1. Standard 90.1 ASHRAE Columbus Chapter
American Society of Heating, Refrigerating and Air-Conditioning Engineers, Inc.
Standard 90.1
Energy Standard for Buildings Except Low-Rise Residential Buildings
Presented to:
October 21, 2013
ASHRAE Columbus Chapter

2. Agenda 90.1-2010 – What Changed 90.1-2013 – What Changed
– Items Being Considered
Questions

3. Development of

4. HVAC Equipment Several Changes Made to Equip Efficiency.
Process for Equipment Efficiency Upgrades.
AHRI
DOE
90.1

5. Notable Changes in
Computer Rooms no longer exempted from standard.
2.3 The provisions of this standard do not apply to
C. equipment and portions of building systems that use energy primarily to provide for industrial, manufacturing, or commercial processes.

6. Computer Rooms Economizers:
TABLE 6.5.1B Minimum Fan-Cooling Unit Size for Which an Economizer is Required for Computer Rooms
Climate Zones Cooling Capacity for Which an Economizer is Required
1a, 1b, 2a, 3a, 4a No economizer requirement
2b, 5a, 6a, 7, 8 ≥135,000 Btu/h
3b, 3c, 4b, 4c, 5b, 5c, 6b ≥65,000 Btu/h

7. Computer Rooms Economizers (Exceptions):
j. Systems primarily serving computer rooms where:
1. the total design cooling load of all computer rooms in the building is less than 3,000,000 Btu/h and the building in which they are located is not served by a centralized chilled water plant, or
2. the room total design cooling load is less than 600,000 Btu/h and the building in which they are located is served by a centralized chilled water plant., or
3. the local water authority does not allow cooling towers, or
4. less than 600,000 Btu/h of computer room cooling equipment capacity is being added to an existing building
Computer Rooms
Economizers (Exceptions):
j. Systems primarily serving computer rooms where:
1. the total design cooling load of all computer rooms in the building is less than 3,000,000 Btu/h and the building in which they are located is not served by a centralized chilled water plant, or
2. the room total design cooling load is less than 600,000 Btu/h and the building in which they are located is served by a centralized chilled water plant., or
3. the local water authority does not allow cooling towers, or
4. less than 600,000 Btu/h of computer room cooling equipment capacity is being added to an existing building

8. Computer Rooms
Economizers (Exceptions): k. Dedicated systems for computer rooms where a minimum of 75% of the design load serves: 1. those spaces classified as an essential facility 2. those spaces having a mechanical cooling design of Tier IV as defined by ANSI/TIA those spaces classified under NFPA 70 Article 708 – Critical Operations Power Systems (COPS) 4. those spaces where core clearing and settlement services are performed such that their failure to settle pending financial transactions could present systemic risk as described in “The Interagency Paper on Sound Practices to Strengthen the Resilience of the US Financial System, April 7, 2003”

9. Computer Rooms Water Economizers Design Capacity
Water economizer systems shall be capable of cooling supply air by indirect evaporation and providing up to 100% of the expected system cooling load at outdoor air temperatures of 50°F dry bulb/45°F wet bulb and below.
(Exceptions):
Systems primarily serving computer rooms in which 100% of the expected system cooling load at 40°F dry bulb / 35°F wet bulb is met with evaporative water economizers.
b. Systems primarily serving computer rooms with dry cooler water economizers which satisfy 100% of the expected system cooling load at 35°F dry bulb.

10. Computer Rooms
TABLE 6.8.1K Air Conditioners and Condensing Units Serving Computers Rooms Minimum SCOP-127 Efficiency Down flow units / Upflow units ANSI/ASHRAE 127

11. Notable Changes in 90.1-2010 Energy Recovery
Exhaust Air Energy Recovery. Individual fan
systems that have both a design supply air capacity of
5000 cfm or greater and have a minimum outdoor air supply of 70% or greater of the design supply air quantity shall have an energy recovery system with at least 50% recovery effectiveness.

12. Energy Recovery

13. Notable Changes in 90.1-2010 Single Zone VAV
New Requirements for chilled water and commercial package rooftop units to have 2 speed or VAV fans.

14. Single Zone VAV
Air-handling and fan-coil units with chilled-water cooling coils and supply fans with motors greater than or equal to 5 hp shall have their supply fans controlled by two-speed motors or variable-speed drives. At cooling demands less than or equal to 50%, the supply fan controls shall be able to reduce the airflow to no greater than the larger of the following:
One half of the full fan speed, or
2. The volume of outdoor air required to meet the ventilation
requirements of Standard 62.1.

15. Single Zone VAV
b. Effective January 1, 2012, all air-conditioning equipment and air-handling units with direct expansion cooling and a cooling capacity at AHRI conditions greater than or equal to 110,000 Btu/h that serve single zones shall have their supply fans controlled by two-speed motors or variable speed drives. At cooling demands less than or equal to 50%, the supply fan controls shall be able to reduce the airflow to no greater than the larger of the following:
Two-thirds of the full fan speed, or
2. The volume of outdoor air required to meet the ventilation requirements of Standard 62.1.

16. Notable Changes in 90.1-2010 Lab Exhaust Fan Power (p)
Fan power limits placed on laboratory exhaust fans.
Fan System Power Limitation
Exception:
c. Fans exhausting air from fume hoods. Note: If this
exception is taken, no related exhaust side credits
shall be taken from Table B and the Fume
Hood Exhaust Exception Deduction must be taken
from Table B.

17. Laboratory Exhaust Fans

18. Notable Changes in 90.1-2010 Fume Hood Exhaust
Modifications made to fume hood exhaust requirements
Fume Hoods. Buildings with fume hood systems
having a total exhaust rate greater than 15,000 cfm shall include at least one of the following features:
a. VAV hood exhaust and room supply systems capable of reducing exhaust and makeup air volume to 50% or less of design values.
b. Direct makeup (auxiliary) air supply equal to at least 75% of the exhaust rate, heated no warmer than 2°F below room setpoint, cooled to no cooler than 3°F above room setpoint, no humidification added, and no simultaneous heating and cooling used for dehumidification control.
c. Heat recovery systems to precondition makeup air from fume hood exhaust in accordance with Section , Exhaust Air Energy Recovery, without using any exception.

19. Fume Hood Exhaust 6.5.7.2 Laboratory Exhaust Systems. Buildings with
laboratory exhaust systems having a total exhaust rate greater
than 5000 cfm shall include at least one of the following features:
VAV laboratory exhaust and room supply system capable of reducing exhaust and makeup air flow rates and/or incorporate a heat recovery system to precondition makeup air from laboratory exhaust that shall meet the following:
A + B×(E/M) ≥50%
Where:
A = Percentage that the exhaust and makeup air flow rates can be reduced from design conditions.
B = Percentage sensible recovery effectiveness.
E = Exhaust airflow rate through the heat recovery device at design conditions
M = Makeup air flow rate of the system at design conditions.

20. Notable Changes in 90.1-2010 Kitchen exhaust hoods (ax)
Worked with TC to properly characterize exhaust hoods and
makeup air for kitchens. Many years of improper language that
encouraged designs that wasted energy.
Kitchen Hoods. Individual kitchen exhaust
hoods larger than 5000 cfm shall be provided with makeup air
sized for at least 50% of exhaust air volume that is
a. unheated or heated to no more than 60°F and
b. uncooled or cooled without the use of mechanical cooling

21. Kitchen Exhaust 6.5.7.1.1 Replacement air introduced directly into the
hood cavity of kitchen exhaust hoods shall not exceed 10% of
the hood exhaust airflow rate.

22. Kitchen Exhaust
Conditioned supply air delivered to any space with a kitchen hood shall not exceed the greater of:
the supply flow required to meet the space heating or cooling load
b. 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

23. Kitchen Exhaust
If a kitchen/dining facility has a total kitchen hood exhaust airflow rate greater than 5,000 cfm then each hood shall have an exhaust rate that complies with Table If a single hood, or hood section, is installed over appliances with different duty ratings, then the maximum allowable flow rate for the hood or hood section shall not exceed the Table values for the highest appliance duty rating under the hood or hood section. Refer to ASHRAE Standard 154 for definitions of hood type, appliance duty, and net exhaust flow rate.
Exception: At least 75% of all the replacement air is transfer air that would otherwise be exhausted.

24. Kitchen Exhaust
If a kitchen/dining facility has a total kitchen hood exhaust airflow rate greater than 5,000 cfm then it shall have one of the following:
At least 50% of all replacement air is transfer air that would otherwise be exhausted.
Demand ventilation system(s) on at least 75% of the exhaust air. Such systems shall be capable of at least 50% 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.
c. Listed energy recovery devices with a sensible heat recovery effectiveness of not less than 40% on at least 50% of the total exhaust airflow.

25. Notable Changes in 90.1-2010 Garage ventilation
Reduce airflow if not required to reduce fan energy and heating
energy.

26. Garage Ventilation 6.4.3.4.5 Enclosed Parking Garage Ventilation.
Enclosed parking garage ventilation systems shall automatically detect contaminant levels and stage fans or modulate fan airflow rates to 50% or less of design capacity provided acceptable contaminant levels are maintained.
Exceptions:
a. Garages less than 30,000 ft2 with ventilation systems that do not utilize mechanical cooling or mechanical heating
b. Garages that have a garage area to ventilation system motor nameplate hp ratio that exceeds 1500 ft2/hp and do not utilize mechanical cooling or mechanical heating.
c. Where not permitted by the authority having jurisdiction.

27. What Changed

28. 90.1-2013 Notable Activities Envelope
1. Significant increase to insulation values (bb)
Standard
Columbus, Ohio
Fairbanks, Alaska
Roof Insulation (ab. deck)
R-20
Metal Framed Wall
R-13 + R7.5 c.i.
Addendum to
Columbus, Ohio
Fairbanks, Alaska
Roof Insulation (ab. deck)
R-30
R-35
Metal Framed Wall
R-13 + R10 c.i.
R-13 + R18.8 c.i.

29. Economizer/Humidification System
Not really a new requirement but clarified applications where hydronic cooling and humidification are utilized to maintain dewpoints above 35F, that a water economizer shall be utilized if an economizer is required.

30. VAV Static Pressure Sensor Location (s)
Located such that set point no greater than 1.2” wg or shall have automatic reset controls based on damper position (reset logic shall have alarm provisions for rogue zones with manual
disable)

31. DDC Requirements (aa)
Most new buildings and renovations to existing systems currently with DDC

32. Escalators & Moving Walkways (b)
When not conveying passengers shall operate at minimum speed per ASME A17.1

33. Fan Efficiency (u) Minimum FEG = 67 Per AMCA 205 Exceptions:
-single or multiple
fans 5 hp or less.
-Part of a system with
a 3rd party
certification or
covered by another
efficiency standard (i.e. part of pkg equip)

34. Cooling Tower Flow Turndown (af)
Previously the standard required towers with motors 7.5 hp and larger to be at least 2 speed. This addendum requires that for multi-tower installations that utilizes VFDs that the towers not be staged, but rather control all fans at the same speed.
Multiple Tower installations with multiple pumps (in parallel) shall be able to reduce flow to 50% of the design flow rate (really a mfgr reqt)

35. Small Motor Efficiency (aj)
Motors 1/12 hp to less than 1 hp shall be ECM or minimum 70% efficient. Also shall have means to adjust motor speed for balancing or remote control. Targets cooling applications (fan coils and fan powered boxes), though have exception when fan is for heating only

36. Hydronic Variable Flow(ak)(90.1-2016)
Requires variable flow on all heating and chilled water systems if there are 3 or more control valves. No longer a hp exemption. Also requires water temperature reset (chilled and htg water based on valve position unless using valve position to comply with variable flow requirement).

37. Boiler System Design Input (Btu/h) Minimum Turndown Ratio (am) **
≥ 1,000,000 and less than or equal to 5,000, (3 to 1)
> 5,000,000 and less than or equal to 10,000,000 (4 to 1)
> 10,000, (5 to 1)
Requires the use of multiple single stage boilers or the use of modulating boilers.

38. Computer Room PUE (ap) PUE=Total Power ÷ Total IT Power
6.6 Alternative Compliance Path
Climate Zone
PUE a 1A
1.61 2A
1.49 3A
1.41 4A
1.36 5A 6A
1.34 1B
1.53 2B
1.45 3B
1.42 4B
1.38 5B
1.33 6B 3C
1.39 4C 5C 7
≤ 1.32 8
≤ 1.30
PUE=Total Power ÷ Total IT Power

39. Mechanical Cooling Capacity
Fan Airflow Control (aq) **
Each cooling system listed in table shall be designed to vary the indoor fan airflow as a function of load and shall comply with the following requirements.
Table Effective Dates for Fan Control
Cooling System Type
Fan Motor Size
Mechanical Cooling Capacity
Effective Date
DX Cooling
any
≥110,000 Btu/h
1/1/2012
≥75,000 Btu/h
1/1/2014
≥65,000 Btu/h
1/1/2016
Chilled Water and
Evaporative cooling
≥5 HP
Any
1/1/2010
≥1/4 HP

40. Humidification and Preheat (as)
Requires humidifiers tubes to be provided with R-0.5 value insulation and restricts preheat coils from generating heat when AHU in mechanical cooling or economizer operation.
Face and bypass
Preheat coil
Steam Humidifier

41. Door Switches (ba) (started as window switches)
Doors (including doors more than 50% glass) require switches to disable or setup/setback cooling/heating to 90F/55F. Exclusions for door with automatic closers, loading dock doors.
90.1 Definition-Doors that are more
than 50% glass are considered
fenestration.

42. Service Water Heater Efficiency (bo) **
Gas hot water systems over 1,000,000 btuh (total bldg) input require minimum 90% thermal efficiency (i.e. condensing style water heaters or heat pump water heaters).
High Efficiency
Condensing Style
Standard Efficiency
Exemption: Individual gas water heaters less than
100,000 btuh input.

43. Commercial Refrigeration (bq)
3 Addendums passes in for 2013 standard, with the first 2 primarily restating current federal requirements. This addendum added additional requirements.
Refrigerated display cases with automatic lighting controls.
Temperature based defrost termination (in addition to time based).
Anti-sweat heater controls (based on ambient dewpoint)
Condensers with variable fan speed control.
Crankcase heaters shut-off on compressor run.

44. Demand Control Ventilation (bs)
Increased stringency from 40p/1000 sq.ft. to 25p/1000 sq.ft.
Occupancies that would be included that are not included now (based on Standard 62.1 default densities) would be:
Classrooms; Music/dance class; Conference lobbies; Office Reception; Museum; Mall commons; Gym; and health club. Daycare; computer labs; and break rooms.
Exempt occupancies would be: Correctional cells; Daycare sickrooms; Science labs; Barber; beauty & nail salons; and bowling alley seating.

45. Energy Recovery (bt)
Table a Energy Recovery Requirement (ventilation systems operating <8000 hr/yr)
Zone
% Outdoor Air at Full Design Airflow Rate
≥10% and <20%
≥20% and <30%
≥30% and <40%
≥40% and <50%
≥50% and <60%
≥60% and <70%
≥70% and <80%
≥80%
Design Supply Fan Airflow Rate (cfm)
3B, 3C, 4B, 4C, 5B NR
1B, 2B,5C
≥26000
≥12000
≥5000
≥4000 6B
≥28000
≥26500
≥11000
≥5500
≥4500
≥3500
≥2500
≥1500
1A, 2A, 3A, 4A, 5A, 6A
≥16000
≥2000
≥1000 ≥0
7,8

46. 24x7 Energy Recovery (cy)
Table b Energy Recovery Requirement (ventilation systems operating ≥8000 hrs/yr)
Zone
% Outdoor Air at Full Design Airflow Rate
≥10% and <20%
≥20% and <30%
≥30% and <40%
≥40% and <50%
≥50% and <60%
≥60% and <70%
≥70% and <80%
≥80%
Design Supply Fan Airflow Rate (cfm) 3C NR
1B, 2B, 3B, 4C, 5C
≥19500
≥9000
≥5000
≥4000
≥3000
≥1500
>0
1A, 2A, 3A, 4B, 5B
≥2500
≥2000
≥1000
≥500
4A, 5A, 6A, 6B, 7, 8

47. Vestibule Heat (ca)
Deactivate heat above 45F outside and limit heating to 60F.
“Vestibules are installed to reduce infiltration into the building. The benefit of a vestibule during the heating season is negated if the vestibule is heated to the heating set point of the adjacent space. At the same time, tempering of vestibule air is needed to avoid ice formation.”

48. VAV Dual Maximum (ck)
Elimination of 30% minimum reheat for DDC boxes, requires reduction to 20% of maximum supply air at deadband, then heat to maximum supply air (20F above space temperature), then a maximum of 50% of air can be reheated.

49. Evaporative Water Economizer Dry Cooler Water Economizer
Water Economizer Sizing Reqts Comp Rms (de)
Table Water Economizer Sizing Dry-Bulb and Wet-Bulb Requirements
for Computer Rooms
Zone
Evaporative Water Economizer
Dry Cooler Water Economizer
Dry-Bulb (°F)
Wet-Bulb (°F) 1 A NR B 2
40.0
35.0
30.0 3
25.0 C 4 5
20.0 6 7 8 :
Evap Water Econ at 40F db/ 35F wb
Drycoolers 35F db.

50. Humidity Control (di)
Restricts the use of fossil fuels or electric for humidification above 30% RH. Recognizes some exceptions such as museums and hospitals or accreditation standards.

51. 90.1-2016 Items Being Considered

52. Elevator Efficiency (cw)
Computer Room Definition (cs)
Expanded Water Economizer Reqts (du)
Evaporative Precoolers for Pkg Air Cooled
Heat Pumps/VRF + Prescriptive Reqts
Bldg Energy Recovery Ventilator Reqt

53. Fan and Pump Efficiency (DOE)
Occupant Based HVAC Controls (62.1) **
Enhanced Demand Control Ventilation
Air Cooled vs Water Cooled
Heat Recovery from Condenser Heat **

54. Advanced Energy Standards (AES) Initiatives
Hydronics working group
RTU working group

55. Chiller Water “System” Example
Regulations
No regulations
ASHRAE fan power requirement, no approach requirement and ignore water use
Do not address multiple chillers and towers although most are applied that way
Cooling Tower
Condenser Water Pump
No focus on condenser water pumping power other than a pipe sizing requirement
Current 550/590 Chiller Standard and Certification focus
ASHRAE 90.1 Full and part load efficiency
Condenser
Compressor
No focus on chilled water pumping power other than pipe sizing
Evaporator
No integration of economizers, exhaust fans, ERV and IAQ
Chilled Water Pump
Air Handler
Outside
Air
No focus on duct pressure drop and very little on applied fan power
Very little focus on the effective air distribution
Conditioned Space

56. Packaged Ducted Rooftop “System” Example
Demand ventilation not reflected in ratings
Economizer and outside air not reflected in ratings
Rating of the rooftop EER and IEER with part of the fan power is covered by AHRI 340/360 but we do not certify the full operating map
Packaged Rooftop
ERV/Rooftop CEF can be used for full load, but not part load and annualized
Power Exhaust not included in ratings
No annualized performance for heating
Only part of the duct work pressure drop included in the ratings
On VAV units reheat not reflected in ratings
Very little focus on the effective air distribution
Conditioned Space