Table E503.7.3(2).

Exceptions:
  1. Factory-installed piping within HVAC equipment tested and rated in accordance with Section E503.4 through Section E503.4.4.1.
  2. Piping that conveys fluids having a design operating temperature range between 60°F (16°C) and 105°F (41°C), inclusive.
  3. Piping that conveys fluids that have not been heated or cooled through the use of fossil fuels or electricity (such as roof and condensate drains, domestic cold water supply, or natural gas piping).
  4. Where heat gain or heat loss will not increase energy usage (such as liquid refrigerant piping).
  5. For piping 1 inch (25.4 mm) or less, insulation shall not be required for strainers, control valves, and balancing valves. [ASHRAE 90.1:6.4.4.1.3]
Thermally ineffective panel surfaces of sensible heating panels, including U-bends and headers, shall be insulated with not less than R-3.5. Adjacent building envelope insulation shall be applied to this insulation value. [ASHRAE 90.1:6.4.4.1.4]
The bottom surfaces of floor structures incorporating radiant heating shall be insulated not less than R-3.5. Adjacent building envelope insulation shall be applied to this insulated value.

Exception: Heated slab-on-grade floors incorporating radiant heating shall be in accordance with ASHRAE 90.1. [ASHRAE 90.1:6.4.4.1.5]
Transverse joints, longitudinal seams, and duct wall penetrations shall be sealed. Pressure-sensitive tape shall not be used as the primary sealant, unless it has been certified to comply with UL 181A or UL 181B by an independent testing laboratory and the tape is used in accordance with that certification. All other connections shall be considered transverse joints, including but not limited to spin-ins, taps, other branch connections, access door frames and jambs, and duct connections to equipment.

Exceptions:
  1. Rods that penetrate the duct wall that shall be permitted to move in order to function properly (control rod for volume damper) shall not be sealed in a fashion that prevents them from working properly.
  2. Spiral lock seams in a round or flat oval duct.
Ductwork shall be leak-tested in accordance with the SMACNA HVAC Air Duct Leakage Test Manual. Representative sections totaling not less than 20 percent of the total installed duct area shall be tested. Where the tested 20 percent fail to comply with the requirements of this section, then 40 percent of the total installed duct area shall be tested. Where the tested 40 percent fail to comply with the requirements of this section, then 100 percent of the total installed duct area shall be tested. Sections shall be selected by the building owner or designated representative of the building owner. Positive pressure leakage testing shall be permitted for negative pressure ductwork. The permitted duct leakage shall be not more than the following:

Lmax = CLP0•65 (Equation E503.4.7.2.1)

Where:
Lmax = maximum permitted leakage, (ft3/min)/100 square feet (0.0001 (m3/s)/m2] duct surface area.
CL = Six, duct leakage class, (ft3/min)/100 square feet (0.0001 (m3/s)/m2] duct surface area at 1 inch water column (0.2 kPa).
P = test pressure, which shall be equal to the design duct pressure class rating, inch water column (kPa).
Cooling systems shall include either an air economizer or fluid economizer in accordance with Section E503.5.1 through Section E503.5.4.1.

Exceptions: Economizers shall not be required for the following systems:
  1. Individual fan-cooling units with a supply capacity less than the minimum listed in Table E503.5(1).
  2. Chilled-water cooling systems without a fan or that use induced airflow, where the total capacity of these systems is less than 1000000 Btu/h (293 kW) in Climate Zones 0, 1B, and 2 through 4; less than 1400000 Btu/h (410 kW) in Climate Zones 5 through 8; or any size in Climate Zone 1A.
  3. Systems that include nonparticulate air treatment in accordance with ASHRAE 62.1.
  4. In hospitals and ambulatory surgery centers, where more than 75 percent of the air designed to be supplied by the system is to spaces that are required to be humidified more than 35°F (2°C) dew-point temperature to comply with applicable codes or accreditation standards; in all other buildings, where more than 25 percent of the air designed to be supplied by the system is to spaces that are designed to be humidified more than 35°F (2°C) dew-point temperature to satisfy process needs. This exception shall not apply to computer rooms.
  5. Systems that include a condenser heat recovery system with a minimum capacity in accordance with Section E503.5.10.1.2.
  6. Systems that serve residential spaces where the system capacity is less than five times the requirement listed in Table E503.5(1).
  7. Systems that serve spaces whose sensible cooling load at design conditions, excluding transmission and infiltration loads, is less than or equal to transmission and infiltration losses at an outdoor temperature of 60°F (16°C).
  8. Systems expected to operate less than 20 hours per week.
  9. Where the use of outdoor air for cooling will affect supermarket open refrigerated casework systems.
  10. For comfort cooling where the cooling efficiency is not less than the efficiency improvement requirements in accordance with Table E503.5(2).
  11. Systems primarily serving computer rooms where in accordance with one of the following:
    1. The total design cooling load of all computer rooms in the building is less than 3000000 Btu/h (879 kW) and the building in which they are located is not served by a centralized chilled water plant.
    2. The room total design cooling load is less than 600000 Btu/h (176 kW) and the building in which they are located is served by a centralized chilled water plant.
    3. The local water authority does not permit cooling towers.
    4. Less than 600000 Btu/h (176 kW) of computer room cooling equipment capacity is being added to an existing building.
  12. Dedicated systems for computer rooms where a minimum of 75 percent of the design load serves one of the following:
    1. Spaces classified as an essential facility.
    2. Spaces having a design of Tier IV in accordance with TIA 942.
    3. Spaces classified as Critical Operations Power Systems (COPS) in accordance with NFPA 70.
    4. Spaces where core clearing and settlement services are performed such that their failure to settle pending financial transactions is capable of systemic risk in accordance with "The Interagency Paper on Sound Practices to Strengthen the Resilience of the US Financial System" (April 7, 2003). [ASHRAE 90.1:6.5.1]
TABLE E503.5(1)
MINIMUM FAN-COOLING UNIT SIZE WHERE AN ECONOMIZER IS REQUIRED
[ASHRAE 90.1: TABLE 6.5.1-1]
CLIMATE ZONES COOLING CAPACITY WHERE AN ECONOMIZER IS REQUIRED
0A, 0B, 1A, 1B No economizer requirement
2A, 2B, 3A, 4A, 5A, 6A, 3B, 3C, 4B, 4C, 5B, 5C, 6B, 7, 8 ≥54000 Btu/h
For SI units: 1000 British thermal units per hour = 0.293 kW

TABLE E503.5(2)
ELIMINATE REQUIRED ECONOMIZER FOR COMFORT COOLING BY INCREASING COOLING EFFICIENCY
[ASHRAE 90.1:TABLE 6.5.1-2]
CLIMATE ZONES EFFICIENCY IMPROVEMENT*
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%
*  Where a unit is rated with an IPLV, IEER or SEER, to eliminate the required economizer, the minimum cooling efficiency of the HVAC unit shall be increased by the percentage shown. Where the HVAC unit is rated with a full load metric like EER cooling, these shall be increased by the percentage shown.
Air economizer systems shall be capable of and configured to modulate outdoor air and return air dampers to provide up to 100 percent of the design supply air quantity as outdoor air for cooling. [ASHRAE 90.1:6.5.1.1.1]
Economizer controls shall be capable of and configured to sequence the dampers with the mechanical cooling equipment and shall not be controlled by only mixed air temperature.

Exception: The use of mixed air temperature limit control shall be permitted for systems controlled from space temperature (such as single-zone systems). [ASHRAE 90.1:6.5.1.1.2]
Air economizers shall be capable of and configured to automatically reduce outdoor air intake to the design minimum outdoor air quantity where outdoor air intake will no longer reduce cooling energy use. High-limit shutoff control types and associated set-points for specific climate zones shall be chosen from Table E503.5.1.2. [ASHRAE 90.1:6.5.1.1.3]

TABLE E503.5.1.2
HIGH-LIMIT SHUTOFF CONTROL SETTINGS FOR AIR ECONOMIZERS2
[ASHRAE 90.1:TABLE 6.5.1.1.3]
CONTROL TYPE ALLOWED ONLY IN CLIMATE ZONE AT LISTED SETPOINT REQUIRED HIGH LIMIT (ECONOMIZER OFF WHERE):
EQUATION DESCRIPTION
Fixed dry bulb temperature 0B, 1B, 2B, 3B, 3C, 4B, 4C, 5B, 5C, 6B, 7, 8 T > 75°F Outdoor air temperature exceeds 75°F
5A, 6A T > 70°F Outdoor air temperature exceeds 70°F
0A, 1A, 2A, 3A, 4A T > 65°F Outdoor air temperature exceeds 65°F
Differential dry bulb temperature 0B, LB, 2B, 3B, 3C, 4B, 4C,
5A, 5B, 5C, 6A, 6B, 7, 8
T > T Outdoor air temperature exceeds return air temperature
Fixed enthalpy with fixed dry-bulb temperature All h > 28 Btu/lb1
or T > 75°F
Outdoor air enthalpy exceeds 28 Btu/lb1 of dry air1 or outdoor air temperature exceeds 75°F
Differential enthalpy with fixed dry-bulb temperature All h > h or
T > 75°F
Outdoor air enthalpy exceeds return air enthalpy or outdoor air temperature exceeds 75°F
For SI units: °C = (°F-32)/l.8, 1 British thermal unit per pound = 2326 J/kg
Notes:
  1. 1  At altitudes substantially different than sea level, the fixed enthalpy limit shall be set to the enthalpy value at 75°F (24°C) and 50 percent relative humidity.
    As an example, at approximately 6000 feet (1829 m) elevation, the fixed enthalpy limit shall be approximately 30.7 Btu/lb (71408 J/kg).
  2. 2  Devices with selectable rather than adjustable setpoints shall be capable of being set to within 2°F (1°C) and 2 Btu/lb (4649 J/kg) of the setpoint listed.
Return air, exhaust or relief, and outdoor air dampers shall comply with Section E503.4.6.4.2. [ASHRAE 90.1:6.5.1.1.4]
Systems shall provide a means to relieve excess outdoor air during air economizer operation to prevent overpressurizing the building. The relief air outlet shall be located to avoid recirculation into the building. [ASHRAE 90.1:6.5.1.1.5]
Outdoor air, return air, mixed air, and supply air sensors shall be calibrated within the following accuracies:
  1. Dry-bulb and wet-bulb temperatures shall be accurate to ±2°F (1.1°C) over the range of 40°F (4.4°C) to 80°F (27°C).
  2. Enthalpy and the value of a differential enthalpy sensor shall be accurate to ±3 Btu/lb (7 E+03 J/kg) over the range of 20 Btu/lb (4.6 E+04 J/kg) to 36 Btu/lb (8.4 E+04 J/kg).
  3. Relative humidity shall be accurate to ±5 percent over the range of 20 percent to 80 percent relative humidity. [ASHRAE 90.1:6.5.1.1.6]
Fluid economizer systems shall be capable of providing up to 100 percent of the expected system cooling load at outdoor air temperatures of not more than 50°F (10°C) dry bulb or 45°F (7°C) wet bulb.

Exceptions:
  1. Systems primarily serving computer rooms in which 100 percent of the expected system cooling load at the dry bulb and wet bulb temperatures in accordance with Table E503.5.2 is met with water-cooled fluid economizers.
  2. Systems primarily serving computer rooms in which 100 percent of the expected system cooling load at the dry bulb temperatures listed in Table E503.5.2 is met with air-cooled fluid economizers.
  3. Systems where dehumidification requirements are not capable of being met using outdoor air temperatures of 50°F (10°C) dry bulb or 45°F (7°C) wet bulb and where 100 percent of the expected system cooling load at 45°F (7°C) dry bulb or 40°F (4°C) wet bulb is met with water-cooled fluid economizers. [ASHRAE 90.1:6.5.1.2.1]
TABLE E503.5.2
WATER ECONOMIZER SIZING DRY-BULB AND WET-BULB REQUIREMENTS FOR COMPUTER ROOMS*
[ASHRAE 90.1:TABLE 6.5.1.2.1]
CLIMATE ZONE WATER COOLED AIR COOLED
DRY BULB, °F WET BULB, °F DRY BULB, °F
0 A NR NR NR
0 B NR NR NR
1 A NR NR NR
1 B NR 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
For SI units: °C = (°F-32)/1.8
NR = Not Required
Precooling coils and fluid-to-water heat exchangers used as part of a fluid economizer system shall either have a water-side pressure drop of less than 15 feet of water (45 kPa), or a secondary loop shall be created so that the coil or heat exchanger pressure drop is not seen by the circulating pumps where the system is in the normal cooling (non-economizer) mode. [ASHRAE 90.1:6.5.1.2.2]
Economizer systems shall be integrated with the mechanical cooling system and be capable of and configured to provide partial cooling even where additional mechanical cooling is required to be in accordance with the remainder of the cooling load. Controls shall not false load the mechanical cooling systems by limiting or disabling the economizer or by other means, such as hot gas bypass, except at the lowest stage of mechanical cooling.

     Units that include an air economizer shall comply with the following:
  1. Unit controls shall have the mechanical cooling capacity control interlocked with the air economizer controls such that the outdoor air damper is at the 100 percent open position when mechanical cooling is on, and the outdoor air damper does not begin to close to prevent coil freezing due to minimum compressor run time until the leaving air temperature is less than 45°F (7°C).
  2. DX units with a rated capacity no less than 65 000 Btu/h (18 kW) that control the capacity of the mechanical cooling directly based on occupied space temperature shall have not less than two stages of mechanical cooling capacity
  3. Other DX units, including those that control space temperature by modulating the airflow to the space, shall comply with the requirements of Table E503.5.3. [ASHRAE 90.1:6.5.1.3]
TABLE E503.5.3
DX COOLING STAGE REQUIREMENTS FOR MODULATING AIRFLOW UNITS
[ASHRAE 90.1:6.5.1.3]
RATING CAPACITY, Btu/h MINIMUM NUMBER OF MECHANICAL COOLING STAGES MINIMUM COMPRESSOR DISPLACEMENT*
≥65000 and <240000 3 ≤35% of full load
≥240000 4 ≤25% full load
For SI units: 1000 British thermal units = 0.293 kW
*  For mechanical cooling stage control that does not use variable compressor displacement the percent displacement shall be equivalent to the mechanical cooling capacity reduction evaluated at the full load rating conditions for the compressor.
HVAC system design and economizer controls shall be such that economizer operation does not increase the building heating energy use during normal operation.

Exception: Economizers on variable air valve (VAV) systems that cause zone level heating to increase due to a reduction in supply air temperature. [ASHRAE 90.1:6.5.1.4]
Systems with hydronic cooling and humidification systems designed to maintain inside humidity at a dew-point temperature more than 35°F (2°C) shall use a fluid economizer where an economizer is required in accordance with Section E503.5 through Section E503.5.4.1. [ASHRAE 90.1:6.5.1.5]
Zone thermostatic controls shall prevent the following:
  1. Reheating.
  2. Recooling.
  3. Mixing or simultaneously supplying air that has been previously mechanically heated and air that 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.
Exceptions:
  1. Zones for which the volume of air that is reheated, recooled, or mixed is less than the larger of the following:
    1. Twenty percent of the zone design peak supply for systems with DDC and 30 percent for other systems.
    2. The outdoor airflow rate required to be in accordance with the ventilation requirements of Chapter 4 or ASHRAE 62.1 for the zone.
    3. A higher rate that is capable of demonstrating, to the satisfaction of the Authority Having Jurisdiction, to reduce overall system annual energy usage by offsetting reheat or recool energy losses through a reduction in outdoor air intake for the system.
    4. The airflow rate required to be in accordance with applicable codes or accreditation standards, such as pressure relationships or minimum air change rates.
  2. Zones with DDC that comply with the following:
    1. The airflow rate in dead band between heating and cooling does not exceed the larger of the following:
      1. Twenty percent of the zone design peak supply rate.
      2. The outdoor airflow rate required to be in accordance with the ventilation requirements of Chapter 4 or ASHRAE 62.1 for the zone.
      3. A higher rate that is capable of demonstrating, to the satisfaction of the Authority Having Jurisdiction, to reduce overall system annual energy usage by offsetting reheat or recool energy losses through a reduction in outdoor air intake.
      4. The airflow rate required in accordance with applicable codes or accreditation standards, such as pressure relationships or minimum air change rates.
    2. The airflow rate that is reheated, recooled, or mixed shall be less than 50 percent of the zone design peak supply rate.
    3. The first stage of heating consists of modulating the zone supply air temperature setpoint up to a maximum setpoint while the airflow is maintained at the dead band flow rate.
    4. The second stage of heating consists of modulating the airflow rate from the dead band flow rate up to the heating maximum flow rate.
  3. Laboratory exhaust systems in accordance with Section E503.5.11.3.
  4. Zones where not less than 75 percent of the energy for reheating or for providing warm air in mixing systems is provided from a site-recovered (including condenser heat) or site-solar energy source. [ASHRAE 90.1:6.5.2.1]
Where reheating is permitted in accordance with this appendix, zones that have both supply and return or exhaust air openings more than 6 feet (1829 mm) above the floor shall not supply heating air more than 20°F (11°C) above the space temperature setpoint.

Exceptions:
  1. Laboratory exhaust systems in accordance with Section E503.5.11.3.
  2. During preoccupancy building warm-up and setback. [ASHRAE 90.1:6.5.2.1.1]
The heating of fluids in hydronic systems that have been previously mechanically cooled and the cooling of fluids that have been previously mechanically heated shall be limited in accordance with Section E503.5.5.2.1 through Section E503.5.5.2.3. [ASHRAE 90.1:6.5.2.2]
Hydronic systems that use a common return system for both hot water and chilled water shall not be used. [ASHRAE 90.1:6.5.2.2.1]
Systems that use a common distribution system to supply both heated and chilled water are acceptable where in accordance with the following:
  1. The system is designed to allow a dead band between changeover from one mode to the other of not less than 15°F (8°C) outdoor air temperature.
  2. The system is designed to operate and is provided with controls that will allow operation in one mode for not less than 4 hours before changing over to the other mode.
  3. Reset controls are provided that allow heating and cooling supply temperatures at the changeover point to be not more than 30°F (17°C) apart. [ASHRAE 90.1:6.5.2.2.2]
Hydronic heat pumps connected to a common heat pump water loop with 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 and configured to provide a heat pump water supply temperature dead band of not less than 20°F (11°C) between initiation of heat rejection and heat addition by the central devices (e.g., tower and boiler).
  2. For climate zone 3 through zone 8, where a closed-circuit tower (fluid cooler) is used, either an automatic valve shall be installed to bypass all but a minimal flow of water around the tower (for freeze protection) or low-leak age positive closure dampers shall be provided. Where an open-circuit tower is used directly in the heat pump loop, an automatic valve shall be installed to bypass heat pump water flow around the tower. Where an open-circuit tower is used in conjunction with a separate heat exchanger to isolate the tower from the heat pump loop, then heat loss shall be controlled by shutting down the circulation pump on the cooling tower loop.
Exception: Where a system loop temperature optimization controller is used to determine the most efficient operating temperature based on real-time conditions of demand and capacity, dead bands of less than 20°F (11°C) shall be permitted. [ASHRAE 90.1:6.5.2.2.3]
Where humidity controls are provided, such controls shall prevent reheating, mixing of hot and cold airstreams, or other means of simultaneous heating and cooling of the same airstream.

Exceptions:
  1. The system is capable of and configured to reduce supply air volume to 50 percent or less of the design airflow rate or the minimum outdoor air ventilation rate in accordance with ASHRAE 62.1 or other applicable federal, state, or local code or recognized standard, whichever is larger before simultaneous heating and cooling takes place.
  2. The individual fan cooling unit has a design cooling capacity of not more than 65000 Btu/h (19 kW) and is capable of and configured to unload to 50 percent capacity before simultaneous heating and cooling takes place.
  3. The individual mechanical cooling unit has a design cooling capacity of not more than 40000 Btu/h (11.7 kW). An individual mechanical cooling unit is a single system composed of a fan or fans and a cooling coil capable of providing mechanical cooling.
  4. Systems serving spaces where specific humidity levels are required to satisfy process needs, such as vivariums, museums, surgical suites, pharmacies, and buildings with refrigerating systems, such as supermarkets, refrigerated warehouses, and ice arenas, and where the building includes site-recovered energy or site solar energy that provide energy equal to 75 percent or more of the annual energy for reheating or for providing warm air in mixing systems. This exception shall not apply to computer rooms.
  5. Not less than 90 percent of the annual energy for reheating or for providing warm air in mixing systems is provided from site-recovered energy (including condenser heat) or site-solar energy.
  6. Systems where the heat added to the airstream is the result of the use of a desiccant system and 75 percent of the heat added by the desiccant system is removed by a heat exchanger, either before or after the desiccant system with energy recovery. [ASHRAE 90.1:6.5.2.3]
Humidifiers with preheating jackets mounted in the airstream shall be provided with an automatic valve to shut off preheat where humidification is not required. [ASHRAE 90.1:6.5.2.4.1]
Humidification system dispersion tube hot surfaces in the airstreams of ducts or air-handling units shall be insulated with a product with an insulating value of not less than R-0.5.

Exception: Systems where mechanical cooling, including economizer operation, does not occur simultaneously with humidification. [ASHRAE 90.1:6.5.2.4.2]
Preheat coils shall have controls that stop their heat output where mechanical cooling, including economizer operation, is occurring. [ASHRAE 90.1:6.5.2.5]
HVAC air system design and control shall be in accordance with the provisions of Section E503.5.6.1 through Section E503.5.6.6.
Each HVAC system having a total fan system motor nameplate horsepower (kW) exceeding 5 hp (3.7 kW) at fan system design conditions shall not exceed the allowable fan system motor nameplate horsepower (kW) (Option 1) or fan system brake horsepower (kW) (Option 2) as shown in Table E503.5.6.1(1). This shall include supply fans, return or relief fans, exhaust fans, and fan-powered terminal units associated with systems providing heating or cooling capability that operate at fan system design conditions. Single-zone VAV systems shall comply with the constant-volume fan power limitation.

Exceptions:
  1. Hospital, vivarium, and laboratory systems that utilize flow control devices on exhaust, return, or both to maintain space pressure relationships necessary for occupant health and safety, or environmental control shall be permitted to use variable-volume fan power limitation.
  2. Individual exhaust fans with motor nameplate horsepower of 1 hp (0.7 kW) or less. [ASHRAE 90.1:6.5.3.1.1]
TABLE E503.5.6.1(1)
FAN POWER LIMITATION*
[ASHRAE 90.1:TABLE 6.5.3.1-1]
LIMIT CONSTANT VOLUME VARIABLE VOLUME
Option 1: Fan system motor nameplate (hp) Allowable nameplate motor (hp) hpCFMs • 0.0011 hpCFMs • 0.0015
Option 2: Fan system (bhp) Allowable fan system (bhp) bhpCFMs • 0.00094 + A bhpCFMs • 0.0013 + A
For SI units: 1 horsepower = 0.746 kW, 1 cubic foot per minute = 0.00047 m3/s

* Where:
CFMs = the maximum design supply airflow rate to conditioned spaces served by the system in cubic feet per minute (m3/s)
hp = the maximum combined motor nameplate horsepower (kW)
bhp = the maximum combined fan brake horsepower (kW)
A = stun of(PD x CFMD/4131)
PD = each applicable pressure drop adjustment from Table E503.5.6.1(2) in inch water column(kPa)
CFMD = the design airflow through each applicable device from Table E503.5.6.1(2) in cubic feet per minute (m3/s)


TABLE E503.5.6.1(2)
FAN POWER LIMITATION PRESSURE DROP ADJUSTMENT
[ASHRAE 90.1:TABLE 6.5.3.1-2]
DEVICE ADJUSTMENT
CREDITS
Return or exhaust systems required by code or accreditation standards to be fully ducted, or systems required to maintain air pressure differentials between adjacent rooms 0.5 in. w.c. (2.15 in w.c. for laboratory and vivarium systems)
Return, exhaust, or both airflow control devices 0.5 in. w.c.
Exhaust filters, scrubbers, or other exhaust treatment The pressure drop of device calculated at fan system design condition
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 electronically enhanced filters Pressure drop calculated at 2x clean filter pressure drop at fan system design condition
Carbon and other gas-phase air cleaners Clean filter pressure drop at fan system design condition
Biosafety cabinet Pressure drop of device at fan system design condition
Energy recovery device, other than coil runaround loop For each airstream [(2.2 x enthalpy recovery ratio) - 0.5] in w.c.
Coil runaround loop 0.6 in. w.c. for each airstream
Evaporative humidifier or cooler in series with another cooling coil Pressure drop of device at fan system design condition
Sound attenuation section (fans serving spaces with design back-ground noise goals below NC35) 0.15 in. w.c.
Exhaust system serving fume hoods 0.35 in. w.c.
Laboratory and vivarium exhaust systems in high-rise buildings 0.25 in. w.c. per 100 feet of vertical duct exceeding 75 ft
DEDUCTIONS
Systems without central cooling device -0.6 in. WC
Systems without central heating device -0.3 in. WC
Systems with central electric resistance heat -0.2 in. WC
For SI units: 1 inch water column = 0.249 kPa, 1 foot = 304.8 mm
For each fan, the selected fan motor shall be not larger than the first available motor size more than the brake horsepower (bhp) (kW). The fan brake horsepower shall be indicated on the design documents to allow for compliance verification by the Authority Having Jurisdiction.

Exceptions:
  1. For fans less than 6 bhp (4.5 kW), where the first available motor larger than the bhp (kW) has a nameplate rating within 50 percent of the bhp (kW), the next larger nameplate motor size shall be selected.
  2. For fans 6 bhp (4.5 kW) and larger, where the first available motor larger than the bhp (kW) has a nameplate rating within 30 percent of the bhp (kW), the next larger nameplate motor size shall be selected.
  3. Systems that are in accordance with Section E503.5.6.1, Option 1.
  4. Fans with motor nameplate horsepower of less than 1 hp (0.7 kW). [ASHRAE 90.1:6.5.3.1.2]
Fans shall have a fan efficiency grade (FEG) of 67 or more, based on manufacturers' certified data in accordance with AMCA 205. The total efficiency of the fan at the design point of operation shall be within 15 percentage points of the maximum total efficiency of the fan.

Exceptions:
  1. Individual fans with a motor nameplate horsepower of 5 hp (3.7 kW) or less that are not part of a group operated as the functional equivalent of a single fan.
  2. Multiple fans in series or parallel (e.g., fan arrays) that have a combined motor nameplate horsepower of 5 hp (3.7 kW) or less and are operated as the functional equivalent of a single fan.
  3. Fans that are part of equipment listed under Section E503.4.
  4. Fans included in equipment bearing a third party-certified seal for air or energy performance of the equipment package.
  5. Powered wall/roof ventilators (PRV).
  6. Fans outside the scope of AMCA 205.
  7. Fans that are intended to only operate during emergency conditions. [ASHRAE 90.1:6.5.3.1.3]
Cooling systems listed in Table E503.5.6.2 shall be designed to vary the indoor fan airflow as a function of load and shall be in accordance with the following:
  1. DX and chilled-water cooling units that control the capacity of the mechanical cooling directly based on space temperature shall have a minimum of two stages of fan control. Low or minimum speed shall not exceed 66 percent of full speed. At low or minimum speed, the fan system shall draw no t more than 40 percent of the fan power at full fan speed. Low or minimum speed shall be used during periods of low cooling load and ventilation-only operation.
  2. Other units, including DX cooling units and chilled water units that control the space temperature by modulating the airflow to the space, shall have modulating fan control. Minimum speed shall not exceed 50 percent of full speed. At minimum speed, the fan system shall draw not more than 30 percent of the power at full fan speed. Low or minimum speed shall be used during periods of low cooling load and ventilation-only operation.
  3. Units that include an air-side economizer to comply with Section E503.5 through Section E503.5.4.1 shall have not less than of two speeds of fan control during economizer operation.
Exceptions:
  1. Modulating fan control shall not be required for chilled-water and evaporative cooling units with less than 1 hp (0.7 kW) fan motors where the units are not used to provide ventilation air and the indoor fan cycles with the load.
  2. Where the volume of outdoor air required to comply with the ventilation requirements of Chapter 4 or ASHRAE 62.1 at low speed exceeds the air that would be delivered at the speed defined in Section E503.5.6.2(1), or Section E503.5.6.2(2), then the minimum speed shall be selected to provide the required ventilation air. [ASHRAE 90.1:6.5.3.2.1]
TABLE E503.5.6.2
FAN AIRFLOW CONTROL
[ASHRAE 90.1:TABLE 6.5.3.2.1]
COOLING SYSTEM TYPE FAN MOTOR SIZE, (hp) MECHANICAL COOLING CAPACITY, (Btu/h)
DX cooling Any ≥65000
Chilled-water and evaporative cooling 1/4 Any
For SI units: 1000 British thermal units per hour = 0.293 kW, 1 horsepower = 0.746 kW, 1 cubic foot per minute = 0.00047 m3/s
Static pressure sensors used to control VAV fans shall be located such that the controller setpoint is not more than 1.2 inches water column (0.30 kPa). Where this results in the sensor being located downstream of major duct splits, sensors shall be installed in each major branch to ensure that static pressure is maintained in each.

Exception: Systems that are in accordance with Section E503.5.6.2.2. [ASHRAE 90.1:6.5.3.2.2]
For multiple-zone VAV systems having a total fan system motor nameplate horsepower exceeding 5 hp (3.7 kW) with DDC of individual zones reporting to the central control panel, static pressure setpoint shall be reset based on the zone requiring the most pressure, such as the setpoint is reset lower until one zone damper is nearly wide open. Controls shall provide the following:
  1. Monitor zone damper positions or other indicator of need for static pressure.
  2. Automatically detect those zones that are capable of excessively driving the reset logic and generate an alarm to the system operator.
  3. Readily allow operator removal of zones from the reset algorithm. [ASHRAE 90.1:6.5.3.2.3]
Multiple-zone VAV systems with DDC individual zone boxes reporting to a central control panel shall include a means to automatically reduce outdoor air intake flow below design rates in response to changes in system ventilation efficiency in accordance with ASHRAE 62.1.

Exceptions:
  1. VAV systems with zonal transfer fans that recirculate air from other zones without directly mixing it with outdoor air, dual-duct dual-fan VAV systems, and VAV systems with fan-powered terminal units.
  2. Systems where total design exhaust airflow is more than 70 percent of total design outdoor air intake flow requirements. [ASHRAE 90.1:6.5.3.3]
Multiple zone HVAC systems shall include controls that automatically reset the supply air temperature in response to representative building loads, or to outdoor air temperature. The controls shall reset the supply air temperature to not less than 25 percent of the difference between the design supply air temperature and the design room air temperature. Controls that adjust the reset based on zone humidity shall be permitted. Zones that are expected to experience relatively constant loads, such as electronic equipment rooms, shall be designed for the fully reset supply temperature.

Exceptions:
  1. Climate zones 0A, 1A, 2A, and 3A.
  2. Systems that prevent reheating, recooling, or mixing of heated and cooled supply air.
  3. Systems where not less than 75 percent of the energy for reheating, on an annual basis, is from site recovered or site solar energy sources. [ASHRAE 90.1:6.5.3.5]
Motors for fans that are1/12 hp (62.1 W) or more and less than 1 hp (0.7 kW) shall be electronically-commutated motors or shall have a motor efficiency of not less than 70 percent where rated in accordance with DOE 10 CFR 431. These motors shall also have the means to adjust motor speed for either balancing or remote control. Belt-driven fans shall be permitted to use sheave adjustments for airflow balancing in lieu of a varying motor speed.

Exceptions:
  1. Motors in the airstream within fan coils and terminal units that operate when providing heating to the space served.
  2. Motors installed in space conditioning equipment certified in accordance with Section E503.4 through Section E503.4.4.1.
  3. Motors shown in Table E503.5.6.5(1) or Table E503.5.6.5(2). [ASHRAE 90.1:6.5.3.6]
TABLE E503.5.6.5(1)
MINIMUM AVERAGE FULL-LOAD EFFICIENCY FOR POLYPHASE SMALL ELECTRIC MOTORS*
[ASHRAE 90.1:TABLE 10.8.3]
FULL-LOAD EFFICIENCY, %
NUMBER OF POLES OPEN MOTORS
2 4 6
SYNCHRONOUS SPEED (RPM) 3600 1800 1200
MOTOR HORSEPOWER EFFICIENCY, %
0.25 65.6 69.5 67.5
0.33 69.5 73.4 71.4
0.50 73.4 78.2 75.3
0.75 76.8 81.1 81.7
1 77.0 83.5 82.5
1.5 84.0 86.5 83.8
2 85.5 86.5 N/A
3 85.5 86.9 N/A
*  Average full-load efficiencies shall be established in accordance with 10 CFR 431.


TABLE E503.5.6.5(2)
MINIMUM AVERAGE FULL-LOAD EFFICIENCY FOR CAPACITOR-START CAPACITOR-RUN AND CAPACITOR-START INDUCTION-RUN SMALL ELECTRIC MOTORS*
[ASHRAE 90.1:TABLE 10.8-4]
FULL-LOAD EFFICIENCY, %
NUMBER OF POLES OPEN MOTORS
2 4 6
SYNCHRONOUS SPEED (RPM) 3600 1800 1200
MOTOR HORSEPOWER EFFICIENCY, %
0.25 66.6 68.5 62.2
0.33 70.5 72.4 66.6
0.50 72.4 76.2 76.2
0.75 76.2 81.8 80.2
1 80.4 82.6 81.1
1.5 81.5 83.8 N/A
2 82.9 84.5 N/A
3 84.1 N/A N/A
*  Average full-load efficiencies shall be established in accordance with 10 CFR 431.
The required minimum outdoor air rate is the larger of the minimum outdoor air rate or the minimum exhaust air rate required by ASHRAE 62.1, ASHRAE 170, or applicable codes or accreditation standards. Outdoor air ventilation systems shall comply with one of the following:
  1. Design minimum system outdoor air provided shall not exceed 135 percent of the required minimum outdoor air rate.
  2. Dampers, ductwork, and controls shall be provided that allow the system to supply no more than the required minimum outdoor air rate with a single setpoint adjustment.
  3. The system includes exhaust air energy recovery complying with Section E503.5.10. [ASHRAE 90.1:6.5.3.7]
Boiler systems with design input of 1000000 Btu/h (293 kW) or more shall comply with the turndown ratio in accordance with Table E503.5.7.

     The system turndown requirement shall use multiple single-input boilers, one or more modulating boilers, or a combination of single-input and modulating boilers.

     Boilers shall comply with the minimum efficiency requirements in Table E503.7.1(6). [ASHRAE 90.1:6.5.4.1]

TABLE E503.5.7
BOILER TURNDOWN
[ASHRAE 90.1:TABLE 6.5.4.1]
BOILER SYSTEM DESIGN INPUT, Btu/h MINIMUM TURNDOWN RATIO
≥ 1000000 and ≤5000000 3 to 1
>5000000 and ≤10000000 4 to 1
>10000000 5 to 1
For SI units: 1000 British thennal units per hour = 0.293 kW
Chilled- and hot-water distribution systems that include three or more control valves designed to modulate or step open and close as a function of load shall be designed for variable fluid flow and shall be capable of and configured to reduce pump flow rates to not more than the larger of 25 percent of the design flow rate or the minimum flow required by the heating/cooling equipment manufacturer for the proper operation of equipment. Individual or parallel pumps serving variable-flow heating-water or chilled-water systems, where the nameplate horsepower of the motor or combined parallel motors is not less than the power shown in Table E503.5.7.1, shall have controls or devices that will result in pump motor demand of not more than 30 percent of design wattage at 50 percent of design water flow. The controls or devices shall be controlled as a function of desired flow or to maintain a minimum required differential pressure. Differential pressure shall be measured at or near the most remote heat exchanger or the heat exchanger requiring the greatest differential pressure. The differential pressure setpoint shall not exceed 110 percent of that required to achieve design flow through the heat exchanger. Where differential pressure control is used to comply with this section, and DDC systems are used, the setpoint shall be reset downward based on valve positions until one valve is nearly wide open.

Exceptions:
  1. Differential pressure set-point reset is not required where valve position is used to comply with Section E503.5.7.3.
  2. Variable-pump flow control is not required on heating-water pumps where more than 50 percent of annual heat is generated by an electric boiler.
  3. Variable flow is not required for primary pumps in a primary/secondary system.
  4. Variable flow is not required for a coil pump provided for freeze protection.
  5. Variable flow is not required for heat recovery coil runaround loops. [ASHRAE 90.1:6.5.4.2]
TABLE E503.5.7.1
PUMP FLOW CONTROL REQUIREMENTS
[ASHRAE 90.1:TABLE 6.5.4.2]
CHILLED WATER PUMPS IN THESE CLIMATE ZONES HEATING WATER PUMPS IN THESE CLIMATE ZONES MOTOR NAMEPLATE HORSEPOWER
0A, 0B, 1A, 1B, 2B NR ≥2 hp
2A, 3B NR ≥3 hp
3A, 3C, 4A, 4B 7, 8 ≥5 hp
4C, 5A, 5B, 5C, 6A, 6B 3C, 5A, 5C, 6A, 6B ≥7.5 hp
- 4A, 4C, 5B ≥10 hp
7,8 4B ≥15 hp
- 2A, 2B, 3A, 3B ≥25 hp
- 1B ≥100 hp
- 0A, 0B, 1A ≥200 hp
For SI units: 1 horsepower = 0.746 kW
Where a chilled-water plant includes more than one chiller, provisions shall be made so that the fluid flow through the chiller is automatically shut off where the chiller is shut down. Chillers piped in series for the purpose of increased temperature differential, shall be considered as one chiller. Where constant-speed chilled-water or condenser water pumps are used to serve multiple chillers, the number of pumps shall be not less than the number of chillers and staged on and off with the chillers. [ASHRAE 90.1:6.5.4.3.1]
Where a boiler plant includes more than one boiler, provisions shall be made so that the flow through the boiler is automatically shut off where the boiler is shut down. Where constant-speed hotwater pumps are used to serve multiple boilers, the number of pumps shall be not less than the number of boilers and staged on and off with the boilers. [ASHRAE 90.1:6.5.4.3.2]
Chilled- and hotwater systems with a design capacity exceeding 300000 Btu/h (88 kW) supplying chilled or heated water (or both) to comfort conditioning systems shall include controls that automatically reset supply water temperatures by representative building loads (including return water temperature) or by outdoor air temperature. Where DDC is used to control valves, the set point shall be reset based on valve positions until one valve is nearly wide open or setpoint limits of the system equipment or application have been reached.

Exceptions:
  1. Where chilled-water supply is already cold, such as chilled water supplied from a district cooling or thermal energy storage system, such that blending would be required to achieve the reset chilled-water supply temperature.
  2. Where a specific temperature is required for a process.
  3. Water temperature reset is not required where valve position is used to comply with Section E503.5.7. [ASHRAE 90.1:6.5.4.4]
Hydronic heat pumps and water-cooled unitary air-conditioners shall have a two-position automatic valve interlocked to shut off water flow when the compressor is off.

Exception: Units employing water economizers. [ASHRAE 90.1:6.5.4.5.1]
Hydronic heat pumps and water-cooled unitary air-conditioners having a total pump system power exceeding 5 hp (3.7 kW) shall have controls, devices, or both (such as variable speed control) that will result in pump motor demand of not more than 30 percent of design wattage at 50 percent of design water flow. [ASHRAE 90.1:6.5.4.5.2]
Chilled-water and condenser-water piping shall be designed such that the design flow rate in a pipe segment does not exceed the values listed in Table E503.5.7.5 for the appropriate total annual hours of operation. Pipe size selections for systems that operate under variable flow conditions, such as modulating two-way control valves at coils, and that contain variable-speed pump motors shall be permitted to be made from the "Variable Flow/Variable Speed" columns. All others shall be made from the "Other" columns.

Exceptions:
  1. Design flow rates exceeding the values in Table E503.5.7.5 shall be permitted in specific sections of pipe where the pipe is not in the critical circuit at design conditions and is not predicted to be in the critical circuit during 30 percent or more of operating hours.
  2. Piping systems that have not more than the total pressure drop than the same system constructed with standard weight steel pipe with piping and fittings sized in accordance with Table E503.5.7.5. [ASHRAE 90.1:6.5.4.6]
TABLE E503.5.7.5
PIPING SYSTEM DESIGN MAXIMUM FLOW RATE (gallons per minute)
[ASHRAE 90.1:TABLE 6.5.4.6]
OPERATING HOURS/YEAR ≤2000 HOURS/YEAR >2000 AND ≤4400 HOURS/YEAR >4400 HOURS/YEAR
NOMINAL PIPE SIZE, (inches) OTHER VARIABLE FLOW/VARIABLE SPEED OTHER VARIABLE FLOW/VARIABLE SPEED OTHER VARIABLE FLOW/VARIABLE SPEED
21/2 120 180 85 130 68 110
3 180 270 140 210 110 170
4 350 530 260 400 210 320
5 410 620 310 470 250 370
6 740 1100 570 860 440 680
8 1200 1800 900 1400 700 1100
10 1800 2700 1300 2000 1000 1600
12 2500 3800 1900 2900 1500 2300
Maximum velocity for pipes over 14-24 inches in size 8.5 ft/s 13.0 ft/s 6.5 ft/s 9.5 ft/s 5.0 ft/s 7.5 ft/s
For SI units: 1 gallon per minute = 0.06 L/s, 1 foot per second= 0.3048 m/s, 1 inch = 25.4 mm
Section E503.5.8 through Section E503.5.9 apply to heat rejection equipment used in comfort cooling systems such as air-cooled condensers, dry coolers, open-circuit cooling towers, closed-circuit cooling towers, and evaporative condensers.

Exception: Heat rejection devices whose energy usage is included in the equipment efficiency ratings listed in Table E503.7.1(1) through Table E503.7.1(4). [ASHRAE 90.1:6.5.5.1]
The fan system on a heat-rejection device powered by an individual motor or an array of motors with a connected power, including the motor service factor, totaling 5 hp (3.7 kW) or more shall have controls and/or devices (such as variable-speed control) that shall result in fan motor demand of no more than 30 percent of design wattage at 50 percent of the design airflow and that shall automatically change the fan speed to control the leaving fluid temperature or condensing temperature or pressure of the heat rejection device.

Exceptions:
  1. Condenser fans serving multiple refrigerant circuits or fluid cooling circuits.
  2. Condenser fans serving flooded condensers. [ASHRAE 90.1:6.5.5.2.1]
Multicell heat rejection equipment with variable-speed fan drives shall:
  1. Operate the maximum number of fans allowed that comply with the manufacturer's requirements for all system components.
  2. Control all fans to the same fan speed required for the instantaneous cooling duty, as opposed to staged (on/off) operation. Minimum fan speed shall comply with the minimum allowable speed of the fan drive system per the manufacturer's recommendations. [ASHRAE 90.1:6.5.5.2.2]
Centrifugal fan open-circuit cooling towers with a combined rated capacity of 1100 gallons per minute (gpm) (69.39 L/s) or greater at 95°F (35°C) condenser water return, 85°F (29°C) condenser water supply, and 75°F (24°C) outdoor air wet-bulb temperature shall comply with the energy efficiency requirement for axial fan open-circuit cooling towers in accordance with Table E503.7.1(7).

Exception: Centrifugal open-circuit cooling towers that are ducted (inlet or discharge) or require external sound attenuation. [ASHRAE 90.1:6.5.5.3]
Open-circuit cooling towers used on water-cooled chiller systems that are configured with multiple- or variable-speed condenser water pumps shall be designed so that all open-circuit cooling tower cells can be run in parallel with the larger of the following:
  1. The flow that is produced by the smallest pump at its minimum expected flow rate.
  2. Fifty percent of the design flow for the cell. [ASHRAE 90.1:6.5.5.4]
Each fan system shall have an energy recovery system where the design supply fan airflow rate exceeds the value listed in Table E503.5.10(1) and Table E503.5.10(2), based on the climate zone and percentage of outdoor air at design airflow conditions. Table E503.5.10(1) shall be used for all ventilation systems that operate less than 8000 hours per year and Table E503.5.10(2) shall be used for all ventilation systems that operate 8000 or more hours per year.

     Energy recovery systems required by this section shall result in an enthalpy recovery ratio of not less than 50 percent. A fifty percent enthalpy recovery ratio shall mean a change in the enthalpy of the outdoor air supply equal to 50 percent of the difference between the outdoor air and entering exhaust air enthalpies at design conditions. Provision shall be provided to bypass or control the energy recovery system to permit air economizer operation in accordance with Section E503.5.1.

Exceptions:
  1. Laboratory systems that are in accordance with Section E503.5.11.3.
  2. Systems serving spaces that are not cooled and that are heated to less than 60°F (16°C).
  3. Where more than 60 percent of the outdoor air heating energy is provided from site-recovered energy or site-solar energy.
  4. Heating energy recovery in Climate Zones 0, 1, and 2.
  5. Cooling energy recovery in climate zones 3C, 4C, 5B, 5C, 6B, 7, and 8.
  6. Where the sum of the airflow rates exhausted and relieved within 20 feet (6096 mm) of each other is less than 75 percent of the design outdoor airflow rate, excluding exhaust air that is;
    1. used for another energy recovery system,
    2. not allowed by ASHRAE 170 for use in energy recovery systems with leakage potential, or
    3. of Class 4 as defined in ASHRAE 62.1.
  7. Systems requiring dehumidification that employ energy recovery in series with the cooling coil.
  8. Systems expected to operate less than 20 hours per week at the outdoor air percentage in accordance with Table E503.5.10(1). [ASHRAE 90.1:6.5.6.1]
TABLE E503.5.10(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]
CLIMATE ZONE PERCENT 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 (cubic feet per minute)
3B, 3C, 4B, 4C, 5B NR NR NR NR NR NR NR NR
0B, 1B, 2B, 5C NR NR NR NR ≥26000 ≥12000 ≥5000 ≥4000
6B ≥28000 ≥26500 ≥11000 ≥5500 ≥4500 ≥3500 ≥2500 ≥1500
0A, 1A, 2A, 3A, 4A, 5A, 6A ≥26000 ≥16000 ≥5500 ≥4500 ≥3500 ≥2000 ≥1000 ≥120
7, 8 ≥4500 ≥4000 ≥2500 ≥1000 ≥140 ≥120 ≥100 ≥80
For SI units: 1 cubic foot per minute = 0.00047 m3/s
* NR = Not Required


TABLE E503.5.10(2)
EXHAUST AIR ENERGY RECOVERY REQUIREMENTS FOR VENTILATION
SYSTEMS OPERATING NOT LESS THAN 8000 HOURS PER YEAR*
[ASHRAE 90.1:TABLE 6.5.6.1-2]
CLIMATE ZONE PERCENT 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 (cubic feet per minute)
3C NR NR NR NR NR NR NR NR
0B, 1B, 2B, 3B, 4C, 5C NR ≥19500 ≥9000 ≥5000 ≥4000 ≥3000 ≥1500 ≥120
0A, 1A, 2A, 3A, 4B, 5B ≥2500 ≥2000 ≥1000 ≥500 ≥140 ≥120 ≥100 ≥80
4A, 5A, 6A, 6B, 7, 8 ≥200 ≥130 ≥100 ≥80 ≥70 ≥60 ≥50 ≥40
For SI units: 1 cubic foot per minute = 0.00047 m3/s
* NR = Not Required
Condenser heat recovery systems shall be installed for the heating or preheating of service hot water where the following conditions exist:
  1. The facility operates 24 hours a day.
  2. The total installed heat rejection capacity of the water-cooled system is more than 6000000 Btu/h (1757 kW) of heat rejection.
  3. The design service water heating load is more than 1000000 Btu/h (293 kW). [ASHRAE 90.1:6.5.6.2.1]
The required heat recovery system shall have the capacity to provide the smaller of:
  1. Sixty percent of the peak heat rejection load at design conditions.
  2. Preheat of the peak service hot water draw to 85°F (29°C).
Exceptions:
  1. Facilities that employ condenser heat recovery for space heating with a heat recovery design of more than 30 percent of the peak water-cooled condenser load at design conditions.
  2. Facilities that provide 60 percent of their service water heating from site-solar, site-recovered energy, or from other sources. [ASHRAE 90.1:6.5.6.2.2]
Exhaust systems shall comply with Section E503.5.11.1 through Section E503.5.11.3.
Replacement air introduced directly into the hood cavity of kitchen exhaust hoods shall not exceed 10 percent of the hood exhaust airflow rate. [ASHRAE 90.1:6.5.7.2.1]
Conditioned supply air delivered to a space with a kitchen hood shall not exceed the greater of the following:
  1. The supply flow required to be in accordance with the space heating or cooling load.
  2. The hood exhaust flow minus the available transfer air from adjacent spaces. Available transfer air is that portion of outdoor ventilation air not required to satisfy other exhaust needs, such as restrooms, and not required to maintain pressurization of adjacent spaces. [ASHRAE 90.1:6.5.7.1.2]
Where a kitchen or dining facility has a total kitchen hood exhaust airflow rate exceeding 5000 ft3/min (2.3597 m3/s), each hood shall have an exhaust rate in accordance with Table E503.5.11.2. Where a single hood, or hood section, is installed over appliances with different duty ratings, the maximum allowable flow rate for the hood or hood section shall not exceed the values in Table E503.5.11.2 for the highest appliance duty rating under the hood or hood section. Refer to ASHRAE 154 for definitions of hood type, appliance duty, and net exhaust flow rate.

Exception: Seventy-five percent or more of the total replacement air is transfer air that would otherwise be exhausted. [ASHRAE 90.1:6.5.7.2.2]


TABLE E503.5.11.2
MAXIMUM NET EXHAUST FLOW RATE, CFM PER LINEAR FOOT OF HOOD LENGTH
[ASHRAE 90.1:TABLE 6.5.7.2.2]
TYPE OF HOOD LIGHT DUTY EQUIPMENT MEDIUM DUTY EQUIPMENT HEAVY DUTY EQUIPMENT EXTRA HEAVY DUTY EQUIPMENT
Wall-mounted canopy 140 210 280 385
Single island 280 350 420 490
Double island (per side) 175 210 280 385
Eyebrow 175 175 Not allowed Not allowed
Backshelf/ Pass-over 210 210 280 Not allowed
For SI units: 1 foot = 304.8 mm, 1 cubic foot per minute = 0.00047 m3/s
Where a kitchen or dining facility has a total kitchen hood exhaust airflow rate more than 5000 ft3/min (2.3597 m3/s), then one of the following shall be provided:
  1. Fifty percent or more of all replacement air is transfer air that would otherwise be exhausted.
  2. Demand ventilation systems on 75 percent or more of the exhaust air. Such systems shall be capable of and configured to provide 50 percent or more reduction in exhaust and replacement air system airflow rates, including controls necessary to modulate airflow in response to appliance operation and to maintain full capture and containment of smoke, effluent, and combustion products during cooking and idle.
  3. Listed energy recovery devices that result in a sensible energy recovery ratio of 40 percent or more on 50 percent or more of the total exhaust airflow. A 40 percent sensible energy recovery ratio shall mean a change in the dry-bulb temperature of the outdoor air supply equal to 40 percent of the difference between the outdoor air and entering exhaust air dry-bulb temperatures at design conditions. [ASHRAE 90.1:6.5.7.2.3]
An approved field test method shall be used to evaluate design air flow rates and demonstrate proper capture and containment performance of installed commercial kitchen exhaust systems. Where demand ventilation systems are utilized to be in accordance with Section E503.5.11.2.1, additional performance testing shall be provided to demonstrate proper capture and containment at minimum airflow. [ASHRAE 90.1:6.5.7.2.4]
Buildings with laboratory exhaust systems having a total exhaust rate of more than 5000 ft3/min (2.3597 m3/s) shall include not less than one of the following features:
  1. VAV laboratory exhaust and room supply systems capable of and configured to reduce exhaust and makeup airflow rates, incorporate a heat recovery system to precondition makeup air from laboratory exhaust, or both and shall be in accordance with the following:

    A+B•(E/M) ≥ 50% (Equation E503.5.11.3)

    Where:
    A = Percentage that the exhaust and makeup airflow rates are capable of being reduced from design conditions.
    B = Sensible energy recovery ratio.
    E = Exhaust airflow rate through the heat recovery device at design conditions.
    M = Makeup airflow rate of the system at design conditions.
  2. VAV laboratory exhaust and room supply systems that are required to have minimum circulation rates to be in accordance with the codes or accreditation standards shall be capable of and configured to reduce zone exhaust and makeup airflow rates to the regulated minimum circulation values, or the minimum required to maintain pressurization relationship requirements. Systems serving nonregulated zones shall be capable of and configured to reduce exhaust and makeup airflow rates to 50 percent of the zone design values, or the minimum required to maintain pressurization relationship requirements.
  3. Direct makeup (auxiliary) air supply of 75 percent or more of the exhaust airflow rate, heated not more than 2°F (1°C) below room setpoint, cooled to not less than 3°F (2°C) above room setpoint, no humidification added, and no simultaneous heating and cooling are used for dehumidification control. [ASHRAE 90.1:6.5.7.3]
Radiant heating shall be used when heating is required for unenclosed spaces.

Exception: Loading docks equipped with air curtains. [ASHRAE 90.1:6.5.8.1]
Radiant heating systems that are used as primary or supplemental enclosed space heating shall be in accordance with this appendix, including, but not limited to, the following:
  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 or thermal storage systems. [ASHRAE 90.1:6.5.8.2]
Cooling systems shall not use hot gas bypass or other evaporator pressure control systems unless the system is designed with multiple steps of unloading or continuous capacity modulation. The capacity of the hot gas bypass shall be limited as indicated in Table E503.5.13 for VAV units and single-zone VAV units. Hot-gas bypass shall not be used on constant-volume units. [ASHRAE 90.1:6.5.9]

TABLE E503.5.13
HOT GAS BYPASS LIMITATION
[ASHRAE 90.1:TABLE 6.5.9]
RATED CAPACITY MAXIMUM HOT GAS BYPASS (percent of total capacity)
≤240000 Btu/h 15%
>240000 Btu/h 10%
For SI units: 1000 British thermal units per hour = 0.293 kW
Conditioned spaces with doors, including doors with more than one-half glass, opening to the outdoors shall be provided with controls that when any such door is open, the following shall occur:
  1. Disable mechanical heating or reset the heating setpoint to 55°F (13°C) or lower within five minutes of the door opening.
  2. Disable mechanical cooling or reset the cooling setpoint to 90°F (32°C) or more within five minutes of the door opening. Mechanical cooling shall be permitted to remain enabled where outdoor air temperature is less than the space temperature.
Exceptions:
  1. Building entries with automatic closing devices.
  2. Any space without a thermostat.
  3. Alterations to existing buildings.
  4. Loading docks. [ASHRAE 90.1:6.5.10]
The Authority Having Jurisdiction shall require submittal of compliance documentation and supplemental information in accordance with Section E503.6.1 through Section E503.6.3.
Compliance documents shall show the pertinent data and features of the building, equipment, and systems in sufficient detail to permit a determination of compliance by the building official and to indicate compliance with the requirements of this appendix. [ASHRAE 90.1:4.2.2.1]
Supplemental information necessary to verify compliance with this appendix, such as calculations, worksheets, compliance forms, vendor literature, or other data, shall be made available where required by the Authority Having Jurisdiction. [ASHRAE 90.1:4.2.2.2]
Operating and maintenance information shall be provided to the building owner. This information shall include, but not be limited to, the information specified in Section E503.6.3.1, Section E503.6.3.2, and Section E503.6.5.2. [ASHRAE 90.1:4.2.2.3]
Construction documents shall require that an operating manual and maintenance manual be provided to the building owner. The manuals shall include, at a minimum, the following:
  1. Submittal data stating equipment rating and selected options for each piece of equipment requiring maintenance.
  2. Operation manuals and maintenance manuals for each piece of equipment requiring maintenance. Required routine maintenance actions shall be clearly identified.
  3. Names and addresses of not less than one qualified service agency.
  4. A complete narrative of how each system is intended to operate.
     The Authority Having Jurisdiction shall only check to ensure that the construction documents required are provided to the owner, and shall not expect copies of any of the materials. [ASHRAE 90.1:8.7.2]
Construction documents shall require for all lighting equipment and lighting controls that an operating and maintenance manual be provided to the building owner or the designated representative of the building owner within 90 days after the date of system acceptance. These manuals shall include, at a minimum, the following:
  1. Submittal data indicating all selected options for each piece of lighting equipment, including but not limited to lamps, ballasts, drivers, and lighting controls.
  2. Operation and maintenance manuals for each piece of lighting equipment and lighting controls with routine maintenance clearly identified including, a s a minimum, a recommended relamping or cleaning program and a schedule for inspecting and recalibrating all lighting controls.
  3. A complete narrative of how each lighting control system is intended to operate including recommended settings. [ASHRAE 90.1:9.7.2.2]
Materials and equipment shall be labeled in a manner that will allow for determination of their compliance with the applicable provisions of this appendix. [ASHRAE 90.1:4.2.3]
Section E503.6.5.1 through Section E503.6.5.4.1 are mandatory provisions and are necessary to comply with this appendix. [ASHRAE 90.1:6.7.2]
Construction documents shall require that, within 90 days after the date of system acceptance, record drawings of the actual installation be provided to the building owner or the designated representative of the building owner. Record drawings shall include, as a minimum, the location and performance data on each piece of equipment, general configuration of duct and pipe distribution system including sizes, and the terminal air or water design flow rates. [ASHRAE 90.1:6.7.2.1]
Construction documents shall require that an operating manual and a maintenance manual be provided to the building owner or the designated representative of the building owner within 90 days after the date of system acceptance. These manuals shall be in accordance with industry-accepted standards and shall include, at a minimum, the following:
  1. Submittal data stating equipment size and selected options for each piece of equipment requiring maintenance.
  2. Operation manuals and maintenance manuals for each piece of equipment and system requiring maintenance, except equipment not furnished as part of the project. Required routine maintenance actions shall be clearly identified.
  3. Names and addresses of not less than one service agency.
  4. HVAC controls system maintenance and calibration information, including wiring diagrams, schematics, and control sequence descriptions. Desired or field-determined setpoints shall be permanently recorded on control drawings at control devices or, for digital control systems, in programming comments.
  5. A complete narrative of how each system is intended to operate, including suggested setpoints. [ASHRAE 90.1:6.7.2.2]
Construction documents shall require that HVAC systems be balanced in accordance with generally accepted engineering standards. Construction documents shall require that a written balance report be provided to the building owner or the designated representative of the building owner for HVAC systems serving zones with a total conditioned area exceeding 5000 square feet (464.52 m2). [ASHRAE 90.1:6.7.2.3.1]
Air systems shall be balanced in a manner to first minimize throttling losses. Then, for fans with fan system power greater than 1 hp (0.7 kW), fan speed shall be adjusted to meet design flow conditions. [ASHRAE 90.1:6.7.2.3.2]
Hydronic systems shall be proportionately balanced in a manner to first minimize throttling losses; then the pump impeller shall be trimmed or pump speed shall be adjusted to meet design flow conditions.

Exceptions: Impellers need not be trimmed nor pump speed adjusted.
  1. For pumps with pump motors of 10 hp (7.5 kW) or less.
  2. Where throttling results is not greater than 5 percent of the nameplate horsepower draw, or 3 hp (2.2 kW), whichever is greater, above that required where the impeller was trimmed. [ASHRAE 90.1:6.7.2.3.3]
HVAC control systems shall be tested to ensure that control elements are calibrated, adjusted, and in proper working condition. For projects larger than 50000 square feet (4645.15 m2) conditioned area, except warehouses and semiheated spaces, detailed instructions for commissioning HVAC systems shall be provided by the designer in plans and specifications. [ASHRAE 90.1:6.7.2.4]
Commissioning shall be performed for HVAC systems in accordance with Level 1, Basic Commissioning of the SMACNA HVAC Systems Commissioning Manual. (See Section E801.0 for additional information on HVAC system commissioning)
The minimum efficiency requirements for equipment shall comply with Section E503.7.1; duct insulation shall comply with Section E503.7.2, and pipe insulation shall comply with Section E503.7.3.
The minimum efficiency requirements for equipment shall comply with Table E503.7.1(1) through Table E503.7.1(16).

This section includes the certificate of acceptance forms referenced in Section E804.0 and Section E805.0.

TABLE E503.7.1(1)
ELECTRICALLY OPERATED UNITARY AIR CONDITIONERS AND CONDENSING UNITS MINIMUM EFFICIENCY REQUIREMENTS
[ASHRAE 90.1:TABLE 6.8.1-1]
EQUIPMENT TYPE SIZE CATEGORY HEATING SECTION TYPE SUBCATEGORY OR RATING CONDITION MINIMUM EFFICIENCY TEST PROCEDURE1
Air conditioners, air cooled <65000 Btu/h2 All Split system, three phase 13.0 SEER AHRI 210/240
Single package, three phase 14 SEER
Through the wall, air cooled ≤30000 Btu/h2 All Split system, three phase 12.0 SEER AHRI 210/240
Single package, three phase 12.0 SEER
Small duct, high velocity, air cooled <65000 Btu/h2 All Split system, three phase 11.0 SEER AHRI 210/240
Air conditioners, air cooled ≥65000 Btu/h and <135000 Btu/h Electric resistance (or none) Split system and single package 11.2 EER
12.9 IEER
AHRI 340/360
All other 11.0 EER
12.7 IEER
≥ 135000 Btu/h and <240000 Btu/h Electric resistance (or none) 11.0 EER
12.4 lEER
All other 10.8 EER
12.2 IEER
≥240000 Btu/h and <760000 Btu/h Electric resistance (or none) 10.0 EER
11.6 IEER
All other 9.8 EER
11.4 IEER
≥760000 Btu/h Electric resistance (or none) 9.7 EER
11.2 IEER
All other 9.5 EER
11.0 IEER
Air conditioners, water cooled <65000 Btu/h All Split system and single package 12.1 EER
12.3 IEER
AHRI 210/240
≥65000 Btu/h and <135000 Btu/h Electric resistance (or none) 12.1 EER
13.9 IEER
AHRI 340/360
All other 11.9 EER
13.7 IEER
≥135000 Btu/h and <240000 Btu/h Electric resistance (or none) 12.5 EER
13.9 IEER
All other 12.3 EER
13.7 IEER
≥240000 Btu/h and <760000 Btu/h Electric resistance (or none) 12.4 EER
13.6 IEER
All other 12.2 EER
13.4 IEER
≥760000 Btu/h Electric resistance (or none) 12.2 EER
13.5 IEER
All other 12.0 EER
13.3 IEER
Air conditioners,
evaporatively cooled
<65000 Btu/h2 All Split system and single package 12.1 EER
12.3 IEER
AHRI 210/240
≥65000 Btu/h and <135000 Btu/h Electric resistance (or none) 12.1 EER
12.3 IEER
AHRI 340/360
All other 11.9 EER
12.1 IEER
≥135000 Btu/h and <240000 Btu/h Electric resistance (or none) 12.0 EER
12.2 IERR
All other 11.8 EER
12.0 IEER
≥240000 Btu/h and <760000 Btu/h Electric resistance (or none) 11.9 EER
12.1 IEER
All other 11.7 EER
11.9 IEER
≥760000 Btu/h Electric resistance (or none) 11.7 EER
11.9 IEER
All other 11.5 EER
11.7 IEER
Condensing units, air cooled ≥135000 Btu/h - - 10.5 EER
11.8 IEER
AHRI 365
Condensing units, water cooled ≥135000 Btu/h - - 13.5 EER
14.0 IEER
AHRI 365
Condensing units, evaporatively cooled ≥135000 Btu/h - - 13.5 EER
14.0 IEER
AHRI 365
For SI units: 1000 British thermal units per hour = 0.293 kW
Notes:
    1. 1   ASHRAE 90.1 contains a complete specification of the referenced test procedure, including the referenced year version of the test procedure.
    2. 2   Single-phase, air-cooled air conditioners less than 65000 Btu/h (19 kW) are regulated by the U.S. Department of Energy Code of Federal Regulations 10 CFR 430. SEER values for single-phase products are set by the U.S. Department of Energy.


TABLE E503.7.1(2)
ELECTRICALLY OPERATED UNITARY AND APPLIED HEAT PUMPS MINIMUM EFFICIENCY REQUIREMENTS
[ASHRAE 90.1:TABLE 6.8.1-2]
EQUIPMENT TYPE SIZE CATEGORY HEATING SECTION TYPE SUBCATEGORY OR RATING CONDITION MINIMUM EFFICIENCY TEST
PROCEDURE1
Air cooled (cooling mode) <65000 Btu/h2 All Split system, three phase 14 SEER AHRI 210/240
Single package, three phase 14 SEER
Through the wall, air cooled (cooling mode) ≤30000 Btu/h2 All Split system, three phase 12.0 SEER AHRl 210/240
Single package, three phase 12.0 SEER
Small duct, high velocity, air cooled <65000 Btu/h2 All Split System, three phase 11.0 SEER AHRI 210/240
Air cooled (cooling mode) ≥65000 Btu/h and <135000 Btu/h Electric resistance (or none) Split system and single package 11.0 EER
12.2 IEER
AHRl 340/360
All other 10.8 EER
12.0 IEER
≥135000 Btu/h and <240000 Btu/h Electric resistance (or none) 10.6 EER
11.6 IEER
All other 10.4 EER
11.4 IEER
≥240000 Btu/h Electric resistance (or none) 9.5 EER
10.6 IEER
All other 9.3 EER
10.4 IEER
Water to air, water loop (cooling mode) <17000 Btu/h All 86°F entering water 12.2 EER ISO 13256-1
≥17000 Btu/h and <65000 Btu/h 13.0 EER
≥65000 Btu/h and
<135000 Btu/h
13.0 EER
Water to air, ground water (cooling mode) <135000 Btu/h All 59°F entering water 18.0 EER ISO 13256-1
Brine to air, ground loop (cooling mode) <135000 Btu/h All 77°F entering water 14.1 EER ISO 13256-1
Water to water, water loop (cooling mode) <135000 Btu/h All 86°F entering water 10.6 EER ISO 13256-2
Water to water,
ground water (cooling mode)
<135000 Btu/h All 59°F entering water 16.3 EER ISO 13256-2
Brine to water,
ground loop (cooling mode)
<135000 Btu/h All 77°F entering water 12.1 EER ISO 13256-2
Air cooled (heating mode) <65000 Btu/h2 (cooling capacity) - Split system, three phase 8.2 HSPF AHRI 210/240
Single package, three phase 8.0 HSPF
Through the wall, air cooled (heating
mode)
≤30000 Btu/h2 (cooling capacity) - Split system, three phase 7.4 HSPF AHRl 210/240
Single package, three phase 7.4 HSPF
Small duct high velocity, air cooled (heating mode) <65000 Btu/h2 - Split system, three phase 6.8 HSPF AHRl 210/240
Air cooled (heating mode) ≥65000 Btu/he and <135000 Btu/h (cooling capacity) - 4 7°F db/43°F wb outdoor air 3.3 COPH AHRI 340/360
17°F db/15°F wb outdoor air 2.25 COPH
≥135000 Btu/he (cooling capacity) 47°F db/43°F wb outdoor air 3.2 COPH
17°F db/15°F wb outdoor air 2.05 COPH
Water to air, water loop (heating mode) <135000 Btu/h (cooling capacity) - 68°F entering water 4.3 COPH ISO 13256-1
Water to air, groundwater
(heating mode)
<135000 Btu/h (cooling capacity) - 50°F entering water 3.7 COPH ISO 13256-1
Brine to air, ground loop (heating mode) <135000 Btu/h (cooling capacity) - 32°F entering fluid 3.2 COPH ISO 13256-1
Water to water, water loop (heating mode) <135000 Btu/h (cooling capacity) - 68°F entering water 3.7 COPH ISO 13256-2
Water to water, groundwater (heating mode) <135000 Btu/h (cooling capacity) - 50°F entering water 3.1 COPH ISO 13256-2
Brine to water, ground loop (heating mode) <135000 Btu/h (cooling capacity) - 32°F entering fluid 2.5 COPH ISO 13256-2
For SI units: 1000 British thermal units per hour = 0.293 kW, °C = (°F-32)/1.8
Notes:
  1. 1  ASHRAE 90.1 contains a complete specification of the referenced test procedure, including the referenced year version of the test procedure.
  2. 2  Single-phase, air-cooled heat pumps less than 65000 Btu/h (19 kW) are regulated by the U.S. Department of Energy Code of Federal Regulations 10 CFR 430. SEER and HSPF values for single-phase products are set by the U.S. Department of Energy.


TABLE E503.7.1(3)
WATER-CHILLING PACKAGES - MINIMUM EFFICIENCY REQUIREMENTS1, 2, 5
[ASHRAE 90.1: TABLE 6.8.1-3]
EQUIPMENT TYPE
SIZE CATEGORY UNITS PATH A PATH B TEST
PROCEDURE3
Air-cooled chillers <150 tons EER
(Btu/Wh)
≥10.100 FL ≥9.700 FL AHRI 550/590
≥13.700 IPLV.IP ≥15.800 IPLV.IP
≥150 tons ≥10.100 FL ≥9.700 FL
≥14.000 IPLV.IP ≥16.100 IPLV.IP
Air-cooled without condenser, electrically operated
All capacities EER
(Btu/Wh)
Air-cooled chillers without condenser must be rated with matching condensers and comply with air-cooled chiller efficiency requirements
AHRI 550/590
Water-cooled, electrically operated positive displacement <75 tons kW/ton ≤0.750 FL ≤0.780 FL AHRI 550/590
≤0.600 IPLV.IP ≤0.500 IPLV.IP
≥75 tons and <150 tons ≤0.720 FL ≤0.750 FL
≤0.560 IPLV.IP ≤0.490 IPLV.IP
≥150 tons and <300 tons ≤0.660 FL ≤0.680 FL
≤0.540 IPLV.IP ≤0.440 IPLV.IP
≥300 tons and <600 tons ≤0.610 FL ≤0.625 FL
≤0.520 IPLV.IP ≤0.410 IPLV.IP
≥600 tons ≤0.560 FL ≤0.585 FL
≤0.500 IPLV.IP ≤0.380 IPLV.IP
Water cooled, electrically operated centrifugal <150 tons kW/ton ≤0.610 FL ≤0.695 FL AHRI 550/590
≤0.550 IPLV.IP ≤0.440 IPLV.IP
≥150 tons and <300 tons ≤0.610 FL ≤0.635 FL
≤0.550 IPLV.IP ≤0.400 IPLV.IP
≥300 tons and <400 tons ≤0.560 FL ≤0.595 FL
≤0.520 IPLV.IP ≤0.390 IPLV.IP
≥400 tons and <600 tons ≤0.560 FL ≤0.585 FL
≤0.500 IPLV.IP ≤0.380 IPLV.IP
≥600 tons ≤0.560 FL ≤0.585 FL
≤0.500 IPLV.IP ≤0.380 IPLV.IP
Air-cooled absorption, single effect All capacities COP (W/W) ≥0.600 FL NA4 AHRI 560
Water-cooled absorption, single effect All capacities COP (W/W) ≥0.700 FL NA4 AHRI 560
Absorption double effect, indirect
fired
All capacities COP (W/W) ≥1.000 FL NA4 AHRI 560
≥1.050 IPLV.IP
Absorption double effect, direct fired All capacities COP (W/W) ≥1.000 FL NA4 AHRI 560
≥1.000 IPLV
For SI units: 1 metric ton = 1000 kg, 1000 British thermal units per hour = 0.293 kW
Notes:
  1. 1  The requirements for centrifugal chillers shall be adjusted for nonstandard rating conditions per Section E503.4.1 and are only applicable for the range of conditions listed there. The requirements for air-cooled, water-cooled positive displacement and absorption chillers are at standard rating conditions defined in the reference test procedure.
  2. 2  Both the full-load and IPLV.IP requirements must be met or exceeded to comply with this appendix. When there is a Path B, compliance can be with either Path A or Path B for any application.
  3. 3  ASHRAE 90.1 contains a complete specification of the referenced test procedure, including the referenced year version of the test procedure.
  4. 4  NA means the requirements are not applicable for Path B, and only Path A can be used for compliance.
  5. 5  FL is the full-load performance requirements, and IPLV.IP is for the part-load performance requirements.


TABLE E503.7.1(4)
ELECTRICALLY OPERATED PACKAGED TERMINAL AIR CONDITIONERS, PACKAGED TERMINAL HEAT PUMPS, SINGLE-PACKAGE VERTICAL AIR CONDITIONERS, SINGLE-PACKAGE VERTICAL HEAT PUMPS, ROOM AIR CONDITIONERS, AND ROOM AIR CONDITIONER HEAT PUMPS - MINIMUM EFFICIENCY REQUIREMENTS
[ASHRAE 90.1: TABLE 6.8.1-4]
EQUIPMENT TYPE SIZE CATEGORY (INPUT) SUBCATEGORY OR RATING
CONDITION
MINIMUM EFFICIENCY TEST
PROCEDURE1
PTAC (cooling mode) standard size All capacities 95° F db outdoor air 13.8 - (0.300 × Cap/1000)3
(before 1/1/2015)
AHRI 310/380
14.0 - (0.300 × Cap/1000)3
(as of 1/1/2015)
PTAC (cooling mode) nonstandard size1 All capacities 95° F db outdoor air 10.9 - (0.213 × Cap/1000)3 EER AHRI 310/380
PTHP (cooling mode) standard size All capacities 95° F db outdoor air 14.0 - (0.300 × Cap/1000)3 AHRI 310/380
PTHP (cooling mode) nonstandard size2 All capacities 95° F db outdoor air 10.8 - (0.213 × Cap/1000)3 EER AHRI 310/380
PTHP (heating mode) standard size All capacities - 3.7 - (0.052 × Cap/1000)3 COPH AHRI 310/380
PTHP (heating mode) nonstandard size2 All capacities - 2.9 - (0.026 × Cap/1000)3 COPH AHRI 310/380
SPVAC (cooling mode) <65,000 Btu/h 95°F db/75°F wb outdoor air 10.0 EER AHRI 390
≥65000 Btu/h and <135000 Btu/h 10.0 EER
≥135000 Btu/h and <240000 Btu/h 10.0 EER
SPVHP (cooling mode) <65000 Btu/h 95°F db/75°F wb outdoor air 10.0 EER AHRI 390
≥65000 Btu/h and <135000 Btu/h 10.0 EER
≥135000 Btu/h and <240000 Btu/h 10.0 EER
SPVHP (heating mode) <65000 Btu/h 47°F db/43°F wb outdoor air 3.0 COPH AHRI 390
≥65000 Btu/h and <135000 Btu/h 3.0 COPH
≥135000 Btu/h and <240000 Btu/h 3.0 COPH
Room air conditioners with louvered sides <6000 Btu/h - 9.7 SEER AHAM RAC-1
≥6000 Btu/h and <8000 Btu/h 9.7 SEER
≥8000 Btu/h and <14000 Btu/h 9.8 EER
≥14000 Btu/h and <20000 Btu/h 9.7 SEER
≥20000 Btu/h 8.5 EER
SPVAC (cooling mode), nonweatherized space constrained ≤30000 Btu/h 95°F db/75°F wb outdoor air 9.2 EER AHRI 390
>30000 Btu/h and ≤36000 Btu/h 9.0 EER
SPVHP (cooling mode), nonweatherized space constrained ≤30000 Btu/h 95°F db/75°F wb outdoor air 9.2 EER AHRI 390
>30000 Btu/h and ≤36000 Btu/h 9.0 EER
SPVHP (heating mode), nonweatherized space constrained ≤30000 Btu/h 47°F db/43°F wb outdoor air 3.0 COPH AHRI 390
>30000 Btu/h and ≤36000 Btu/h 3.0 COPH
Room air conditioners without louvered sides <8000 Btu/h - 9.0 EER AHAM RAC-1
≥8000 Btu/h and <20000 Btu/h - 8.5 EER
≥20000 Btu/h - 8.5 EER
Room air conditioner heat pumps with louvered sides <20000 Btu/h - 9.0 EER AHAM RAC-1
≥20000 Btu/h 8.5 EER
Room air conditioner heat pumps without louvered sides <14000 Btu/h - 8.5 EER AHAM RAC-1
≥14000 Btu/h 8.0 EER
Room air conditioner, casement only All capacities - 8.7 EER AHAM RAC-1
Room air conditioner, casement slider All capacities - 9.5 EER AHAM RAC-1
For SI units: 1000 British thermal units per hour = 0.293 kW, °C = (°F-32)/1.8
Notes:
  1. 1   ASHRAE 90.1 contains a complete specification of the referenced test procedure, including the referenced year version of the test procedure.
  2. 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 external wall 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 (0.432 m2).
  3. 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 the calculation. Where the unit's capacity is more than 15000 Btu/h (4.4 kW), use 15000 Btu/h (4.4 kW) in the calculation.


TABLE E503.7.1(5)
WARM-AIR FURNACES AND COMBINATION WARM-AIR FURNACES/AIR-CONDITIONING UNITS, WARM-AIR DUCT FURNACES, AND UNIT HEATERS - MINIMUM EFFICIENCY REQUIREMENTS
[ASHRAE 90.1: TABLE 6.8.1-5]
EQUIPMENT TYPE SIZE CATEGORY (INPUT) SUBCATEGORY OR
RATING CONDITION
MINIMUM
EFFICIENCY
TEST PROCEDURE1
Warm-air furnace, gas fired <225000 Btu/h Maximum capacity3 78% AFUE or
80% Et2, 4
DOE 10 CFR Part 430 or Section 2.39, Thermal Efficiency, CSA Z21.47
≥225000 Btu/h 80% Et4 Section 2.39, Thermal Efficiency, CSA Z21.47
Warm-air furnace, oil fired <225000 Btu/h Maximum capacity3 78% AFUE or
80% Et2, 4
DOE 10 CFR Part 430 or Section 42, Combustion, UL 727
≥225000 Btu/h 81% Et4 Section 42, Combustion, UL 727
Warm-air duct furnaces, gas fired All capacities Maximum capacity3 80% EC5 Section 2.10, Efficiency, CSA Z83.8
Warm-air unit heaters, gas fired All capacities Maximum capacity3 80% EC5, 6 Section 2.10, Efficiency, CSA Z83.8
Warm-air unit heaters, oil fired All capacities Maximum capacity3 80% EC5, 6 Section 40, Combustion, UL 731
For SI units: 1000 British thermal units per hour = 0.293 kW
Notes:
  1. 1   ASHRAE 90.1 contains a complete specification of the referenced test procedure, including the referenced year version of the test procedure.
  2. 2   Combination units not covered by the U.S. Department of Energy Code of Federal Regulations 10 CFR 430 [three-phase power or cooling capacity greater than or equal to 65000 Btu/h (19 kW)] may comply with either rating.
  3. 3   Compliance of multiple firing rate units shall be at the maximum firing rate.
  4. 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 air is drawn from the conditioned space.
  5. 5   Ec = combustion efficiency (100 percent less flue losses). See test procedure for detailed discussion.
  6. 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 E503.7.1(6)
GAS- AND OIL-FIRED BOILERS - MINIMUM EFFICIENCY REQUIREMENTS2, 3
[ASHRAE 90.1: TABLE 6.8.1-6]
EQUIPMENT TYPE1 SUBCATEGORY OR
RATING CONDITION
SIZE CATEGORY
(INPUT)
MINIMUM EFFICIENCY EFFICIENCY AS OF
3/2/2020
TEST PROCEDURE
Boilers, hot water Gas fired <300000 Btu/h6, 7 82% AFUE 82% AFUE 10 CFR Part 430
≥300000 Btu/h and
≤2500000 Btu/h4
80% Et 80% Et 10 CFR Part 431
>2500000 Btu/h1 82% Ec 82% Ec
Oil fired5 <300000 Btu/h7 84% AFUE 84% AFUE 10 CFR Part 430
≥300000 Btu/h and ≤2500000 Btu/h4 82% Et 82% Et 10 CFR Part 431
>2500000 Btu/h1 84% Ec 84% Ec
Boilers, steam Gas fired <300000 Btu/h7 80% AFUE 80% AFUE 10 CFR Part 430
Gas fired - all,
except natural draft
≥300000 Btu/h and ≤2500000 Btu/h4 79% Et 79% Et 10 CFR Part 430
>2500000 Btu/h1 79% Et 79% Et
Gas fired - natural
draft
≥300000 Btu/h and ≤2500000 Btu/h4 77% Et 79% Et
>2500000 Btu/h1 77% Et 79% Et
Oil fired5 <300000 Btu/h 82% AFUE 82% AFUE 10 CFR Part 430
≥300000 Btu/h and ≤2500000 Btu/h4 81% Et 81% Et 10 CFR Part 431
>2500000 Btu/h1 81% Et 81% Et
For SI units: 1000 British thermal units per hour = 0.293 kW
Notes:
  1. 1   These requirements apply to boilers with rated input of 8000000 Btu/h (2343 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. 2   Ec = combustion efficiency (100 percent less flue losses). See reference document for detailed information.
  3. 3   Et = thermal efficiency. See reference document for detailed information.
  4. 4    Maximum capacity - minimum and maximum ratings as provided for and allowed by the unit's controls.
  5. 5   Includes oil-fired (residual).
  6. 6   Boilers shall not be equipped with a constant burning pilot light.
  7. 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 incremental change in inferred heat load produces a corresponding incremental change in the temperature of the water supplied.


TABLE E503.7.1(7)
PERFORMANCE REQUIREMENTS FOR HEAT REJECTION EQUIPMENT MINIMUM EFFICIENCY REQUIREMENTS
[ASHRAE 90.1: TABLE 6.8.1-7]
EQUIPMENT TYPE TOTAL SYSTEM HEAT-REJECTION CAPACITY AT RATED CONDITIONS SUBCATEGORY OR RATING CONDITION8 PERFORMANCE
REQUIRED1, 2, 3, 6, 7
TEST PROCEDURE4, 5
Propeller or axial fan open-circuit
cooling towers
All 95°F entering water
85° F leaving water
75°F entering wb
≥40.2 gpm/hp CTI ATC-105 and
CTI STD-201 RS
Centrifugal fan open-circuit cooling towers All 95°F entering water
85°F leaving water
75°F entering wb
≥20.0 gpm/hp CTI ATC-105 and
CTI STD-201 RS
Propeller or axial fan closed-circuit
cooling towers
All 102°F entering water
90° F leaving water
75°F entering wb
≥16.1 gpm/hp CTI ATC-105S and
CTI STD-201 RS
Centrifugal closed-circuit cooling towers All 102°F entering water
90°F leaving water
75°F entering wb
≥7.0 gpm/hp CTI ATC-105S and
CTI STD-201 RS
Propeller or axial fan evaporative
condensers
All R-507A test fluid
165°F entering gas temperature
105°F condensing temperature
75°F entering wb
≥157000 Btu/h•hp CTI ATC-106
Propeller or axial fan evaporative condensers All Ammonia test fluid
140°F entering gas temperature
96.3°F condensing temperature
75°F entering wb
≥134000 Btu/h•hp CTI ATC-106
Centrifugal fan evaporative condensers All R-507A test fluid
165°F entering gas temperature
105°F condensing temperature
75°F entering wb
≥135000 Btu/h•hp CTI ATC-106
Centrifugal fan evaporative condensers All Ammonia test fluid
140°F entering gas temperature
96.3°F condensing temperature
75°F entering wb
≥110000 Btu/h•hp CTI ATC-106
Air cooled condensers All 125°F condensing temperature
190°F entering gas temperature
15°F subcooling
95°F entering db
≥176000 Btu/h•hp AHRI 460
For SI units: °C = (°F-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 = 0.746 kW
Notes:
  1. 1   For purposes of this table, open-circuit cooling tower performance is defined as the water flow rating of the tower at the thermal rating condition listed in Table E503.7.1(7) divided by the fan motor nameplate power.
  2. 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 E503.7.1(7) divided by the sum of the fan motor nameplate power and the integral spray pump motor nameplate power.
  3. 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. 4   ASHRAE 90.1 contains a complete specification of the referenced test procedure, including the referenced year version of the test procedure.
  5. 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. 6   All cooling towers shall comply with the minimum efficiency listed in the table for that specific type of tower with the capacity effect of any project-specific accessories and/or options included in the capacity of the cooling tower.
  7. 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. 8   Requirements 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 E503.7.1(8)
HEAT TRANSFER EQUIPMENT- MINIMUM EFFICIENCY REQUIREMENTS
[ASHRAE 90.1: TABLE 6.8.1-8]
EQUIPMENT TYPE SUBCATEGORY MINIMUM EFFICIENCY1 TEST PROCEDURE2
Liquid-to-liquid heat exchangers Plate type NR AHRI 400
Notes:
  1. 1   NR = No Requirement
  2. 2   ASHRAE 90.1 contains a complete specification of the referenced test procedure, including the referenced year version of the test procedure.
TABLE E503.7.1 (9)
ELECTRICALLY OPERATED VARIABLE-REFRIGERANT-FLOW AIR CONDITIONERS-MINIMUM EFFICIENCY REQUIREMENTS
[ASHRAE 90.1: TABLE 6.8.1-9]
EQUIPMENT TYPE SIZE CATEGORY HEATING SECTION
TYPE
SUBCATEGORY OR RATING
CONDITION
MINIMUM EFFICIENCY TEST PROCEDURE
VRF air conditioners,
air cooled
<65000 Btu/h All VRF multisplit system 13.0 SEER AHRI 1230
≥65000 Btu/h and
<135000 Btu/h
Electric resistance
(or none)
VRF multisplit system 11.2 EER
13.1 IEER
(before 1/1/2017)
15.5 IEER
(as of 1/1/2017)
≥135000 Btu/h and
<240000 Btu/h
Electric resistance
(or none)
VRF multisplit system 11.0 EER
12.9 IEER
(before 1/1/2017)
14.9 IEER
(as of 1/1/2017)
≥240000 Btu/h Electric resistance
(or none)
VRF multisplit system 10.0 EER
11.6 IEER
(before 1/1/2017)
13.9 IEER
(as of 1/1/2017)
For SI units: 1000 British thermal units per hour = 0.293 kW

TABLE E503.7.1(10)
ELECTRICALLY OPERATED VARIABLE-REFRIGERANT-FLOW AND APPLIED HEAT PUMPS - MINIMUM EFFICIENCY REQUIREMENTS
[ASHRAE 90.1: TABLE 6.8.1-10]
EQUIPMENT TYPE SIZE CATEGORY HEATING SECTION
TYPE
SUBCATEGORY OR
RATING CONDITION
MINIMUM EFFICIENCY TEST PROCEDURE
VRF air cooled (cooling mode) <65000 Btu/h All VRF multisplit system 13.0 SEER AHRI 1230
≥65000 Btu/h and
<135000 Btu/h
Electric resistance
(or none)
11.0 EER
12.9 IEER
(before 1/1/2017)
14.6 IEER
(as of 1/1/2017)
VRF multisplit system with heat recovery 10.8 EER
12.7 IEER
(before 1/1/2017)
14.4 IEER
(as of 1/1/2017)
≥135000 Btu/h and
<240000 Btu/h
VRF multisplit system 10.6 EER
12.3 IEER
(before 1/1/2017)
13.9 IEER
(as of 1/1/2017)
VRF multisplit system with heat recovery 10.4 EER
12.1 IEER
(before 1/1/2017)
13.7 IEER
(as of 1/1/2017)
≥240000 Btu/h VRF multisplit system 9.5 EER
11.0 IEER
(before 1/1/2017)
12.7 IEER
(as of 1/1/2017)
VRF multisplit system with heat recovery 9.3 EER
10.8 IEER
(before 1/1/2017)
12.5 IEER
(as of 1/1/2017)
VRF water source (cooling mode) <65000 Btu/h All VRF multisplit systems 86°F
entering water
12.0 EER
16.0 IEER
(as of 1/1/2018)
AHRI 1230
VRF multisplit systems with heat
recovery 86°F entering water
11.8 EER
15.8 IEER
(as of 1/1/2018)
≥65000 Btu/h and
<135000 Btu/h
VRF multisplit system 86°F
entering water
12.0 EER
16.0 IEER
(as of 1/1/2018)
VRF multisplit system with heat
recovery 86°F entering water
11.8 EER
15.8 IEER
(as of 1/1/2018)
≥135000 Btu/h and
<240000 Btu/h
VRF multisplit system 86°F
entering water
10.0 EER
14.0 IEER
(as of 1/1/2018)
VRF multisplit system with heat
recovery 86°F entering water
9.8 EER
13.8 IEER
(as of 1/1/2018)
≥240000 Btu/h VRF multisplit system 86°F
entering water
10.0 EER
(before 1/1/2018)
12.0 IEER
(as of 1/1/2018)
VRF multisplit system with heat
recovery 86°F entering water
9.8 EER
(before 1/1/2018)
11.8 IEER
(as of 1/1/2018)
VRF groundwater source (cooling mode)
<135000 Btu/h All VRF multisplit system with heat
recovery 59°F entering water
16.2 EER AHRI 1230
VRF multisplit system with heat
recovery 59°F entering water
16.0 EER
≥135000 Btu/h VRF multisplit system with heat
recovery 59°F entering water
13.8 EER
VRF multisplit system with heat
recovery 59°F entering water
13.6 EER
VRF ground source (cooling mode) <135000 Btu/h All VRF multisplit system 77°F
entering water
13.4 EER AHRI 1230
VRF multisplit system with heat
recovery 77°F entering water
13.2 EER
≥135000 Btu/h VRF multisplit system 77°F
entering water
11.0 EER
VRF multisplit system with heat
recovery 77°F entering water
10.8 EER
VRF Air cooled (heating mode) <65000 Btu/h
(cooling capacity)
- VRF Multisplit system 7.7 HSPF AHRI 1230
≥65000 Btu/h and
<135000 Btu/h
- VRF Multisplit system 47°F
db/43°F wb outdoor air
3.3 COPH
17°F db/15°F wb outdoor air 2.25 COPH
≥135000 Btu/h
(cooling capacity)
- VRF Multisplit system 47°F
db/43°F wb outdoor air
3.2 COPH
17°F db/15°F wb outdoor air 2.05 COPH
VRF Water source (heating mode) <65000 Btu/h
(cooling capacity)
- VRF multisplit system
68°F entering water
4.2 COPH
(before 1/1/2018)
4.3 COPH
(as of 1/1/2018)
AHRI 1230
≥65000 Btu/h and
<135000 Btu/h
(cooling capacity)
- VRF multisplit system
68°F entering water
4.2 COPH
(before 1/1/2018)
4.3 COPH
(as of 1/1/2018)
≥135000 Btu/h and
<240000 Btu/h
(cooling capacity)
- VRF multisplit system
68°F entering water
3.9 COPH
(before 1/1/2018)
4.0 COPH
(as of 1/1/2018)
≥240000 Btu/h
(cooling capacity)
- VRF multisplit system
68°F entering water
3.9 COPH
VRF Groundwater source (heating mode) <135000 Btu/h
(cooling capacity)
- VRF Multisplit system 50°F
entering water
3.6 COPH AHRI 1230
≥135000 Btu/h
(cooling capacity)
- VRF Multisplit system 50°F
entering water
3.3 COPH
VRF Ground source (heating mode) <135000 Btu/h
(cooling capacity)
- VRF Multisplit system 32°F
entering water
3.1 COPH AHRI 1230
≥135000 Btu/h
(cooling capacity)
- VRF Multisplit system 32°F
entering water
2.8 COPH
For SI units: 1000 British thermal units per hour = 0.293 kW, °C = (°F-32)/1.8

TABLE E503.7.1(11)
AIR CONDITIONERS AND CONDENSING UNITS SERVING COMPUTER ROOMS MINIMUM EFFICIENCY REQUIREMENTS
[ASHRAE 90.1: TABLE 6.8.1-11]
EQUIPMENT
TYPE
NET SENSIBLE
COOLING CAPACITY
STANDARD MODEL MINIMUM NET SENSIBLE COPc TEST PROCEDURE
RETURN AIR DRY-BULB TEMPERATURE/
DEW-POINT TEMPERATURE
CLASS 1 CLASS 2 CLASS 3
75°F/52°F 85°F/52°F 95°F/52°F
Air cooled <65000 Btu/h Downflow unit 2.30 AHRI 1360
Upflow unit-ducted 2.10
Upflow unit-nonducted 2.09
Horizontal-flow unit 2.45
≥65000 Btu/h and
<240000 Btu/h
Downflow unit 2.20
Upflow unit-ducted 2.05
Upflow unit-nonducted 1.99
Horizontal-flow unit 2.35
≥240000 Btu/h Downflow unit 2.00
Upflow unit-ducted 1.85
Upflow unit-nonducted 1.79
Horizontal-flow unit 2.15
Water cooled <65000 Btu/h Downflow unit 2.50 AHRI 1360
Upflow unit-ducted 2.30
Upflow unit-nonducted 2.25
Horizontal-flow unit 2.70
≥65000 Btu/h and
<240000 Btu/h
Downflow unit 2.40
Upflow unit-ducted 2.20
Upflow unit-nonducted 2.15
Horizontal-flow unit 2.60
≥240000 Btu/h Downflow unit 2.25
Upflow unit-ducted 2.10
Upflow unit-nonducted 2.05
Horizontal-flow unit 2.45
Water cooled with
fluid economizer
<65000 Btu/h Downflow unit 2.45 AHRI 1360
Upflow unit-ducted 2.25
Upflow unit-nonducted 2.20
Horizontal-flow unit 2.60
≥65000 Btu/h and
<240000 Btu/h
Downflow unit 2.35
Upflow unit-ducted 2.15
Upflow unit-nonducted 2.10
Horizontal-flow unit 2.55
≥240000 Btu/h Downflow unit 2.20
Upflow unit-ducted 2.05
Upflow unit-nonducted 2.00
Horizontal-flow unit 2.40
Glycol cooled <65000 Btu/h Downflow unit
2.30 AHRI 1360
Upflow unit-ducted 2.10
Upflow unit-nonducted 2.00
Horizontal-flow unit 2.40
≥65000 Btu/h and
<240000 Btu/h
Downflow unit 2.05
Upflow unit-ducted 1.85
Upflow unit-nonducted 1.85
Horizontal-flow unit 2.15
≥240000 Btu/h Downflow unit 1.95
Upflow unit-ducted 1.80
Upflow unit-nonducted 1.75
Horizontal-flow unit 2.10
Glycol cooled with
fluid economizer
<65000 Btu/h Downflow unit 2.25 AHRI 1360
Upflow unit-ducted 2.10
Upflow unit-nonducted 2.00
Horizontal-flow unit 2.35
≥65000 Btu/h and
<240000 Btu/h
Downflow unit 1.95
Upflow unit-ducted 1.80
Upflow unit-nonducted 1.75
Horizontal-flow unit 2.10
≥240000 Btu/h Downflow unit 1.90
Upflow unit-ducted 1.80
Upflow unit-nonducted 1.70
Horizontal-flow unit 2.10
For SI units: 1000 British thermal units per hour = 0.293 kW, °C = (°F-32)/1.8

TABLE E503.7.1(12)
COMMERCIAL REFRIGERATOR AND FREEZERS - MINIMUM EFFICIENCY REQUIREMENTS
[ASHRAE 90.1:TABLE 6.8.1-12]
EQUIPMENT TYPE APPLICATION ENERGY USE LIMITS, KWH/DAY* TEST PROCEDURE
Refrigerator with solid doors Holding temperature 0.10 x V + 2.04 AHRl 1200
Refrigerator with transparent doors Holding temperature 0.12 x V + 3.34 AHRl 1200
Freezers with solid doors Holding temperature 0.40 x V + 1.38 AHRl 1200
Freezers with transparent doors Holding temperature 0.75 x V + 4.10 AHRl 1200
Refrigerators/freezers with solid doors Holding temperature the greater of 0.12 x V + 3.34 or 0.70 AHRl 1200
Commercial refrigerators Pulldown 0.126 x V + 3.51 AHRl 1200
For SI units: 1000 British thermal units per hour per day = 0.293 kW/day
* V = the chiller or frozen compartment volume (ft3) as defined in Association of Home Appliance Manufacturers.


TABLE E503.7.1(13)
COMMERCIAL REFRIGERATION - MINIMUM EFFICIENCY REQUIREMENTS
[ASHRAE 90.1: TABLE 6.8.1-13]
EQUIPMENT TYPE ENERGY USE LIMITS2, 3 KWH/DAY TEST PROCEDURE
EQUIPMENT CLASS1 FAMILY CODE OPERATING MODE RATING TEMPERATURE
VOP.RC.M Vertical open Remote condensing Medium temperature 0.82 x TDA + 4.07 AHRI 1200
SVO.RC.M Semivertical open Remote condensing Medium temperature 0.83 x TDA + 3.18 AHRI 1200
HZO.RC.M Horizontal open Remote condensing Medium temperature 0.35 x TDA + 2.88 AHRI 1200
VOP.RC.L Vertical open Remote condensing Low temperature 2.27 x TDA + 6.85 AHRI 1200
HZO.RC.L Horizontal open Remote condensing Low temperature 0.57 x TDA + 6.88 AHRI 1200
VCT.RC.M Vertical transparent door Remote condensing Medium temperature 0.22 x TDA + 1.95 AHRI 1200
VCT.RC.L Vertical transparent door Remote condensing Low temperature 0.56 x TDA + 2.61 AHRI 1200
SOC.RC.M Service over counter Remote condensing Medium temperature 0.51 x TDA + 0.11 AHRI 1200
VOP.SC.M Vertical open Self contained Medium temperature 1.74 x TDA + 4.71 AHRI 1200
SVO.SC.M Semivertical open Self contained Medium temperature 1.73 x TDA + 4.59 AHRI 1200
HZO.SC.M Horizontal open Self contained Medium temperature 0.77 x TDA + 5.55 AHRI 1200
HZO.SC.L Horizontal open Self contained Low temperature 1.92 x TDA + 7.08 AHRI 1200
VCT.SC.I Vertical transparent door Self contained Ice cream 0.67 x TDA + 3.29 AHRI 1200
VCS.SC.I Vertical solid door Self contained Ice cream 0.38 x V + 0.88 AHRI 1200
HCT.SC.I Horizontal transparent door Self contained Ice cream 0.56 x TDA + 0.43 AHRI 1200
SVO.RC.L Semivertical open Remote condensing Low temperature 2.27 x TDA + 6.85 AHRI 1200
VOP.RC.I Vertical open Remote condensing Ice cream 2.89 x TDA + 8.7 AHRI 1200
SVO.RC.I Semivertical open Remote condensing Ice cream 2.89 x TDA + 8.7 AHRI 1200
HZO.RC.I Horizontal open Remote condensing Ice cream 0.72 x TDA + 8.74 AHRI 1200
VCT.RC.I Vertical transparent door Remote condensing Ice cream 0.66 x TDA + 3.05 AHRI 1200
HCT.RC.M Horizontal transparent door Remote condensing Medium temperature 0.16 x TDA + 0.13 AHRI 1200
HCT.RC.L Horizontal transparent door Remote condensing Low temperature 0.34 x TDA + 0.26 AHRI 1200
HCT.RC.I Horizontal transparent door Remote condensing Ice cream 0.4 x TDA + 0.31 AHRI 1200
VCS.RC.M Vertical solid door Remote condensing Medium temperature 0.11 x V + 0.26 AHRI 1200
VCS.RC.L Vertical solid door Remote condensing Low temperature 0.23 x V + 0.54 AHRI 1200
VCS.RC.I Vertical solid door Remote condensing Ice cream 0.27 x V + 0.63 AHRI 1200
HCS.RC.M Horizontal solid door Remote condensing Medium temperature 0.11 x V + 0.26 AHRI 1200
HCS.RC.L Horizontal solid door Remote condensing Low temperature 0.23 x V + 0.54 AHRI 1200
HCS.RC.I Horizontal solid door Remote condensing Ice cream 0.27 x V + 0.63 AHRI 1200
HCS.RC.I Horizontal solid door Remote condensing Ice cream 0.27 x V + 0.63 AHRI 1200
SOC.RC.L Service over counter Remote condensing Low temperature 1.08 x TDA + 0.22 AHRI 1200
SOC.RC.I Service over counter Remote condensing Ice cream 1.26 x TDA + 0.26 AHRI 1200
VOP.SC.L Vertical open Self contained Low temperature 4.37 x TDA + 11.82 AHRI 1200
VOP.SC.I Vertical open Self contained Ice cream 5.55 x TDA + 15.02 AHRI 1200
SVO.SC.L Semivertical open Self contained Low temperature 4.34 x TDA + 11.51 AHRI 1200
SVO.SC.I Semivertical open Self contained Ice cream 5.52 x TDA + 14.63 AHRI 1200
HZO.SC.I Horizontal open Self contained Ice cream 2.44 x TDA + 9.0 AHRI 1200
SOC.SC.I Service over counter Self contained Ice cream 1.76 x TDA + 0.36 AHRI 1200
HCS.SC.I Horizontal solid door Self contained Ice cream 0.38 x V + 0.88 AHRI 1200
For SI units: 1000 British thermal units per hour per day = 0.293 kW/day, °C = (°F-32)/1.8
Notes:
  1. 1 Equipment class designations consist of a combination [in sequential order separated by periods (AAA).(BB).(C)] of the following:
    1. (AAA)-An equipment 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).
    2. (BB)-An operating,node code (RC = remote condensing and SC = self contained).
    3. (C)-A rating temperature code (M = medium temperature [38°F], L = low temperature [0°F], or I = ice cream temperature [15°F]). For example, "VOP.RC.M" refers to the "vertical open, remote condensing, medium temperature" equipment class.
  2. 2 V is the volume of the case (ft) as measured in accordance with AHRI 1200.
  3. 3 TDA is the total display area of the case (ft) as measured in accordance with AHRI 1200.


TABLE E503.7.1(14)
VAPOR COMPRESSION BASED INDOOR POOL DEHUMIDIFIERS - MINIMUM EFFICIENCY REQUIREMENTS
[ASHRAE 90.1:TABLE 6.8.1-14]
EQUIPMENT TYPE SUBCATEGORY OR RATING CONDITION MINIMUM EFFICIENCY TEST PROCEDURE
Single package indoor*
(with or without economizer)
Rating Conditions: A, B, or C 3.5 MRE AHRI 910
Single package indoor water-cooled
(with or without economizer)
3.5 MRE
Single package indoor air-cooled
(with or without economizer)
3.5 MRE
Split system indoor air-cooled
(with or without economizer)
3.5 MRE
* Units without air-cooled condenser

TABLE E503.7.1(15)
ELECTRICALLY OPERATED DX-DOAS UNITS, SINGLE-PACKAGE AND REMOTE CONDENSER, WITHOUT ENERGY RECOVERY - MINIMUM EFFICIENCY REQUIREMENTS
[ASHRAE 90.1:TABLE 6.8.1-15]
EQUIPMENT TYPE SUBCATEGORY OR CONDITION MINIMUM EFFICIENCY TEST PROCEDURE
Air cooled
(dehumidification mode)
- 4.0 ISMRE AHRI 920
Air source heat pumps
(dehumidification mode)
- 4.0 ISMRE AHRI 920
Water cooled
(dehumidification mode)
Cooling tower condenser water 4.9 ISMRE AHRI 920
Chilled Water 6.0 ISMRE
Air source heat pump
(heating mode)
- 2.7 ISCOP AHRI 920
Water source heat pump
(dehumidification mode)
Ground source, closed loop 4.8 ISMRE AHRI 920
Ground-water source 5.0 ISMRE
Water source 4.0 ISMRE
Water source heat pump
(heating mode)
Ground source, closed loop 2.0 ISCOP AHRI 920
Ground-water source 3.2 ISCOP
Water source 3.5 ISCOP


TABLE E503.7.1(16)
ELECTRICALLY OPERATED DX-DOAS UNITS, SINGLE PACKAGE AND REMOTE CONDENSER, WITH ENERGY RECOVERY - MINIMUM EFFICIENCY REQUIREMENTS
[ASHRAE 90.1:TABLE 6.8.1-16]
EQUIPMENT TYPE SUBCATEGORY OR RATING CONDITION MINIMUM EFFICIENCY TEST PROCEDURE
Air cooled
(dehumidification mode)
- 5.2 ISMRE AHRI 920
Air source heat pumps
(dehumidification mode)
- 5.2 ISMRE AHRI 920
Water cooled
(dehumidification mode)
Cooling tower condenser water 5.3 ISMRE AHRI 920
Chilled Water 6.6 ISMRE
Air source heat pump
(heating mode)
- 3.3 ISCOP AHRI 920
Water source heat pump
(dehumidification mode)
Ground source, closed loop 5.2 ISMRE AHRI 920
Ground-water source 5.8 ISMRE
Water source 4.8 ISMRE
Water source heat pump
(heating mode)
Ground source, closed loop 3.8 ISCOP AHRI 920
Ground-water source 4.0 ISCOP
Water source 4.8 ISCOP
Duct insulation shall comply with Table E503.7.2.

TABLE E503.7.2
MINIMUM DUCT INSULATION R-VALUE1
[ASHRAE 90.1:TABLE 6.8.2]
CLIMATE ZONE DUCT LOCATION
EXTERIOR2 UNCONDITIONED SPACE AND BURIED DUCTS INDIRECTLY CONDITIONED SPACE3, 4
SUPPLY AND RETURN DUCTS FOR HEATING AND COOLING
0 to 4 R-8 R-6 R-1.9
5 to 8 R-12 R-6 R-1.9
SUPPLY AND RETURN DUCTS FOR HEATING ONLY
0 to 1 none none none
2 to 4 R-6 R-6 R-1.9
5 to 8 R-12 R-6 R-1.9
SUPPLY AND RETURN DUCTS FOR COOLING ONLY
0 to 6 R-8 R-6 R-1.9
7 to 8 R-1.9 R-1.9 R-1.9
Notes:
  1. 1   Insulation R-values, measured in [°F•h•ft2/(Btu•in)] [(m•K)/W], are for the insulation as installed and do not include film resistance. The required minimum thicknesses do not consider water vapor transmission and possible surface condensation. Where portions of the building envelope are used as a plenum enclosure, building envelope insulation shall be as required by the most restrictive condition of Section E503.4.7.1 or ASHRAE 90.1, depending on whether the plenum is located in the roof, wall, or floor. Insulation resistance measured on a horizontal plane in accordance with ASTM C518 at a mean temperature of 75°F (24°C) at the installed thickness.
  2. 2   Includes attics above insulated ceilings, parking garages and crawl spaces.
  3. 3   Includes return air plenums, with or without exposed roofs above.
  4. 4   Return ducts in this duct location do not require insulation.
Pipe insulation shall comply with Table E503.7.3(1) through Table E503.7.3(2).

TABLE E503.7.3(1)
MINIMUM PIPE INSULATION THICKNESS FOR HEATING AND HOT WATER SYSTEMS1, 2, 3, 4, 5
(STEAM, STEAM CONDENSATE, HOT WATER HEATING, AND DOMESTIC WATER SYSTEMS)
[ASHRAE 90.1:TABLE 6.8.3-1]
FLUID OPERATING TEMPERATURE RANGE (F°) AND USAGE INSULATION CONDUCTIVITY NOMINAL PIPE SIZE OR TUBE SIZE (inches)
CONDUCTIVITY Btu•inch/(h•ft2•°F) MEAN RATING TEMPERATURE °F <1 1 to < 11/2 11/2 to <4 4 to <8 ≥8
INSULATION THICKNESS (inches)
>350 0.32 - 0.34 250 4.5 5.0 5.0 5.0 5.0
251 - 350 0.29 - 0.32 200 3.0 4.0 4.5 4.5 4.5
201 - 250 0.27 - 0.30 150 2.5 2.5 2.5 3.0 3.0
141 - 200 0.25 - 0.29 125 1.5 1.5 2.0 2.0 2.0
105 - 140 0.22 - 0.28 100 1.0 1.0 1.5 1.5 1.5
For SI units: °C=(°F-32)/1.8, 1 inch = 25 mm, 1 British thermal unit inch per hour square foot degree Fahrenheit = [0.1 W/(m•K)]
Notes:
  1. 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•in/(h•ft2•°F)] [W/(m•K)].
    k = the upper value of the conductivity range listed in this table for the applicable fluid temperature.
  2. 2   These thicknesses shall be based on energy efficiency considerations only. Additional insulation shall be permitted to required relative to safety issues/surface temperature.
  3. 3   Piping 11/2 inches (40 mm) or less and located in partitions within conditioned spaces, reduction of insulation thickness by 1 inch (25.4 mm) shall be permitted before thickness adjustment required in footnote 1, but not a thickness less than 1 inch (25.4 mm).
  4. 4   For direct-buried heating and hot water system piping, reduction of insulation thickness by 11/2 inch (40 mm) shall be permitted before thickness adjustment required in footnote 1, but not a thickness less than 1 inch (25.4 mm).
  5. 5   Table E503.7.3(1) is based on steel pipe. Non-metallic pipes, less than schedule 80 thickness shall use the table values. For other non-metallic pipes having a thermal resistance more than that of steel pipe, reduced insulation thicknesses shall be permitted where documentation is provided showing that the pipe with the proposed insulation has less heat transfer per foot (mm) than a steel pipe of the same size with the insulation thickness shown in Table E503.7.3(1).


TABLE E503.7.3(2)
MINIMUM PIPE INSULATION THICKNESS FOR COOLING SYSTEMS (CHILLED WATER, BRINE, AND REFRIGERANT) 1, 2, 3, 4
[ASHRAE 90.1: TABLE 6.8.3-2]
INSULATION CONDUCTIVITY NOMINAL PIPE SIZE OR TUBE SIZE(inches)
FLUID OPERATING TEMPERATURE RANGE (°F) AND USAGE CONDUCTIVITY Btu•inch/(h•ft2•°F) MEAN RATING TEMPERATURE °F <1 1 to <11/2 11/2 to <4 4 to <8 >8
INSULATION THICKNESS(inches)
40°F - 60°F 021 - 0.27 75 0.5 0.5 1.0 1.0 1.0
<40°F 0.20 - 0.26 50 0.5 1.0 1.0 1.0 1.5
For SI units: °C = (°F-32)/1.8, 1 inch = 25 mm, 1 British thermal unit inch per hour square foot degree Fahrenheit = [0.1 W/m•K )]

Notes:
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•°F)] [W/(m•K)].
k = the upper value of the conductivity range listed in this table for the applicable fluid temperature.
2   These thicknesses shall be based on energy efficiency considerations only. Issues such as water, vapor permeability, or surface condensation require vapor retarders or additional insulation.
3   Insulation shall not be required for direct-buried cooling system piping.
4   Table E503.7.3(2) is based o n steel pipe. Non-metallic pipes less than schedule 80 thickness shall use the table values. For other non-metallic pipes having thermal resistance more than that of steel pipe, reduced insulation thicknesses shall be permitted where documentation is provided showing that the pipe with the proposed insulation has less heat transfer per foot (mm) than a steel pipe of the same size with the insulation thickness shown in Table E503.7.3(2).
HVAC systems serving heating, cooling, or ventilation needs of a computer room shall be in accordance with Section E503.1, Section E503.4, Section E503.8.1 or Section E503.8.2, Section E503.8.3, Section E502.7 through Section E502.7.2, and Section E503.7. [ASHRAE 90.1:6.6.1]
The computer room PUE1 shall be not more than the values listed in Table E503.8.1. Hourly simulation of the proposed design, for purposes of calculating PUE1, shall be in accordance with ASHRAE 90.1.

Exception: The compliance path shall not be permitted for a proposed computer room design utilizing a combined heat and power system. [ASHRAE 90.1:6.6.1.1]

TABLE E503.8.1
POWER USAGE EFFECTIVENESS (PUE) MAXIMUM
[ASHRAE 90.1:TABLE 6.6.1]
CLIMATE ZONE PUE*
0A 1.64
0B 1.62
1A 1.61
2A 1.49
3A 1.41
4A 1.36
5A 1.36
6A 1.34
1B 1.53
2B 1.45
3B 1.42
4B 1.38
5B 1.33
6B 1.33
3C 1.39
4C 1.38
5C 1.36
7 1.32
8 1.30
* PUEo and PUE1 shall not include energy for battery charging.
The computer room PUE0 shall be not more than the values listed in Table E503.8.1. The PUEo shall be the highest value determined at outdoor cooling design temperatures, and shall be limited to systems utilizing electricity for an energy source. The PUE0 shall be calculated for the following conditions:
  1. One hundred percent design IT equipment energy.
  2. Fifty percent design IT equipment energy. [ASHRAE 90.1:6.6.1.2]
Documentation on the following components shall be provided, including a breakdown of energy consumption or demand:
  1. IT equipment
  2. Power distribution losses external to the IT equipment
  3. HVAC systems
  4. Lighting [ASHRAE 90.1:6.6.1.3]
Solar energy systems shall be installed in accordance with the Uniform Solar Energy and Hydronics Code (USEHC).
Geothermal systems that use the earth or body of water as a heat source or sink for heating or cooling shall be in accordance with Section E505.1.1 through Section E509.2.
Geothermal systems shall be designed by a registered design professional. The geothermal system design, installation, and testing shall be in accordance with CSA C448.
Water source heat pumps used in conjunction with geothermal heat exchangers shall be listed and labeled for use in such systems and shall be designed for the minimum and maximum design water temperature.
Ground source heat pump ground-loop piping and tubing material for water-based systems shall comply with the standards cited in this appendix.
Piping shall be rated for the operating temperature and pressure of the ground source heat pump-loop system. Fittings shall be rated for the temperature and pressure applications and recommended by the manufacturer for installation with the piping material installed. Where used underground, materials shall be approved for burial.
The installation of used pipe, fittings, valves, and other materials shall not be permitted.
Ground source heat pump ground-loop pipe and tubing shall comply with the standards listed in Table E505.5.

TABLE E505.5
PLASTIC GROUND SOURCE LOOP PIPING
MATERIAL STANDARD
Chlorinated polyvinyl chloride (CPVC) ASTM D2846; ASTM F441; ASTM F442
Cross-linked polyethylene (PEX) ASTM F876; ASTM F877; CSA B137.5; NSF 358-3
Polyethylene/aluminum/polyethylene (PE-AL-PE) pressure pipe ASTM F1282; CSA B137.9
High Density Polyethylene (HDPE) ASTM D2737; ASTM D3035; ASTM F714; AWWAC901; CSA B137.1; CSA C448; NSF 358-1
Polypropylene (PP) ASTM F2389; CSA B137.11; NSF 358-2
Polyvinyl chloride (PVC) ASTM D1785; ASTM D2241
Polyethylene Raised Temperature (PE-RT) ASTM F2623; ASTM F2769
Fittings for ground source heat pump systems shall be approved for installation with the piping materials to be installed, and shall comply with the standards listed in Table E505.6.

TABLE E505.6
GROUND SOURCE LOOP PIPE FITTINGS
MATERIAL STANDARD
Chlorinated polyvinyl chloride (CPVC) ASTM D2846; ASTM F437; ASTM F438; ASTM F439; ASTM F1970; CSA B137.6
Cross-linked poly ethylene (PEX) ASTM F877; ASTM F1807; ASTM F1960; ASTM F2080; ASTM F2159; ASTM F2434; CSA B137.5; NSF 358-3
Polyethylene/aluminum/polyethylene (PE-AL-PE) ASTM F1282; ASTM F2434; CSA B137.9
High Density Poly ethylene (HDPE) ASTM D2683; ASTM D3261; ASTM F1055; CSA B137.1; CSA C448; NSF 358-1
Polypropylene (PP) ASTM F2389; CSA B137.11, NSF 358-2
Polyvinyl chloride (PVC) ASTM D2464; ASTM D2466; ASTM D2467; ASTM F1970; CSA B137.2; CSA B137.3
Poly ethylene Raised Temperature (PE-RT) ASTM D3261; ASTM F1807; ASTM F2159; ASTM F2769;
Joints and connections shall be of an approved type. Joints and connections shall be tight for the pressure of the ground source-loop system. Joints and fittings used underground shall be approved for buried applications.
Joints between various piping materials shall be made with approved transition fittings.
Pipe shall be cut square, reamed, and free of burrs and obstructions. Pipe ends shall have full-bore openings and shall not be undercut. CPVC, PE, and PVC pipe shall be chamfered.
Where required by Section E506.5 through Section E506.12.2, the preparation and installation of mechanical and thermoplastic-welded joints shall be in accordance with Section E506.4 and Section E506.5.
Mechanical joints shall be installed in accordance with the manufacturer's installation instructions.
Joint surfaces for thermoplastic welded joints shall be cleaned by an approved procedure. Joints shall be welded in accordance with the manufacturer's installation instructions.
Joints between CPVC plastic piping and fittings shall comply with Section E506.7.1 and Section E506.7.2.
Threads shall comply with ASME B1.20.1. Schedule 80 or heavier plastic pipe shall be threaded with dies specifically designed for plastic pipe. Thread lubricant, pipe-joint compound or tape shall be applied on the male threads only and shall be approved for application on the piping material.
Solvent cement joints for CPVC pipe and fittings shall be clean from dirt and moisture. Solvent cements in accordance with ASTM F493, requiring the use of a primer, shall be orange in color. The primer shall be colored and be in accordance with ASTM F656. Listed solvent cement in accordance with ASTM F493 that does not require the use of primers, yellow or red in color shall be permitted for pipe and fittings manufactured in accordance with ASTM D2846, 1/2 of an inch (15 mm) through 2 inches (50 mm) in diameter.
Compression or plastic to metal transition joints between cross-linked polyethylene plastic tubing and fittings shall comply with Section E506.8.1 and Section E506.8.2. Mechanical joints shall comply with Section E506.5.
Where compression-type fittings include inserts and ferrules or o-rings,the fittings shall be installed with the inserts and ferrules or o-rings.
Soldering on the metal portion of the system shall be performed not less than 18 inches (457 mm) from a plastic-to-metal adapter in the same water line.
Joints between polyethylene plastic piping shall comply with Section E506.9.1 through Section E506.9.3.
Joints shall be of the socket-fusion, saddle-fusion, or butt-fusion type and joined in accordance with ASTM D2657. Joint surfaces shall be clean and free of moisture. Joint surfaces shall be heated to melt temperatures and joined. The joint shall be undisturbed until cool. Fittings shall be manufactured in accordance with ASTM D2683 or ASTM D3261.
Joints shall be of the electrofusion type. Joint surfaces shall be clean and free of moisture, and scoured to expose virgin resin. Joint surfaces shall be heated to melt temperatures for the period of time specified by the manufacturer. The joint shall be undisturbed until cool. Fittings shall be manufactured in accordance with ASTM F1055.
Joint surfaces shall be clean and free of moisture. Pipe ends shall be chamfered and inserted into the fittings to full depth. Fittings shall be manufactured in accordance with ASTM F1924.
Joints between PP plastic pipe and fittings shall comply with Section E506.10.1 and Section E506.10.2.
Heat-fusion joints for polypropylene (PP) pipe and tubing joints shall be installed with socket-type heat-fused polypropylene fittings, electrofusion polypropylene fittings, or by butt fusion. Joint surfaces shall be clean and free from moisture. The joint shall be undisturbed until cool. Joints shall be made in accordance with ASTM F2389.
Mechanical and compression sleeve joints shall be installed in accordance with the manufacturer's installation instructions.
Joints between raised temperature polyethylene tubing and fittings shall comply with Section E506.11.1 and Section E506.11.2. Mechanical joints shall comply with Section E506.5.
Where compression-type fittings include inserts and ferrules or o-rings, the fittings shall be installed without omitting the inserts and ferrules or o-rings.
Solder joints in a metal pipe shall not occur within 18 inches (457 mm) of a transition from such metal pipe to PE-RT pipe.
Joints between PVC plastic pipe and fittings shall comply with Section E506.12.1 and Section E506.12.2.
Solvent cement joints for PVC pipe and fittings shall be clean from dirt and moisture. Purple primer in accordance with ASTM F656 shall be applied until the surface of the pipe and fitting is softened. Solvent cement in accordance with ASTM D2564 shall be applied to joint surfaces.
Threads shall comply with ASME B1.20.1. Schedule 80 or heavier plastic pipe shall be threaded with dies specifically designed for plastic pipe. Thread lubricant, pipe-joint compound or tape shall be applied on the male threads only and shall be approved for application on the piping material.
Shutoff valves shall be installed in ground source-loop piping systems in the locations indicated in Section E507.2 through Section E507.8.
Shutoff valves shall be installed on the supply and return side of a heat exchanger, except where the heat exchanger is integral with a boiler or is a component of a manufacturer's boiler and heat exchanger packaged unit, and is capable of being isolated from the hydronic system by the supply and return valves.
Shutoff valves shall be installed on the building supply and return of a central utility system.
Shutoff valves shall be installed on the connection to a pressure vessel.
Shutoff valves shall be installed on both sides of a pressure-reducing valve.
Shutoff valves shall be installed on connections to mechanical equipment and appliances. This requirement does not apply to components of a ground source loop system such as pumps, air separators, metering devices, and similar equipment.
Shutoff valves shall be installed at connections to nondiaphragm-type expansion tanks.
A pressure relief valve shall be installed on the low-pressure side of a hydronic piping system that has been reduced in pressure. The relief valve shall be set at the maximum pressure of the system design.
Piping, valves, fittings, and connections shall be installed in accordance with the manufacturer's installation instructions.
Where ground source heat pump ground loop systems have a connection to a potable water supply, the potable water system shall be protected.
Openings for pipe penetrations in walls, floors, and ceilings shall be larger than the penetrating pipe. Openings through concrete or masonry building elements shall be sleeved. The annular space surrounding pipe penetrations shall be protected in accordance with the building code.
A pipe in a ground source heat pump piping system, having an exterior surface temperature exceeding 250°F (121°C), shall have a clearance of not less than 1 inch (25.4 mm) from combustible materials.
A ground source heat pump ground-loop piping system shall not be in direct contact with building materials that cause the piping or fitting material to degrade or corrode, or that interferes with the operation of the system.
Piping shall be installed so as to prevent detrimental strains and stresses in the pipe. Provisions shall be made to protect piping from damage resulting from expansion, contraction, and structural settlement. Piping shall be installed so as to avoid structural stresses or strains within building components.
Piping located in a flood hazard area shall be capable of resisting hydrostatic and hydrodynamic loads and stresses, including the effects of buoyancy, during the occurrence of flooding to the design flood elevation.
Pipe shall be supported in accordance with Section 313.1.
Ground source heat pump ground-loop systems shall be designed so that the flow velocities do not exceed the maximum flow velocity recommended by the pipe and fittings manufacturer. Flow velocities shall be controlled to reduce the possibility of water hammer.
Ground source heat pump ground-loop system piping shall be marked with tape, metal tags, or other methods where it enters a building. The marking shall indicate the following words: "GROUND SOURCE HEAT PUMP-LOOP SYSTEM." The marking shall indicate antifreeze used in the system by name and concentration.
Antifreeze and other materials used in the system shall be chemically compatible with the pipe, tubing, fittings, and mechanical systems.
The transfer fluid shall be compatible with the makeup water supplied to the system.
Before connection header trenches are backfilled, the assembled loop system shall be pressure tested with water at 100 psi (689 kPa) for 15 minutes with no observed leaks. Flow and pressure loss testing shall be performed, and the actual flow rates and pressure drops shall be compared to the calculated design values. Where actual flow rate or pressure drop values differ from calculated design values by more than 10 percent, the cause shall be identified and corrective action taken.
Ground source heat pump ground loop piping to be embedded in concrete shall be pressure tested prior to pouring concrete. During pouring, the pipe shall be maintained at the proposed operating pressure.
The provisions of this section shall establish the means of reducing the quantity of air contaminants that are odorous, irritating, or harmful to the comfort and well-being of a building's installers, occupants, and neighbors.
A direct-vent sealed-combustion gas or sealed wood-burning fireplace, or a sealed wood stove shall be installed. The fireplace shall comply with Section E602.1.1 and Section E602.1.2.
Masonry and factory-built fireplaces located in conditioned spaces shall be in accordance with Section E602.1.1.1 through Section E602.1.1.3.
Closeable metal or glass doors covering the entire opening of the firebox shall be installed.
A combustion air intake to draw air from the outside of the building directly into the firebox, which is an area of not less than 6 square inches (0.004 m2) and is equipped with a readily accessible, operable, and tight-fitting damper or combustion-air control device.
The flue damper shall have a readily accessible control.

Exception: Where a gas log, log lighter, or decorative gas appliance is installed in a fireplace, the flue damper shall be blocked open where required by this code or the manufacturer's installation instructions.
Continuous burning pilot lights and the use of indoor air for cooling a firebox jacket, where the indoor air is vented to the outside of the building, are prohibited.
Indoor air quality of a building shall be maintained in accordance with Section E603.1.1 through Section E603.1.3.
Temporary ventilation during construction shall be provided in accordance with the following:
  1. Ventilation during construction shall be achieved through openings in the building shell using fans to produce not less than three air changes per hour.
  2. During dust-producing operations, the supply and return HVAC system openings shall be protected from dust in accordance with Section E603.1.3.
  3. Where the building is occupied during demolition or construction, ventilation shall be provided in accordance with the Control Measures of the SMACNA IAQ Guidelines for Occupied Buildings Under Construction.
  4. The permanent HVAC system shall not be used during construction to condition and ventilate the building within the required temperature range for material and equipment installation. Where required, a supplemental HVAC system shall be used during construction, return air shall be equipped with filters with a minimum efficiency reporting value (MERV) of 8, in accordance with ASHRAE 52.2, or an average efficiency of 30 percent in accordance with ASHRAE 52.2. Before occupancy, filters shall be replaced with filters having a MERV 13 rating in accordance with Section E603.3.
Exception: Embedded hydronics system shall be permitted to be used to condition the building during construction.
After construction ends and interior finishes are installed, flush-out the building to reduce contaminant concentrations by supplying a total outdoor air volume of 14000 cubic feet per square foot (ft3/ft2) (4267.2 m3/m2) of occupiable building area. An internal temperature of not less than 60°F (16°C) and relative humidity not higher than 60 percent shall be maintained during the flush-out process. Occupancy shall begin on condition of 3500 ft3/ft2 (1066.8 m3/m2) of building area, with the remaining 10500 ft3/ft2 (3200.4 m3/m2) being accomplished as soon as possible.

Exception: Other means of reducing the contaminant concentration levels shall be permitted where approved by the Authority Having Jurisdiction.
At the time of rough installation, or during storage on the construction site and until final startup of the heating and cooling equipment, duct and other related air distribution component openings shall be covered with tape, plastic, sheet metal, or other methods acceptable to the enforcing agency to reduce the amount of dust or debris that collects in the system.
Rooms where activities produce hazardous fumes or chemicals, including commercial kitchens, garages, janitorial or laundry rooms, and copy or printing rooms, shall be exhausted and isolated from adjacent spaces in accordance with this code.
In mechanically ventilated buildings, particle filters, or air-cleaning devices shall be provided to clean outdoor and return air prior to its delivery to occupied spaces. The particle or air cleaner shall have a MERV of 13.

Exception: A filter or air cleaning device with a lower MERV value shall be permitted provided it is the highest value commercially available for the specific equipment that is installed.
Installations of HVAC and refrigeration shall not contain CFCs and shall be in accordance with this code.
Roof drainage systems shall discharge to a place of disposal in accordance with the plumbing code. Storm water shall be directed away from the building.
Rooms or occupied spaces within single-family homes and multifamily structures of three stories or less above grade shall be designed to have ventilation (outdoor) air for occupants in accordance with Section E605.1.1 through Section E605.1.3.2, or the applicable local code.
Naturally ventilated spaces shall be permanently open to and within 20 feet (6096 mm) of operable wall or roof openings to the outdoors, the openable area of which is not less than 5 percent of the conditioned floor area of the naturally ventilated space. Where openings are covered with louvers or otherwise obstructed, openable area shall be based on the free unobstructed area through the opening.
The means to open required operable openings shall be readily accessible to building occupants where the space is occupied.
Each space that is not naturally ventilated in accordance with Section E605.1.1 shall be ventilated with a mechanical system capable of providing an outdoor air rate not less than 15 ft3/min (0.007 m3/s) per person times the expected number of occupants. Mechanical ventilation shall comply with this code.
A Mechanical exhaust system, supply system, or combination thereof shall be installed to operate for each dwelling unit to provide continuous dwelling-unit ventilation with outdoor air rate not less than the rate specified in Section E605.1.3.1. [ASHRAE 62.2:4.1]
The total required ventilation rate (Qtot) shall be as specified in Table E605.1.3.1 or, alternatively, calculated in accordance with Equation E605.1.3.1.

Qtot = 0.03Afloor + 7.5(Nbr + 1) (Equation E605.1.3.1)

Where:
Qtot = total required ventilation rate, cubic feet per minute (ft3/min)
Afloor = dwelling unit square foot (ft2)
Nbr = number of bedrooms; not to be less than one
For SI units: 1 cubic foot per minute = 0.00047 m3/s, 1 square foot = 0.0929 m2

Exceptions: Dwelling-unit mechanical ventilation systems shall not be required where the Authority Having Jurisdiction determines that window operation is a locally permissible method of providing ventilation and provided one or more of the following conditions is met:
  1. The building has no mechanical cooling and is located in zone 1 or 2.
  2. The building is thermally conditioned for human occupancy for less than 876 hours per year. [ASHRAE 62.2:4.1.1]
TABLE E605.1.3.1
VENTILATION AIR REQUIREMENTS, (cubic foot per minute)
[ASHRAE 62.2:TABLE 4.1a]
FLOOR AREA(ft2) BEDROOMS
1 2 3 4 5
<500 30 38 45 53 60
501-1000 45 53 60 68 75
1001-1500 60 68 75 83 90
1501-2000 75 83 90 98 105
2001-2500 90 98 105 113 120
2501-3000 105 113 120 128 135
3001-3500 120 128 135 143 150
3501-4000 135 143 150 158 165
4001-4500 150 158 165 173 180
4501-5000 165 173 180 188 195
For SI units: 1 square foot = 0.0929 m2, 1 cubic foot per minute = 0.00047 m3/s
Effective Annual Average Infiltration Rate (Qinf) shall be calculated using Equation E605.1.3.2:

Qinf(cfm) = (NL x wsf x Afloor) / (7.3)* [Equation E605.1.3.2]

Where:
NL = normalized leakage
wsf = weather and shielding factor from ASHRAE 62.2.
Afloor = floor area of residence, ft2 (m2)
* Replace 7.3 with 1.44 for metric units. [ASHRAE 62.2:4.1.2(e)]
Required Mechanical Ventilation Rate (Qfan) shall be calculated using Equation E605.1.3.3:

Qfan = Qtot - (Qinf x Aext) [Equation E605.1.3.3]

Where:
Qfan = required mechanical ventilation rate, cfm (L/s)
Qtot = total required ventilation rate, cfm (L/s)
Qinf = may be not greater than 2/3 x Qtot
(see ASHRAE 62.2 for exceptions for existing buildings)
Aext = 1 for single-family detached homes, or the ratio of exterior envelope surface area that is not attached to garages or other dwelling units to total envelope surface area for single-family attached homes. [ASHRAE 62.2:4.1.2(f)]
Table E605.1.3.1 and Equation E605.1.3.1 assume two persons in a studio or one-bedroom dwelling unit and an additional person for each additional bedroom. Where higher occupant densities are known, the rate shall be increased by 7.5 ft3/min (0.003 m3/s) for each additional person. Where approved by the Authority Having Jurisdiction, lower occupant densities shall be permitted to be used. [ASHRAE 62.2:4.1.3]
The dwelling-unit mechanical ventilation system shall consist of one or more supply or exhaust fans and associate ducts and controls. Local exhaust fans shall be permitted to be part of a mechanical exhaust system. Where local exhaust fans are used to provide dwelling-unit ventilation, the local exhaust airflow shall be permitted to be created towards the whole dwelling-unit ventilation airflow requirement. Outdoor air ducts connected to the return side of an air handler shall be permitted as supply ventilation where manufacturer's requirements for return air temperature are met. See ASHRAE 62.2 for guidance on selection of methods. [ASHRAE 62.2:4.2]
The dwelling-unit mechanical ventilation system shall consist of one or more supply or exhaust fans and associated ducts and controls. Local exhaust fans shall be permitted to be part of a mechanical exhaust system. Where local exhaust fans are used to provide dwelling-unit ventilation, the local exhaust airflow shall be permitted to be credited towards the whole dwelling-unit ventilation airflow requirement. Outdoor air ducts connected to the return side of an air handler shall be permitted as supply ventilation where manufacturer's requirements for return air temperature are met. See ASHRAE 62.2 for guidance on selection of methods. [ASHRAE 62.2:4.2]
The airflow required by this section shall be the quantity of outdoor ventilation air supply, indoor air, or both exhausted by the mechanical ventilation system as installed and shall be measured according to the ventilation equipment manufacturer's instructions, or by using a flow hood, flow grid, or other airflow measuring device at the mechanical ventilation fan's inlet terminals/grilles, outlet terminals/grilles, or in the connected ventilation ducts. Ventilation airflow of systems with multiple operating modes shall be tested in all modes designed to be in accordance with this section. [ASHRAE 62.2:4.3]
A readily accessible manual ON-OFF control, including but not limited to a fan switch or a dedicated branch-circuit overcurrent device, shall be provided. Controls shall include text or an icon indicating the system's function.

Exception: For multifamily dwelling units, the manual ON-OFF control shall not be required to be readily accessible. [ASHRAE 62.2:4.4]
Dwelling-unit mechanical ventilation systems designed to provide variable ventilation shall comply with Section E605.1.7.1 or Section E605.1.7.2 or Section E605.1.7.3. Section E605.1.7.2 and Section E605.1.7.3 also require compliance with ASHRAE 62.2 and require verification with supporting documentation from the manufacturer, designer, or specifier of the ventilation control system that the system meets the requirements of these sections. Where the dwelling-unit ventilation rate varies based on occupancy, occupancy shall be determined by occupancy sensors or by an occupant-programmable schedule. [ASHRAE 62.2:4.5]
To comply with this section, a variable ventilation system shall be installed to provide an average dwelling-unit ventilation rate over any three-hour period that is greater than or equal to Qfan as determined in accordance with Section E605.1.3.3. [ASHRAE 62.2:4.5.1]
This section shall only be allowed to be used where one or more fixed patterns of designed ventilation are known at the time compliance to Section E605.0 is being determined. Such patterns include those both clock-driven and driven by typical meteorological data. Compliance with this section shall be in accordance with either Section E605.1.7.2.1 or Section E605.1.7.2.2. [ASHRAE 62.2:4.5.2]
An annual schedule of ventilation complies with this section when the annual average relative exposure during occupied periods is not more than unity as calculated in accordance with ASHRAE 62.2. [ASHRAE 62.2:4.5.2.1]
The schedule of ventilation complies with this section when it is broken into blocks of time and each block individually has an average relative exposure during occupied periods that is not more than unity as calculated in ASHRAE 62.2. [ASHRAE 62.2:4.5.2.2]
A real-time ventilation controller complies with this section when it is designed to adjust the ventilation system based on real-time input to the ventilation calculations so that the average relative exposure during occupied periods is not more than unity as calculated in ASHRAE 62.2. The averaging period shall be not less than one day but not more than one year and shall be based on simple, recursive or running average, but not extrapolation. [ASHRAE 62.2:4.5.3]
A dwelling-unit ventilation system shall be designed and operated in such a way as to provide the same or lower annual exposure as would be provided in accordance with Section E605.1.3. The calculations shall be based on a single zone with a constant contaminant emission rate. The manufacturer, specifier, or designer of the equivalent ventilation system shall certify that the system is in accordance with this intent and provide supporting documentation. [ASHRAE 62.2:4.6]
Except where a whole house energy recovery system is used, a mechanical exhaust fan vented to the outdoors shall be provided in each room containing a bathtub, shower, or tub/shower combination. The ventilation rate shall be not less than 50 ft3/min (0.02 m3/s) for intermittent operation and 20 ft3/min (0.009 m3/s) for continuous operation. Fans shall comply with the Energy Star Program.
Heating and air conditioning filters shall have a MERV rating of 6 or higher. The air distribution system shall be designed for the pressure drop across the filter.
The building shall comply with this code and ASHRAE 62.1 for ventilation air supply.
The mechanical systems and controls of building shall be designed to provide and maintain indoor comfort conditions in accordance with ASHRAE 55.
Heating and air-conditioning systems shall be sized, designed, and have their equipment selected in accordance with the following:
  1. Heat loss and heat gain are established in accordance with ACCA Manual J, ASHRAE handbooks, or other equivalent methods.
  2. Duct systems shall be sized in accordance with ACCA Manual D, ASHRAE handbooks, or other equivalent methods.
  3. Heating and cooling equipment in accordance with ACCA Manual S or other equivalent methods.
Primers and solvent cements used to join plastic pipe, and fittings shall be in accordance with Section E608.1.1 and Section E608.1.2.
Solvent cement, including one-step solvent cement, shall have a volatile organic compound (VOC) content of less than or equal to 65 ounces per gallon (oz/gal) (487 g/L) for CPVC cement, 68 oz/gal (509 g/L) for PVC cement, and 43 oz/gal (322 g/L) for ABS cement, as determined by the South Coast Air Quality Management District's Laboratory Methods of Analysis for Enforcement Samples, Method 316A.
Primer shall have a volatile organic compound (VOC) content of less than or equal to 73 oz/gal (546 g/L), as determined by the South Coast Air Quality Management District's Laboratory Methods of Analysis for Enforcement Samples, Method 316A.
The provisions of this section address minimum qualifications of installers of mechanical systems covered within the scope of this appendix.
Where permits are required, the Authority Having Jurisdiction shall have the authority to require contractors, installers, or service technicians to demonstrate competency. Where determined by the Authority Having Jurisdiction, the contractor, installer, or service technician shall be licensed to perform such work.
The provisions of this section apply to the commissioning of commercial and institutional HVAC systems.
HVAC commissioning shall be included in the design and construction processes of the project to verify that the HVAC systems and components meet the owner's project requirements and in accordance with this appendix. Commissioning shall be performed in accordance with this appendix by personnel trained and certified in commissioning by a nationally recognized organization. Commissioning requirements shall include the following:
  1. Owner's project requirements
  2. Basis of design
  3. Commissioning measures shown in the construction documents
  4. Commissioning plan
  5. Functional performance
  6. Testing
  7. Post construction documentation and training
  8. Commissioning report
     HVAC systems and components covered by this appendix as well as process equipment and controls, and renewable energy systems shall be included in the scope of the commissioning requirements.
The performance goals and requirements of the HVAC system shall be documented before the design phase of the project begins. This documentation shall include not less than the following:
  1. Environmental and sustainability goals
  2. Energy efficiency goals
  3. Indoor environmental quality requirements
  4. Equipment and systems performance goals
  5. Building occupant and O&M personnel expectations
A written explanation of how the design of the HVAC system meets the owner's project requirements shall be completed at the design phase of the building project, and updated as necessary during the design and construction phases. The basis of design document shall cover not less than the following systems:
  1. Heating, ventilation, air conditioning (HVAC) systems and controls
  2. Water heating systems
  3. Renewable energy systems
A commissioning plan shall be completed to document the approach to how the project will be commissioned, and shall be started during the design phase of the building project. The commissioning plan shall include not less than the following:
  1. General project information
  2. Commissioning goals
  3. Systems to be commissioned. Plans to test systems and components shall include not less than the following:
    1. A detailed explanation of the original design intent.
    2. Equipment and systems to be tested, including the extent of tests.
    3. Functions to be tested.
    4. Conditions under which the test shall be performed.
    5. Measurable criteria for acceptable performance.
  4. Commissioning team information.
  5. Commissioning process activities, schedules, and responsibilities. Plans for the completion of commissioning requirements listed in Section E802.5 through Section E802.7 shall be included.
Functional performance tests shall demonstrate the correct installation and operation of each component, system, and system-to-system interface in accordance with the approved plans and specifications. Functional performance testing reports shall contain information addressing each of the building components tested, the testing methods utilized, and readings and adjustments made.
A system manual and systems operations training are required.
Documentation of the operational aspects of the HVAC system shall be completed within the systems manual and delivered to the building owner and facilities operator. The systems manual shall include not less than the following:
  1. Site information, including facility description, history, and current requirements.
  2. Site contact information.
  3. Basic O&M, including general site operating procedures, basic troubleshooting, recommended maintenance requirements, and site events log.
  4. Major systems.
  5. Site equipment inventory and maintenance notes.
  6. Equipment/system warranty documentation and information.
  7. "As-Built" design drawings.
  8. Other resources and documentation.
The training of the appropriate maintenance staff for each equipment type or system shall include not less than the following:
  1. System/Equipment overview (what it is, what it does, and what other systems or equipment it interfaces with).
  2. Review of the information in the systems manual.
  3. Review of the record drawings on the system/equipment.
A complete report of commissioning process activities undertaken through the design, construction, and post-construction phases of the building project shall be completed and provided to the owner.
Part II of this appendix provides a means of verifying the commissioning requirements of Section E802.1. The activities specified in Part II of this appendix includes three aspects, as described as follows:
  1. Visual inspection of the equipment and installation.
  2. Review of the certification requirements.
  3. Functional tests of the systems and controls.
Details of commissioning acceptance requirements shall be incorporated into the construction documents, including information that describes the details of the functional tests to be performed. This information shall be permitted to be integrated into the specifications for testing and air balancing, energy management and control system, equipment startup procedures or commissioning. It is possible that the work will be performed by a combination of the test and balance (TAB) contractor, mechanical/electrical contractor, and the energy management control system (EMCS) contractor, so applicable roles and responsibilities shall be clearly called out.
The roles and responsibilities of the persons involved in commissioning acceptance are included in Section E803.2.1.1 through Section E803.2.1.3.
The field technician shall be responsible for performing and documenting the results of the acceptance procedures on the certificate of acceptance forms. The field technician shall sign the certificate of acceptance to certify that the information he provides on the certificate of acceptance is true and correct.
The responsible person shall be the contractor or registered design professional of record. A certificate of acceptance shall be signed by a responsible person to take responsibility for the scope of work specified by the certificate of acceptance document. The responsible person shall perform the field testing and verification work, and where this is the case, the responsible person shall complete and sign both the field technician's signature block and the responsible person's signature block on the certificate of acceptance form. The responsible person assumes responsibility for the acceptance testing work performed by the field technician agent or employee.
The certificate of acceptance shall be submitted to the Authority Having Jurisdiction in order to receive the final certificate of occupancy. The Authority Having Jurisdiction shall not release a final certificate of occupancy unless the submitted certificate of acceptance demonstrates that the specified systems and equipment have been shown to be performing in accordance with the applicable acceptance requirements. The Authority Having Jurisdiction has the authority to require the field technician and responsible person to demonstrate competence, to its satisfaction. Certificate of acceptance forms are located in Section E806.0.
Functional tests shall be performed on new equipment and systems installed in either new construction or retrofit applications in accordance with this section. The appropriate certificate of acceptance form along with each specific test shall be completed and submitted to the Authority Having Jurisdict ion before a final occupancy permit can be granted.
Functional testing shall be performed on the devices and systems listed in this section. The functional test results are documented using the applicable certificate of acceptance forms shown in parenthesis and located in Section E806.0. The functional tests shall be performed in accordance with Section E805.0 using the following forms:
  1. Minimum ventilation controls for constant and variable air volume systems (Form MECH-2A).
  2. Zone temperature and scheduling controls for constant volume, single-zone, unitary air conditioner and heat pump systems (Form MECH-3A).
  3. Duct leakage on a subset of small single-zone systems depending on the ductwork location (Form MECH-4A).
  4. Air economizer controls for economizers that are not factory installed and tested (Form MECH-5A).
  5. Demand-controlled ventilation control systems (Form MECH-6A).
  6. Supply fan variable flow controls (Form MECH-7A).
  7. Valve leakage for hydronic variable flow systems and isolation valves on chillers and boilers in plants with more than one chiller or boiler being served by the same primary pumps through a common header (Form MECH-8A).
  8. Supply water temperature reset control strategies programmed into the building automation system for water systems (e.g., chilled, hot, or condenser water) (Form MECH-9A).
  9. Hydronic variable flow controls on a water system where the pumps are controlled by variable frequency drives (e.g., chilled and hot water systems; water-loop heat pump systems) (Form MECH-10A).
  10. Automatic demand shed control (Form MECH-11A).
  11. Fault detection and diagnostic for DX units (Form MECH-12A).
  12. Automatic fault detection and diagnostic systems (AFDD) (Form MECH-13A).
  13. Distributed energy storage DEC/DX AC systems (Form MECH-14A).
  14. Thermal energy storage (TES) systems (Form MECH-15A).
The functional testing process shall comply with Section E804.3.1 through Section E804.3.4.
The installing contractor, registered design professional of record, owner's agent, or the person responsible for certification of the acceptance testing on the certificate of acceptance (responsible person) shall review the plans and specifications to ensure that they are in accordance with the acceptance requirements. This is typically done prior to signing a certificate of compliance.
The installing contractor, registered design professional of record, owner's agent, or the person responsible for certification of the acceptance testing on the certificate of acceptance (responsible person) shall perform a construction inspection prior to testing to ensure that the equipment that is installed is capable of complying with the requirements of this appendix and is calibrated. The installation of associated systems and equipment necessary for proper system operation is required to be completed prior to the testing.
One or more field technicians shall perform the acceptance testing; identify performance deficiencies; ensure that they are corrected; and where necessary, repeat the acceptance procedures until the specified systems and equipment are performing in accordance with the acceptance requirements. The field technician who performs the testing shall sign the certificate of acceptance to certify the information has been provided to document the results of the acceptance procedures is true and correct.

     The responsible person shall review the test results from the acceptance requirement procedures provided by the field technician and sign the certificate of acceptance to certify compliance with the acceptance requirements. The responsible person shall be permitted to perform the field technician's responsibilities, and shall then sign the field technician declaration on the certificate of acceptance to certify that the information on the form is true and correct.
The Authority Having Jurisdiction shall not issue the final certificate of occupancy until required certificates of acceptance are submitted. Copies of completed, signed certificates of acceptance are required to be posted, or made available with the permit(s), and shall be made available to the Authority Having Jurisdiction.
This test ensures that adequate outdoor air ventilation is provided through the variable air volume air handling unit at two representative operating conditions. The test consists of measuring outdoor air values at maximum flow and at or near minimum flow. The test verifies that the minimum volume of outdoor air is introduced to the air handling unit where the system is in occupied mode at these two conditions of supply airflow. This test shall be performed in conjunction with supply fan variable flow controls test procedures to reduce the overall system testing time as both tests use the same two conditions of airflow for their measurements.
The procedure for performing a functional test for variable air volume systems shall be in accordance with Section E805.1.1.1 and Section E805.1.1.2.
Prior to functional testing, verify and document that the system controlling outside airflow is calibrated either in the field or factory.
The functional testing shall be in accordance with the following steps:

Step 1: Where the system has an outdoor air economizer, force the economizer high limit to disable economizer control (e.g., for a fixed drybulb high limit, lower the setpoint below the current outdoor air temperature).

Step 2: Adjust supply airflow to either the sum of the minimum zone airflows or 30 percent of the total design airflow. Verify and document the following:
  1. Measured outside airflow reading is within 10 percent of the total ventilation air called for in the certificate of compliance.
  2. OSA controls stabilize within 5 minutes.
Step 3: Adjust supply airflow to achieve design airflow. Verify and document the following:
  1. Measured outside airflow reading is within 10 percent of the total ventilation air called for in the certificate of compliance.
  2. OSA controls stabilize within 5 minutes.
Step 4: Restore system to "as-found" operating conditions.
System controlling outdoor air flow shall be calibrated in the field or at the factory.

     Measured outdoor airflow reading shall be within 10 percent of the total value found on the certificate of compliance under the following conditions:
  1. Minimum system airflow.
  2. Thirty percent of total design flow design supply airflow.
The purpose of this test is to ensure that adequate outdoor air ventilation is provided through the constant volume air handling unit to the spaces served under operating conditions. The intent of this test is to verify that the minimum volume of outdoor air is introduced to the air handling unit during typical space occupancy.
The procedure for performing a functional test for constant air volume systems shall be in accordance with Section E805.2.1.1 and Section E805.2.1.2.
Prior to functional testing, verify and document the following:
  1. Minimum position is marked on the outside air damper.
  2. The system has means of maintaining the minimum outdoor air damper position.
Where the system has an outdoor air economizer, force the economizer to the minimum position and stop outside air damper modulation (e.g., for a fixed drybulb high limit, lower the setpoint below the current outdoor air temperature).
The system has a means of maintaining the minimum outdoor air damper position. The minimum damper position is marked on the outdoor air damper. The measured outside airflow reading shall be within 10 percent of the total ventilation air called for in the certificate of compliance.
The purpose of this test is to verify the individual components of a constant volume, single-zone, unitary air conditioner and heat pump system function correctly; including: thermostat installation and programming, supply fan, heating, cooling, and damper operation.
The procedure for performing a functional test for constant volume, single-zone, unitary air conditioner and heat pump systems shall be in accordance with Section E805.3.1.1 and Section E805.3.1.2.
Prior to functional testing, verify and document the following:
  1. Thermostat is located within the space-conditioning zone that is served by the HVAC system.
  2. Thermostat shall be in accordance with temperature adjustment and dead band requirements.
  3. Occupied, unoccupied, and holiday schedules shall be programmed per the facility's schedule.
  4. Preoccupancy purge is programmed.
The functional testing shall be in accordance with the following steps:

Step 1: Disable economizer and demand control ventilation systems (where applicable).

Step 2: Simulate a heating demand during the occupied condition. Verify and document the following:
  1. Supply fan operates continually.
  2. The unit provides heating.
  3. No cooling is provided by the unit.
  4. Outside air damper is at minimum position.
Step 3: Simulate operation in the dead band during occupied condition. Verify and document the following:
  1. Supply fan operates continually.
  2. Neither heating nor cooling is provided by the unit.
  3. Outside air damper is at minimum position.
Step 4: Simulate cooling demand during occupied condition. Lock out economizer (where applicable). Verify and document the following:
  1. Supply fan operates continually.
  2. The unit provides cooling.
  3. No heating is provided by the unit.
  4. Outside air damper is at minimum position.
Step 5: Simulate operation in the dead band during unoccupied mode. Verify and document the following:
  1. Supply fan is off.
  2. Outside air damper is fully closed.
  3. Neither heating nor cooling is provided by the unit.
Step 6: Simulate heating demand during unoccupied conditions. Verify and document the following:
  1. Supply fan is on (either continuously or cycling).
  2. Heating is provided by the unit.
  3. No cooling is provided by the unit.
  4. Outside air damper is either closed or at minimum position.
Step 7: Simulate cooling demand during unoccupied condition. Lock out economizer (where applicable). Verify and document the following:
  1. Supply fan is on (either continuously or cycling).
  2. Cooling is provided by the unit.
  3. No heating is provided by the unit.
  4. Outside air damper is either closed or at minimum position.
Step 8: Simulate manual override during unoccupied condition. Verify and document the following:
  1. System operates in "occupied" mode.
  2. System reverts to "unoccupied" mode where manual override time period expires.
Step 9: Restore economizer and demand control ventilation systems (where applicable), and remove system overrides initiated during the test.
Thermostat is located within the space-conditioning zone that is served by the respective HVAC system. The thermostat shall comply with temperature adjustment and dead band requirements. Occupied, unoccupied, and holiday schedules shall be programmed per the facility's schedule. Preoccupancy purge is programmed in accordance with the requirements.
The purpose of this test is to verify duct work associated with non-exempt constant volume, single-zone, HVAC units (e.g., air conditioners, heat pumps, and furnaces) meet the material, installation, and insulation R-values and leakage requirements outlined in this appendix. This test is required for single-zone units serving less than 5000 square feet (464.52 m2) of floor area where 25 percent or more of the duct surface area is in one of the following spaces:
  1. Outdoors.
  2. In a space directly under a roof where the U-factor of the roof is greater than the U-factor of the ceiling.
  3. In a space directly under a roof with fixed vents or openings to the outside or unconditioned spaces.
  4. In an unconditioned crawlspace.
  5. In other unconditioned spaces.
     This test applies to both new duct systems and to existing duct systems being extended or the space conditioning system is altered by the installation or replacement of space conditioning equipment, including: replacement of the air handler; outdoor condensing unit of a split system air conditioner or heat pump; cooling or heating coil; or the furnace heat exchanger. Existing duct systems do not have to be tested where they are insulated or sealed with asbestos.
The procedure for performing a functional test for air distribution systems shall be in accordance with Section E805.4.1.1 and Section E805.4.1.2.
Prior to functional testing, verify and document the following:
  1. Duct connections shall comply with the requirements of this appendix and this code.
  2. Flexible ducts are not compressed.
  3. Ducts are fully accessible for testing.
  4. Joints and seams are properly sealed in accordance with the requirements of this appendix.
  5. Insulation R-Values shall comply with the minimum requirements of this appendix.
Perform duct leakage test in accordance with Section E503.4.7.2.1.
Flexible ducts are not compressed or constricted. Duct connections shall comply with the requirements of this appendix and this code (new ducts only). Joints and seams are properly sealed in accordance with the requirements of this appendix and this code (new ducts only). Duct R-values shall comply with the minimum requirements of this appendix (new ducts only). Insulation is protected from damage and suitable for outdoor usage where applicable (new ducts only). The leakage shall not exceed the rate in accordance with Section E503.4.7.2.
The purpose of functionally testing an air economizer cycle is to verify that an HVAC system uses outdoor air to satisfy space cooling loads where outdoor air conditions are acceptable. There are two types of economizer controls; stand-alone packages and DDC controls. The stand-alone packages are commonly associated with small unitary rooftop HVAC equipment, and DDC controls are typically associated with built-up or large packaged air handling systems. Test procedures for both economizer control types are provided.

     For units with economizers that are factory installed and certified operational by the manufacturer to economizer quality control requirements, the in-field economizer functional tests do not have to be conducted. A copy of the manufacturer's certificate shall be attached to the Form MECH-SA. However, the construction inspection, including compliance with high-temperature lockout temperature setpoint, shall be completed regardless of whether the economizer is field or factory installed.
The procedure for performing a functional test for air economizer controls shall comply with Section E805.5.1.1 and Section E805.5.1.2.
Prior to functional testing, verify and document the following:
  1. Economizer lockout setpoint is in accordance with this appendix.
  2. Economizer lockout control sensor is located to prevent false readings.
  3. System is designed to provide up to 100 percent outside air without over-pressurizing the building.
  4. For systems with DDC controls lockout sensor(s) are either factory calibrated or field calibrated.
  5. For systems with non-DDC controls, manufacturer's startup and testing procedures are applied.
The functional testing shall be in accordance with the following steps:

Step 1: Disable demand control ventilation systems (where applicable).

Step 2: Enable the economizer, and simulate a cooling demand large enough to drive the economizer fully open. Verify and document the following:
  1. Economizer damper is 100 percent opened and return air damper is 100 percent closed.
  2. Where applicable, verify that the economizer remains 100 percent open where the cooling demand can no longer be met by the economizer alone.
  3. Applicable fans and dampers operate as intended to maintain building pressure.
  4. The unit heating is disabled.
Step 3: Disable the economizer and simulate a cooling demand. Verify and document the following:
  1. Economizer damper shall close to its minimum position.
  2. Applicable fans and dampers shall operate as intended to maintain building pressure.
  3. The unit heating is disabled.
Step 4: Simulate a heating demand, and set the economizer so that it is capable of operating (e.g., actual outdoor air conditions are below lockout setpoint). Verify the economizer is at minimum position.

Step 5: Restore demand control ventilation systems (where applicable) and remove system overrides initiated during the test.
Air economizer controls acceptance criteria shall be as follows:
  1. Where the economizer is factory installed and certified, a valid factory certificate is required for acceptance. No additional equipment tests are necessary.
  2. Air economizer lockout setpoint is in accordance with this appendix. Outside sensor location accurately reads true outdoor air temperature and is not affected by exhaust air or other heat sources.
  3. Sensors are located to achieve the desired control.
  4. During economizer mode, the outdoor air damper shall modulate open to a maximum position and return air damper to 100 percent closed.
  5. The outdoor air damper is 100 percent open before mechanical cooling is enabled and for units 75000 Btu/h (22 kw) and larger remains at 100 percent open while mechanical cooling is enabled (economizer integration where used for compliance).
  6. Where the economizer is disabled, the outdoor air damper closes to a minimum position; the return damper modulates 100 percent open, and mechanical cooling remains enabled.
The purpose of this test is to verify that systems required to employ demand-controlled ventilation shall be permitted to vary outside ventilation flow rates based on maintaining interior carbon dioxide (CO2) concentration setpoints. Demand-controlled ventilation refers to an HVAC system's ability to reduce outdoor air ventilation flow below design values where the space served is at less than design occupancy. Carbon dioxide is a good indicator of occupancy load and is the basis used for modulating ventilation flow rates.
The procedure for performing a functional test for demand-control ventilation (DVC) systems shall be in accordance with Section E805.6.1.1 and Section E805.6.1.2.
Prior to functional testing, verify and document the following:
  1. Carbon dioxide control sensor is factory calibrated or field-calibrated in accordance with this appendix.
  2. The sensor is located in the high-density space between 3 feet (914 mm) and 6 feet (1829 mm) above the floor or at the anticipated level of the occupants' heads.
  3. DCV control setpoint is at or below the carbon dioxide concentration permitted by this appendix.
The functional testing shall be in accordance with the following steps:

Step 1: Disable economizer controls.

Step 2: Simulate a signal at or slightly above the carbon dioxide concentration setpoint required by this appendix. Verify and document the following:
  1. For single zone units, outdoor air damper modulates open to satisfy the total ventilation air called for in the certificate of compliance.
  2. For multiple zone units, either outdoor air damper or zone damper modulate open to satisfy the zone ventilation requirements.
Step 3: Simulate signal well below the carbon dioxide setpoint. Verify and document the following:
  1. For single zone units, outdoor air damper modulates to the design minimum value.
  2. For multiple zone units, either outdoor air damper or zone damper modulate to satisfy the reduced zone ventilation requirements.
Step 4: Restore economizer controls and remove system overrides initiated during the test.

Step 5: With controls restored, apply carbon dioxide calibration gas at a concentration slightly above the setpoint to the sensor. Verify that the outdoor air damper modulates open to satisfy the total ventilation air called for in the certificate of compliance.
Demand-controlled ventilation systems acceptance criteria shall be as follows:
  1. Each carbon dioxide sensor is factory calibrated (with calibration certificate) or field calibrated.
  2. Each carbon dioxide sensor is wired correctly to the controls to ensure proper control of the outdoor air damper.
  3. Each carbon dioxide sensor is located correctly within the space 1 foot (305 mm) to 6 feet (1829 mm) above the floor.
  4. Interior carbon dioxide concentration setpoint is not more than 600 parts per million (ppm) plus outdoor air carbon dioxide value where dynamically measured or not more than 1000 ppm where no OSA sensor is provided.
  5. A minimum OSA setting is provided where the system is in occupied mode in accordance with this appendix regardless of space carbon dioxide readings.
  6. A maximum OSA damper position for DCV control shall be established in accordance with this appendix, regardless of space carbon dioxide readings.
  7. The outdoor air damper shall modulate open where the carbon dioxide concentration within the space exceeds setpoint.
  8. The outdoor air damper modulates closed (toward minimum position) where the carbon dioxide concentration within the space is below setpoint.
The purpose of this test is to ensure that the supply fan in a variable air volume application modulates to meet system airflow demand. In most applications, the individual VAV boxes serving each space will modulate the amount of air delivered to the space based on heating and cooling requirements. As a result, the total supply airflow provided by the central air handling unit shall vary to maintain sufficient airflow through each VAV box. Airflow shall be controlled using a variable frequency drive (VFD) to modulate supply fan speed and vary system airflow. The most common strategy for controlling the VFD is to measure and maintain static pressure within the duct.
The procedure for performing a functional test for supply fan variable controls shall be in accordance with Section E805.7.1.1 and Section E805.7.1.2.
Prior to functional testing, verify and document the following:
  1. Supply fan controls modulate to increase capacity.
  2. Supply fan maintains discharge static pressure within plus or minus 10 percent of the current operating set point.
  3. Supply fan controls stabilize within a 5 minute period.
The functional testing shall be in accordance with the following steps:

Step 1: Simulate demand for design airflow. Verify and document the following:
  1. Supply fan controls modulate to increase capacity.
  2. Supply fan maintains discharge static pressure within plus or minus 10 percent of the current operating set point.
  3. Supply fan controls stabilize within a 5 minute period.
Step 2: Simulate demand for minimum airflow. Verify and document the following:
  1. Supply fan controls modulate to decrease capacity.
  2. Current operating setpoint has decreased (for systems with DDC to the zone level).
  3. Supply fan maintains discharge static pressure within plus or minus 10 percent of the current operating setpoint.
  4. Supply fan controls stabilize within a 5 minute period.
Step 3: Restore system to correct operating conditions.
Supply fan variable flow controls acceptance criteria shall be as follows:
  1. Static pressure sensor(s) is factory calibrated (with calibration certificate) or field calibrated.
  2. For systems without DDC controls to the zone level, the pressure sensor setpoint is less than one-third of the supply fan design static pressure.
  3. For systems with DDC controls with VAV boxes reporting to the central control panel, the pressure setpoint is reset by zone demand (box damper position or a trim and respond algorithm).
At full flow:
  1. Supply fan maintains discharge static pressure within plus or minus 10 percent of the current operating control static pressure setpoint.
  2. Supply fan controls stabilizes within a 5 minute period.
  3. At minimum flow (not less than 30 percent of total design flow).
  4. Supply fan controls modulate to decrease capacity.
  5. Current operating setpoint has decreased (for systems with DDC to the zone level).
  6. Supply fan maintains discharge static pressure within plus or minus 10 percent of the current operating setpoint.
The purpose of this test is to ensure that control valves serving variable flow systems are designed to withstand the pump pressure over the full range of operation. Valves with insufficient actuators will lift under certain conditions causing water to leak through and loss of control. This test applies to the variable flow systems, chilled and hot-water variable flow systems, chiller isolation valves, boiler isolation valves, and water-cooled air conditioner and hydronic heat pump systems.
The procedure for performing a functional test for valve leakage shall be in accordance with Section E805.8.1.1 and Section E805.8.1.2.
Prior to functional testing, verify and document the valve and piping arrangements were installed in accordance with the design drawings.
The functional testing shall be in accordance with the following steps:

Step 1: For each pump serving the distribution system, dead head the pumps using the discharge isolation valves at the pumps. Document the following:
  1. Record the differential pressure across the pumps.
  2. Verify that this is within 5 percent of the submittal data for the pump.
Step 2: Reopen the pump discharge isolation valves. Automatically close valves on the systems being tested. Where three-way valves are present, close off the bypass line. Verify and document the following:
  1. The valves automatically close.
  2. Record the pressure differential across the pump.
  3. Verify that the pressure differential is within 5 percent of the reading from Step 1 for the pump that is operating during the valve test.
Step 3: Restore system to correct operating conditions.
System has no flow where coils are closed and the pump is turned on.
The purpose of this test is to ensure that both the chilled water and hot water supply temperatures are automatically reset based on either building loads or outdoor air temperature, as indicated in the control sequences. Many HVAC systems are served by central chilled and heating hot water plants. The supply water operating temperatures shall meet peak loads where the system is operating at design conditions. As the loads vary, the supply water temperatures shall be permitted to be adjusted to satisfy the new operating conditions. The chilled water supply temperature shall be permitted to be raised as the cooling load decreases, and heating hot water supply temperature shall be permitted to be lowered as the heating load decreases.

     This requirement applies to chilled and hot water systems that are not designed for variable flow, and that have a design capacity greater than or equal to 500000 Btu/h (147 kW).
The procedure for performing a functional test for supply water temperature reset controls shall be in accordance with Section E805.9.1.1 and Section E805.9.1.2.
Prior to functional testing, verify and document the supply water temperature sensors shall be either factory or field calibrated.
The functional testing shall be in accordance with the following steps:

Step 1: Change reset control variable to its maximum value. Verify and document the following:
  1. Chilled or hot water temperature setpoint is reset to appropriate value.
  2. Actual supply temperature changes to meet setpoint.
  3. Verify that supply temperature is within 2 percent of the control setpoint.
Step 2: Change reset control variable to its minimum value. Verify and document the following:
  1. Chilled or hot water temperature setpoint is reset to appropriate value.
  2. Actual supply temperature changes to meet setpoint.
  3. Verify that supply temperature is within 2 percent of the control setpoint.
Step 3: Restore reset control variable to automatic control. Verify and document the following:
  1. Chilled or hot water temperature setpoint is reset to appropriate value.
  2. Actual supply temperature changes to meet setpoint.
  3. Verify that supply temperature is within 2 percent of the control setpoint.
The supply water temperature sensors are either factory calibrated (with calibration certificates) or field-calibrated. Sensor performance shall comply with the specifications. The supply water reset is operational.
The purpose of this test is to ensure that hydronic variable flow chilled water and water-loop heat pump systems with circulating pumps larger than 5 hp (3.7 kW) vary system flow rate by modulating pump speed using a variable frequency drive (VFD) or equivalent. As the loads within the building fluctuate, control valves modulate the amount of water passing through each coil and add or remove the desired amount of energy from the air stream to satisfy the load. In the case of water-loop heat pumps, each two-way control valve associated with a heat pump will be closed where that unit is not operating. As each control valve modulates, the pump variable frequency drive (VFD) responds accordingly to meet system water flow requirements. This is not required on heating hot water systems with variable flow designs or for condensing water serving water cooled chillers.
The procedure for performing a functional test for hydronic system variable flow controls shall be in accordance with Section E805.10.1.1 and Section E805.10.1.2.
Prior to functional testing, verify and document the pressure sensors are either factory or field calibrated.
The functional testing shall comply with the following steps:

Step 1: Open control valves to increase water flow to not less than 90 percent design flow. Verify and document the following:
  1. Pump speed increases.
  2. System pressure is either within plus or minus 5 percent of current operating setpoint, or the pressure is below the setpoint, and the pumps are operating at 100 percent speed.
  3. System operation shall stabilize within 5 minutes after test procedures are initiated.
Step 2: Modulate control valves to reduce water flow to 50 percent of the design flow or less, but not lower than the pump minimum flow. Verify and document the following:
  1. Pump speed decrease.
  2. Current operating setpoint has decreased (for systems with DDC to the zone level).
  3. Current operating setpoint has not increased (for all other systems).
  4. System pressure is within 5 percent of current operating setpoint.
  5. System operation stabilizes within 5 minutes after test procedures are initiated.
The differential pressure sensor is either factory calibrated (with calibration certificates) or field calibrated. The pressure sensor shall be located at or near the most remote HX or control valve. The setpoint system controls shall stabilize.
The purpose of this test is to ensure that the central demand shed sequences have been properly programmed into the DDC system.
The procedure for performing a functional test for automatic demand shed controls shall be in accordance with Section E805.11.1.1 and Section E805.11.1.2.
Prior to functional testing, verify and document that the EMCS interface enables activation of the central demand shed controls.
The functional testing shall comply with the following steps:

Step 1: Engage the global demand shed system. Verify and document the following:
  1. That the coo ling setpoint in noncritical spaces increases by the proper amount.
  2. That the cooling setpoint in critical spaces do not change.
Step 2: Disengage the global demand shed system. Verify and document the following:
  1. That the coo ling setpoint in noncritical spaces return to their original values.
  2. That the cooling setpoint in critical spaces do not change.
The control system changes the setpoints of noncritical zones on activation of a single central hardware or software point then restores the initial setpoints where the point is released.
The purpose of this test is to verify proper fault detection and reporting for automated fault detection and diagnostics systems for packaged units. Automated FDD systems ensure proper equipment operation by identifying and diagnosing common equipment problems such as improper refrigerant charge, low airflow, or faulty economizer operation. Qualifying FDD systems receive a compliance credit where using the performance approach. A system that does not meet the eligibility requirements shall be permitted to be installed, but no compliance credit will be given.
The procedure for performing a functional test for fault detection and diagnostics (FDD) for packaged direct-expansion (DX) units shall be in accordance with Section E805.12.1.1 and Section E805.12.1.2.
Prior to functional testing, verify and document that the FDD hardware is installed on equipment by the manufacturer, and that equipment make and model include factory-installed FDD hardware that match the information indicated on copies of the manufacturer's cut sheets and on the plans and specifications.

     This procedure applies to fault detection and diagnostics (FDD) system for direct-expansion packaged units containing the following features:
  1. The unit shall include a factory-installed economizer and shall limit the economizer deadband to not more than 2°F (-17°C).
  2. The unit shall include direct-drive actuators on outside air and return air dampers.
  3. The unit shall include an integrated economizer with either differential drybulb or differential enthalpy control.
  4. The unit shall include a low temperature lockout on the compressor to prevent coil freeze-up or comfort problems.
  5. Outside air and return air dampers shall have maximum leakage rates in accordance to this appendix.
  6. The unit shall have an adjustable expansion control device such as a thermostatic expansion valve (TXV).
  7. To improve the ability to troubleshoot charge and compressor operation, a high-pressure refrigerant port will be located on the liquid line. A low-pressure refrigerant port will be located on the suction line.
  8. The following sensors shall be permanently installed to monitor system operation, and the controller shall have the capability of displaying the value of each parameter:
    1. Refrigerant suction pressure
    2. Refrigerant suction temperature
    3. Liquid line pressure
    4. Liquid line temperature
    5. Outside air temperature
    6. Outside air relative humidity
    7. Return air temperature
    8. Return air relative humidity
    9. Supply air temperature
    10. Supply air relative humidity
         The controller will provide system status by indicating the following conditions:
    1. Compressor enabled
    2. Economizer enabled
    3. Free cooling available
    4. Mixed air low limit cycle active
    5. Heating enabled
         The unit controller shall have the capability to manually initiate each operating mode so that the operation of compressors, economizers, fans, and heating system can be independently tested and verified.
The functional testing shall be in accordance with the following steps:

Step 1: Test low airflow condition by replacing the existing filter with a dirty filter or appropriate obstruction.
Step 2: Verify that the fault detection and diagnostics system reports the fault.
Step 3: Verify that the system is able to verify the correct refrigerant charge.
Step 4: Calibrate outside air, return air, and supply air temperature sensors.
The system is able to detect a low airflow condition and report the fault. The system is able to detect where refrigerant charge is low or high and the fault is reported.
The purpose of this test is to verify that the system detects common faults in air handling units and terminal units. FDD systems for air handling units and zone terminal units require DDC controls to the zone level. Successful completion of this test provides a compliance credit where using the performance approach. An FDD system that does not pass this test shall be permitted to be installed, but no compliance credit will be given.
The procedure for performing a functional test for automatic fault detection diagnostics (FDD) for Air Handling Units and Zone Terminal Units shall be in accordance with Section E805.13.1.1.
The functional testing shall be in accordance with Section E805.13.1.1.1 and Section E805.13.1.1.2.
The functional testing of AHU with FDD controls shall be in accordance with the following steps:

Step 1: Sensor drift/failure:
  1. Disconnect outside air temperature sensor from unit controller.
  2. Verify that the FDD system reports a fault.
  3. Connect OAT sensor to the unit controller.
  4. Verify that FDD indicates normal system operation.
Step 2: Damper/actuator fault:
  1. From the control system workstation, command the mixing box dampers to full open (100 percent outdoor air).
  2. Disconnect power to the actuator and verify that a fault is reported at the control workstation.
  3. Reconnect power to the actuator and command the mixing box dampers to full open.
  4. Verify that the control system does not report a fault.
  5. From the control system workstation, command the mixing box dampers to a full-closed position (0 percent outdoor air).
  6. Disconnect power to the actuator and verify that a fault is reported at the control workstation.
  7. Reconnect power to the actuator and command the dampers closed.
  8. Verify that the control system does not report a fault during normal operation.
Step 3: Valve/actuator fault:
  1. From the control system workstation, command the heating and cooling coil valves to full open or closed, then disconnect power to the actuator and verify that a fault is reported at the control workstation.
Step 4: Inappropriate simultaneous heating, mechanical cooling, and economizing or all functions:
  1. From the control system workstation, override the heating coil valve and verify that a fault is reported at the control workstation.
  2. From the control system workstation, override the cooling coil valve and verify that a fault is reported at the control workstation.
  3. From the control system workstation, override the mixing box dampers and verify that a fault is reported at the control workstation.
The functional testing of one of each type of terminal unit (VAV box) in the project not less than 5 percent of the terminal boxes shall be in accordance with the following steps:

Step 1: Sensor drift/failure:
  1. Disconnect the tubing to the differential pressure sensor of the VAV box.
  2. Verify that control system detects and reports the fault.
  3. Reconnect the sensor and verify proper sensor operation.
  4. Verify that the control system does not report a fault.
Step 2: Damper/actuator fault:
  1. Damper stuck open.
    1. Command the damper to full open (room temperature above setpoint).
    2. Disconnect the actuator to the damper.
    3. Adjust the cooling setpoint so that the room temperature is below the cooling setpoint to command the damper to the minimum position. Verify that the control system reports a fault.
    4. Reconnect the actuator and restore to normal operation.
  2. Damper stuck closed.
    1. Set the damper to the minimum position.
    2. Disconnect the actuator to the damper.
    3. Set the cooling setpoint below the room temperature to simulate a call for cooling. Verify that the control system reports a fault.
    4. Reconnect the actuator and restore to normal operation.
Step 3: Valve/actuator fault (for systems with hydronic reheat):
  1. Command the reheat coil valve to full open.
  2. Disconnect power to the actuator. Set the heating setpoint temperature to be lower than the current space temperature, to command the valve closed. Verify that the fault is reported at the control workstation.
  3. Reconnect the actuator and restore normal operation.
Step 4: Feedback loop tuning fault (unstable airflow):
  1. Set the integral coefficient of the box controller to a value 50 times the current value.
  2. The damper cycles continuously and airflow is unstable. Verify that the control system detects and reports the fault.
  3. Reset the integral coefficient of the controller to the original value to restore normal operation.
Step 5: Disconnected inlet duct:
  1. From the control system workstation, command the damper to full closed; then disconnect power to the actuator, and verify that a fault is reported at the control workstation.
The system is able to detect common faults with air-handling units, such as a sensor failure, a failed damper, an actuator, or an improper operating mode.

     The system is able to detect and report common faults with zone terminal units, such as a failed damper, an actuator, or a control tuning issue.
The purpose of this test is to verify the proper operation of distributed energy storage DX systems. Distributed energy systems (DES) reduce peak demand by operating during off-peak hours and storing cooling, usually in the form of ice. During peak cooling hours the ice is melted to avoid compressor operation. The system typically consists of a water tank containing refrigerant coils that cool the water and convert it to ice. As with a standard direction expansion (DX) air conditioner, the refrigerant is compressed in a compressor and then cooled in an air-cooled condenser. The liquid refrigerant then is directed through the coils in the water tank to make ice or to air handler coils to cool the building. This applies to constant or variable volume, direct expansion (DX) systems with distributed energy storage (DES/DXAC).
The procedure for performing a functional test for distributed energy storage DX AC systems shall be in accordance with Section E805.14.1.1 through Section E805.14.1.3.
Prior to functional testing, verify and document the following:

  1. The water tank is filled to the proper level.
  2. The water tank is sitting on a foundation with adequate structural strength.
  3. The water tank is insulated and the top cover is in place.
  4. The DES/DXAC is installed correctly (e.g., refrigerant piping, etc.).
  5. Verify that the correct model number is installed and configured.
The functional testing shall be in accordance with the following steps: Step 1: Simulate cooling load during daytime period (e.g., by setting time schedule to include actual time and placing thermostat cooling setpoint below actual temperature). Verify and document the following:
  1. Supply fan operates continually.
  2. Where the DES/DXAC has cooling capacity, DES/DXAC shall run to meet the cooling demand (in ice melt mode).
  3. Where the DES/DXAC has no ice and there is a call for cooling, the DES/DXAC shall run in direct cooling mode.
Step 2: Simulate no cooling load during daytime condition. Verify and document the following:
  1. Supply fan operates in accordance with the facility thermostat or control system.
  2. The DES/DXAC and the condensing unit do not run.
Step 3: Simulate no cooling load during morning shoulder time period. Verify and document the following:
  1. The DES/DXAC is idle.
Step 4: Simulate a cooling load during morning shoulder time period. Verify and document the following:
  1. The DES/DXAC runs in direct cooling mode.
Set the proper time and date in accordance with the manufacturer's instructions for approved installers.
Distributed energy storage DXAC system acceptance criteria shall be as follows:
  1. Verify night time ice making operation.
  2. Verify that tank discharges during on-peak cooling periods.
  3. Verify that the compressor does not run and the tank does not discharge where there is no cooling demand during on-peak periods.
  4. Verify that the system does not operate during a morning shoulder period where there is no cooling demand.
  5. Verify that the system operates in direct mode (with compressor running) during the morning shoulder time period.
The purpose of this test is to verify the proper operation of thermal energy storage (TES) systems. TES systems reduce energy consumption during peak demand periods by shifting energy consumption to nighttime. Operation of the thermal energy storage compressor during the night produces cooling energy which is stored in the form of cooled fluid or ice in tanks. During peak cooling hours the thermal storage is used for cooling to prevent the need for chiller operation. This section is limited to the following types of TES systems:
  1. Chilled water storage
  2. Ice-on-coil
  3. Ice harvester
  4. Brine
  5. Ice-slurry
  6. Eutectic salt
  7. Clathrate hydrate slurry (CHS)
The procedure for performing a functional test for thermal energy storage (TES) system shall be in accordance with Section E805.15.1.1 and Section E805.15.1.2.
Prior to functional testing, verify and document the following for the chiller and storage tank:
  1. Chiller:
    1. Brand and Model
    2. Type (centrifugal, reciprocating, other)
    3. Capacity (tons) (SIZE)
    4. Starting efficiency (kW /ton) at beginning of ice production (COMP - kW/TON - START)
    5. Ending efficiency (kW/ton) at end of ice production (COMP - kW/TON/END)
    6. Capacity reduction (percent/°F) (PER - COMP - REDUCT IF)
    7. Verify that the efficiency of the chiller meets or exceeds the requirements of Section E501.0.
  2. Storage Tank:
    1. Storage type (TES-TYPE)
    2. Number of tanks (SIZE)
    3. Storage capacity per tank (ton-hours) (SIZE)
    4. Storage rate (tons) (COOL - STORE - RATE)
    5. Discharge rate (tons) (COOL- SUPPLY - RATE)
    6. Auxiliary power (watts) (PUMPS+ AUX - kW)
    7. Tank area (CTANK - LOSS - COEFF)
    8. Tank insulation (R-Value) (CTANK - LOSS - COEFF)
  3. TES System:
    1. The TES system is one of the above eligible systems.
    2. Initial charge rate of the storage tanks (tons).
    3. Final charge rate of the storage tank (tons).
    4. Initial discharge rate of the storage tanks (tons).
    5. Final discharge rate of the storage tank (tons).
    6. Charge test time (hrs).
    7. Discharge test time (hrs).
    8. Tank storage capacity after charge (ton-hrs).
    9. Tank storage capacity after discharge (ton-hrs).
    10. Tank standby storage losses (UA).
    11. Initial chiller efficiency (kW /ton) during charging.
    12. Final chiller efficiency (kW/ton) during charging.
The functional testing shall be in accordance with the following steps:

Step 1: Verify that the TES system and the chilled water plant is controlled and monitored by an energy management system (EMS).

Step 2: Force the time to be between 9:00 p.m. and 9:00 a.m., and simulate a partial or no charge of the tank. Simulate no cooling load by setting the indoor temperature setpoint(s) higher than the ambient temperature.

     Where the tank is full or nearly full of ice, it shall be permitted to adjust the control settings for this test. In some cases, the control system will not permit the chiller to start the ice-making process unless a portion of the ice has been melted. The controls designer shall be permitted to use an inventory meter (a 4-20 mA sensor that indicates water level) to determine whether or not ice-making can commence (e.g., not allow ice-making unless the inventory meter signal is less than 17 mA). Where this is the case, this limit can be reset to 20 mA during testing to allow ice making to occur.

     Verify that the TES system starts charging (storing energy). This shall be checked by verifying flow and inlet and outlet temperatures of the storage tank, or directly by reading an inventory meter where the system has one.

Step 3: Force the time to be between 6:00 p.m. and 9:00 p.m., and simulate a partial charge on the tank. Simulate a cooling load by setting the indoor temperature setpoint lower than the ambient temperature. Verify that the TES system starts discharging. This shall be checked by observing tank inlet and outlet temperatures and system flow, or directly by reading an inventory meter where the system has one. Where the system has no charge, verify that the system will still attempt to meet the load through storage.

Step 4: Force the time to be between noon and 6:00 p.m., and simulate a cooling load by lowering the indoor air temperature setpoint below the ambient temperature. Verify that the tank starts discharging and the compressor is off.

Step 5: Force the time to be between 9:00 a.m. to noon, and simulate a cooling load by lowering the indoor air temperature setpoint below the ambient temperature. Verify that the tank does not discharge and the cooling load is met by the compressor.

Step 6: Force the time to be between 9:00 p.m. and 9:00 a.m. and simulate a full tank charge. This can be done in a couple of ways:
  1. By changing the inventory sensor limit that indicates tank capacity to the energy management system so that it indicates a full tank.
  2. By resetting the coolant temperature that indicates a full charge to a higher temperature than the current tank leaving temperature. Verify that the tank charging is stopped.
Step 7: Force the time to be between noon and 6:00 p.m. and simulate no cooling load by setting the indoor temperature setpoint above the ambient temperature. Verify that the tank does not discharge and the compressor is off.
Thermal energy storage (TES) system acceptance criteria shall be as follows:
  1. Verify that the system is able to charge the storage tank during off-peak periods where there is no cooling load.
  2. Verify that tank discharges during on-peak cooling periods.
  3. Verify that the compressor does not run and the tank does not discharge where there is no cooling demand during on-peak periods.
  4. Verify that the system does not operate during a morning shoulder period where there is no cooling demand.
  5. Verify that the system operates in direct mode (with compressor running) during the morning shoulder time period.
This section includes the certificate of acceptance forms referenced in Section E804.0 and Section E805.0.

CERTIFICATE OF ACCEPTANCE                                                                                                                         MECH-2A
Outdoor Air Acceptance                                                                                                                                  (Page 1 of 3)
Project Name/Address:

System Name or Identification/Tag:

System Location or Area Served:

Enforcement Agency:

Permit Number:
Note: Submit one Certificate of Acceptance for each system that
must demonstrate compliance.
Enforcement Agency Use: Checked by/Date

FIELD TECHNICIAN'S DECLARATION STATEMENT
  • I certify under penalty of perjury the information provided on this form is true and correct.
  • I am the person who performed the acceptance requirements verification reported on this Certificate of Acceptance (Field Technician).
  • I certify that the construction/installation identified on this form complies with the acceptance requirements indicated in the plans and specifications approved by the enforcement agency, and conforms to the applicable acceptance requirements and procedures specified in Section E801.0 through Section E806.0.
  • I have confirmed that the Installation Certificate(s) for the construction/installation identified on this form has been completed and is posted or made available with the building permit(s) issued for the building.
Company Name:

Field Technician's Name:

Field Technician's Signature:
Date Signed: Position with Company (Title):


RESPONSIBLE PERSON'S DECLARATION STATEMENT
  • I certify under penalty of perjury that I am the Field Technician, or the Field Technician is acting on my behalf as my employee or my agent and I have reviewed the information provided on this form.
  • I am a licensed contractor or registered design professional who is eligible per the requirements of the Authority Having Jurisdiction to take responsibility for the scope of work specified on this document and attest to the declarations in this statement (responsible person).
  • I certify that the information provided on this form substantiates that the construction/installation identified on this form complies with the acceptance requirements indicated in the plans and specifications approved by the enforcement agency, and conforms to the applicable acceptance requirements and procedures specified in Section E801.0 through Section E806.0.
  • I have confirmed that the Installation Certificate(s) for the construction/installation identified on this form has been completed and is posted or made available with the permit(s) issued for the building.
  • I will ensure that a completed, signed copy of this Certificate of Acceptance shall be posted, or made available with the building permit(s) issued for the building, and made available to the enforcement agency for all applicable inspections. I understand that a signed copy of this Certificate of Acceptance is required to be included with the documentation the builder provides to the building owner at occupancy.
Company Name:

Phone:
Responsible Person's Name:

Responsible Person's Signature:
License: Date Signed:

Position With Company (Title):

CERTIFICATE OF ACCEPTANCE                                                                                                                      MECH-2A
Outdoor Air Acceptance                                                                                                                               (Page 2 of 3)
Project Name/Address:

System Name or Identification/Tag:

System Location or Area Served:

Intent: Verify measured outside airflow reading is within ± 10% of the total required outside airflow value found in Section E805.1 through Section E805.2.2

Construction Inspection
  1. 1. Instrumentation to perform test includes, but not limited to:
    1. a. Watch.
    2. b. Calibrated means to measure airflow.
  2. 2. Check one of the following:
    1. □ Variable Air Volume (VAV) - Check as appropriate:
      1. a. Sensor used to control outdoor air flow must have calibration certificate or be field calibrated.
        1. □ Calibration certificate (attach calibration certification).
        2. □ Field calibration (attach results).
    2. □ Constant Air Volume (CAV) - Check as appropriate:
      1. □ System is designed to provide a fixed minimum OSA when the unit is on.

Outdoor Air Acceptance
A. Functional Testing. (Check appropriate column) CAV VAV
a. Verify unit is not in economizer mode during test - check appropriate column.
Step 1: CAV and VAV testing at full supply airflow.
a. Adjust supply to achieve design airflow.
b. Measured outdoor airflow reading (ft3/min).
c. Required outdoor airflow (ft3/min).
d. Time for outside air damper to stabilize after VAV boxes open (minutes).
e. Return to initial conditions ( check).
Step 2: VAV testing at reduced supply airflow.
a. Adjust supply airflow to either the sum of the minimum zone airflows or 30% of the total design airflow.
b. Measured outdoor airflow reading (ft3/min).
c. Required outdoor airflow (ft3/min).
d. Time for outside air damper to stabilize after VAV boxes open and minimum air
    flow achieved (minutes).
e. Return to initial conditions ( check).
B. Testing Calculations and Results. CAV VAV
Percent OSA at full supply airflow (%OAFA for Step 1).
a. %OAFA = Measured outside air reading/Required outside air (Step 1b / Step lc) % %
b. 90% ≤ %OAFA ≤ 110% Y/N Y/N
c. Outside air damper position stabilizes within 15 minutes (Step 1d < 15 minutes) Y/N Y/N
Percent OSA at reduced supply airflow (%OARA for Step 2).
a. %OARA = Measured outside air reading/required outside air (Step 2b / Step 2c). % %
b. 90% ≤ %OARA ≤ 110%. Y/N
c. Outside air damper position stabilizes within 15 minutes (Step 2d < 15 minutes). Y/N
Note: Shaded boxes do not apply for CAV systems.
For SI units. 1 cubic foot per minute = 0.00047 m3/s

CERTIFICATE OF ACCEPTANCE                                                                                                                      MECH-2A
Outdoor Air Acceptance                                                                                                                               (Page 3 of 3)
Project Name/Address:

System Name or Identification/Tag:

System Location or Area Served:

C. PASS/FAIL Evaluation ( check one):
PASS: All Construction Inspection responses are complete and Testing Calculations & Results responses are positive (Y -yes).
FAIL: Any Construction Inspection responses are incomplete OR there is one or more negative (N -no) responses in Testing Calculations & Results section. Provide explanation below. Use and attach additional pages if necessary.

CERTIFICATE OF ACCEPTANCE                                                                                                                     MECH-3A
Constant Volume Single Zone Unitary Air Conditioner and Heat Pump Systems                                 (Page 1 of 3)
Project Name/Address:

System Name or Identification/Tag:

System Location or Area Served:

Enforcement Agency:

Permit Number:
Note: Submit one Certificate of Acceptance for each system that
must demonstrate compliance.
Enforcement Agency Use: Checked by/Date

FIELD TECHNICIAN'S DECLARATION STATEMENT
  • I certify under penalty of perjury the information provided on this form is true and correct.
  • I am the person who performed the acceptance requirements verification reported on this Certificate of Acceptance (Field Technician).
  • I certify that the construction/installation identified on this form complies with the acceptance requirements indicated in the plans and specifications approved by the enforcement agency, and conforms to the applicable acceptance requirements and procedures specified in Section E801.0 through Section E806.0.
  • I have confirmed that the Installation Certificate(s) for the construction/installation identified on this form has been completed and is posted or made available with the building permit(s) issued for the building.

Company Name:

Field Technician's Name:

Field Technician's Signature:
Date Signed: Position with Company (Title):


RESPONSIBLE PERSON'S DECLARATION STATEMENT
  • I certify under penalty of perjury that I am the Field Technician, or the Field Technician is acting on my behalf as my employee or my agent and I have reviewed the information provided on this form.
  • I am a licensed contractor or registered design professional who is eligible per the requirements of the Authority Having Jurisdiction to take responsibility for the scope of work specified on this document and attest to the declarations in this statement (responsible person).
  • I certify that the information provided on this form substantiates that the construction/installation identified on this form complies with the acceptance requirements indicated in the plans and specifications approved by the enforcement agency, and conforms to the applicable acceptance requirements and procedures specified in Section E801.0 through Section E806.0.
  • I have confirmed that the Installation Certificate(s) for the construction/installation identified on this form has been completed and is posted or made available with the permit(s) issued for the building.
  • I will ensure that a completed, signed copy of this Certificate of Acceptance shall be posted, or made available with the building permit(s) issued for the building, and made available to the enforcement agency for all applicable inspections. I understand that a signed copy of this Certificate of Acceptance is required to be included with the documentation the builder provides to the building owner at occupancy.
Company Name:

Phone:
Responsible Person's Name:

Responsible Person's Signature:
License: Date Signed:

Position With Company (Title):

CERTIFICATE OF ACCEPTANCE                                                                                                                      MECH-3A
Constant Volume Single Zone Unitary Air Conditioner and Heat Pump Systems                                  (Page 2 of 3)
Project Name/Address:

System Name or Identification/Tag:

System Location or Area Served:

Intent: Verify the individual components of a constant volume, single-zone, unitary air conditioner and heat pump system function correctly, including: thermostat installation and programming, supply fan, heating, cooling, and damper operation

Construction Inspection
  1. 1. Instrumentation to perform test includes, but not limited to:
    1. a. None required
  2. 2. Installation
    1. □ Thermostat is located within the space-conditioning zone that is served by the HVAC system.
  3. 3. Programming (check all of the following):
    1. □ Thermostat meets the temperature adjustment and dead band requirements.
    2. □ Occupied, unoccupied, and holiday schedules have been programmed per the facility's schedule.
    3. □ Preoccupancy purge has been programmed to meet the requirements of Section E805.3 through Section
         E 805.3.2.

A. Functional Testing Requirements.                                                                                                 Operating Modes
Cooling load during unoccupied condition
Cooling load during occupied condition
Manual override
No-load during unoccupied condition
Heating load during unoccupied condition
No-load during occupied condition
Heating load during occupied condition
Step 1: Check and verify the following for each simulation mode required. A B C D E F G
a. Supply fan operates continually.
b. Supply fan turns off.
c. Supply fan cycles on and off.
d. System reverts to "occupied'' mode to satisfy any condition.
e. System turns off when manual override time period expires.
f. Gas-fired furnace, heat pump, or electric heater stages on.
g. Neither heating or cooling is provided by the unit.
h. No heating is provided by the unit.
i. No cooling is provided by the unit.
j. Compressor stages on.
k. Outside air damper is open to minimum position.
I. Outside air damper closes completely.
m. System returned to initial operating conditions after all tests have been completed: Y/N

B. Testing Results A B C D E F G
Indicate if Passed (P), Failed (F), or N/A (X), fill in appropriate letter.

CERTIFICATE OF ACCEPTANCE                                                                                                                    MECH-3A
Constant Volume Single Zone Unitary Air Conditioner and Heat Pump Systems                                (Page 3 of 3)
Project Name/Address:

System Name or Identification/Tag:

System Location or Area Served:

C. PASS/FAIL Evaluation. (check one):
PASS: All Construction Inspection responses are complete and Testing Results responses are "Pass" (P).
FAIL: Any Construction Inspection responses are incomplete OR there is one or more "Fail" (F) responses in
Testing Results section. Provide explanation below. Use and attach additional pages if necessary.

CERTIFICATE OF ACCEPTANCE                                                                                                                     MECH-4A
Air Distribution Systems Acceptance                                                                                                        (Page 1 of 3)
Project Name/Address:

System Name or Identification/Tag:

System Location or Area Served:

Enforcement Agency:

Permit Number:
Note: Submit one Certificate of Acceptance for each system that
must demonstrate compliance.
Enforcement Agency Use: Checked by/Date

FIELD TECHNICIAN'S DECLARATION STATEMENT
  • I certify under penalty of perjury the information provided on this form is true and correct.
  • I am the person who performed the acceptance requirements verification reported on this Certificate of Acceptance (Field Technician).
  • I certify that the construction/installation identified on this form complies with the acceptance requirements indicated in the plans and specifications approved by the enforcement agency, and conforms to the applicable acceptance requirements and procedures specified in Section E801.0 through Section E806.0.
  • I have confirmed that the Installation Certificate(s) for the construction/installation identified on this form has been completed and is posted or made available with the building permit(s) issued for the building.
Company Name:

Field Technician's Name:

Field Technician's Signature:
Date Signed: Position with Company (Title):


RESPONSIBLE PERSON'S DECLARATION STATEMENT
  • I certify under penalty of perjury that I am the Field Technician, or the Field Technician is a