Transcript Slide 1

STD 90.1-2010, A FIRST LOOK
Mechanical Provisions
Drake H. Erbe
Airxchange, Inc.
Rockland, MA
781-871-4817 X313
[email protected]
www.airxchange.com
Std 90.1-2010
Mechanical Provisions
6/29/2010
Summary of areas, changes, addenda
• Equipment Efficiencies tables
– Changes in existing equipment-a,k,y,ao,t,bw,aj,bk
– Addition of new equipment-l,o,co,ad, cp,bg,bu
– Part load-s,m
– Expanded certified conditions-bl,bt
• Equipment Requirements/Limitations
– 2 speed fans-n
– VSD on pumps and fans-ak,cv,n
– Demand control on simple systems-ap
– Open cooling towers >1100-u
– Fan power-p, dj,
– Dampers-at,cb
Summary of areas, changes, addenda
• Airside System Requirements
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Supply air reset-bh
Ventilation reset-ck
VAV single zone fan power-ca
Energy Recovery-e
Zone controls-h,as,bx
• Waterside System Requirements
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Pump head calculations-v
WSHP systems-ak
Pipe sizing-af,cc
Piping Insulation-ba,bi
Summary of areas, changes, addenda
• Economizers
– Data Centers-bu
– Trade-off-au
– New/different requirements-cy
• Additional miscellaneous
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Laboratory Systems-as,bx
Kitchen Hoods-ax
Duct Leakage-cq
Garage Ventilation-di
Elevators-df
Cooling Towers
Addenda a,l
• This adds minimum efficiency and certification requirements for both axial
and centrifugal fan closed-circuit cooling towers (also known as fluid
coolers) into Table 6.8.1G. And clearly identifies open and closed
requirements.
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Cooling Towers
Addendum u
• This addendum puts a limitation
on centrifugal fan cooling tower
which typically use more energy
than axial fan cooling towers.
• Above 1,100 gpm at standard
rating conditions the centrifugal
fan cooling towers will have to
meet the efficiency requirements
for axial fan towers with a few
exceptions
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Dehumidification
Addendum b
• This addendum provides some clarification to dehumidification
requirements in 6.5.2.3 when applied to laboratories and other spaces
covered by other standards.
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Humidification
Addendum c
• This addendum makes some further revisions to the
humidification section 6.5.2.3
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Zone Controls
Addendum h
This change includes a new exception to Section 6.5.2.1 that is geared toward zones with direct digital
controls (DDC). The new exception (exception b) largely addresses the apparent conflict between
Standards 55, 62.1, and 90.1. This conflict is that the current 30% reheat maximum typically
requires very high supply air temperatures (e.g., >100°F) to meet peak heating load. High supply
air temperatures result in poor comfort per Standard 55 and poor ventilation effectiveness per
Standard 62.1.
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Laboratory Exhaust Systems
Addendum as
• This addendum makes some revisions to 6.5.2.1 and completely redoes
6.5.7 to clearly outline requirements for laboratory exhaust systems, and
adds a definition for sensible effectiveness used in 6.5.7.
• 6.5.2.1 major revisions
– Adds exception a4. The air flow rate required to comply with applicable codes or
accreditation standards, such as pressure relationships or minimum air change rates.
– 3c Deletes Zones where special pressurization relationships, cross-contamination
requirements, or code-required minimum circulation rates are such that variable air
volume systems are impractical. Laboratory exhaust systems that comply with 6.5.7.2.
• Section 3.2 add
sensible recovery effectiveness: change in the dry-bulb temperature of the outdoor air supply
divided by the difference between the outdoor air and return air dry-bulb temperatures,
expressed as a percentage.
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Laboratory Exhaust Systems
Addendum as
Changes to 6.5.7
• Now for laboratory exhaust systems
• Reduced from 15000 to 5000 cfm exhaust
• Better definition of VAV with heat recovery
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Zone Controls
Addendum bx
• Revises exceptions to 6.5.2.1,
which expands upon revisions
made by addendum-h and as
to 90.1-2007
• Change limits ceiling supply air
temperature to 20oF
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Furnaces & Water Heating
Addenda k,ao
• These addenda revise Tables 6.8.1E and 7.8 to more clear and
informative. Table 7.8 is updated to reflect the current federal efficiency
levels for residential water heaters, and adds a requirement for electric
table top water heaters.
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Heat Pump Pool Heaters
Addendum y
• This addendum establishes ARI 1160 as the test procedure for heat-pump
pool heaters and requires that the minimum coefficient of performance
(COP) of 4 be met at the low outdoor temperature of 50°F (instead of the
high outdoor temperature of 80°F currently required).
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Chillers
Addendum
m
This addendum establishes, effective January 1, 2010 an additional path of
compliance for water-cooled chillers.
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– Path A is intended for applications where significant operating time is
expected at full-load conditions.
– On the other hand, Path B is an alternative set of efficiency levels for water
cooled chillers intended for applications where significant time is expected at
part load.
– Compliance with the standard can be achieved by meeting the requirements
of either Path A or Path B.
– However, both full-load and IPLV levels must be met to fulfill the
requirements of Path A or Path B.
The addendum also combines all water-cooled positive displacement chillers into
one category and adds a new size category for centrifugal chillers at or above 600
tons.
The air cooled chiller without condenser equipment category has been eliminated.
All air-cooled chillers without condensers must now be rated with matching
condensers.
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Chillers
Addendum m
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Chillers
Addenda
bl,bt
These addenda are intended to
bring a
total of approximately 85% of the chillers
under the standard.
Addendum bt extends the range where
the Kadj can be used for centrifugals thus
expanding the range where certification
can be applied for centrifugals and the
scope of the minimum efficiency
requirements.
The kadj equation has been revised and
also includes a leaving evaporator
temperature correction.
A manufacturers nameplate requirement
is also included
Addendum bl includes glycol and brine
6.4.1.2.2 Positive displacement (air- and watercooled) chilling packages. Equipment with a
leaving evaporator fluid temperature higher than
32°F, shall show compliance with Table 6.8.1C
when tested or certified with water at standard
rating conditions, per the referenced test
procedure.
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DX & AHU Speed Control
Addendum n
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Variable-air-volume fan control is currently
required in the standard for multiple-zone
systems.
This proposal extends these requirements for
large single-zone units. Important aspects of
this proposal include the following:
– It applies to both unitary (packaged)
equipment and chilled water air-handling
units.
– It only applies to DX units with a cooling
capacity greater than or equal to 110,000
Btu/h.
– It only applies to chilled water systems with
motors greater than 5 HP
The proposal can be met using either two-speed
motors or variable-speed drives on the supply
fan(s).
The minimum speed requirement is set at 67%
fan speed to avoid coil freezeup problems
It does not take effect until 1/1/2012 for DX
systems and 1/1/2010 for chilled water systems
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Energy Recovery
Addendum e
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This addendum revises the requirements for exhaust air energy recovery and extends the
requirements to a broader range of buildings.
6.5.6.1 Exhaust Air Energy Recovery. Each fan system shall have an energy recovery system when
the system’s supply air flow rate exceeds the value listed in table 6.5.6.1 based on the climate
zone and percentage of outdoor air flow rate at design conditions.
The simplified version now refers to 6.5.6
The addendum also revises the some of the wording of the existing requirements and exceptions
Adds exception j Systems expected to operate less than 20 hrs per week at the outdoor air
percentage covered by table 6.5.6.1
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Fan Power Limitation
Addendum
p
This addendum is the second phase of
correcting the fan power limitation
deficiencies of Standard 90.1-2004. The
first phase was corrected by Addendum
ac to the 2004 standard and is included
in Standard 90.1-2007. That addendum
addressed all fan systems with exception
of those systems serving fume hoods.
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Fan Power Limitation
Addendum dj
The current wording of Table 6.5.3.1.1B does not provide any limit on the pressure drop of energy
recovery devices. This addendum limits the fan energy allowance for energy recovery devices to
values that approximate the results of the economic analysis conducted for addendum e, with
some allowance to permit adequate pressure drop for products near the minimum recovery
effectiveness of 50%. A separate allowance is also created for coil runaround loop systems.
TABLE 6.5.3.1.1B Fan Power Limitation Pressure Drop Adjustment
(Revisions to the table in part)
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IEER
Addendum s
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This addendum is actually a continuation of addendum g to the 2004 standard
which increased the efficiencies of packaged equipment
This addendum completes the change by adding new minimum efficiency
requirements for the new AHRI 340/360 IEER part load metric
The new metric corrects some issues with the old IPLV and better reflects the
operation of commercial equipment indoor fans.
New AHRI IEER part load metric
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Efficiency Moves
In 2010 the HCFC refrigerants
are eliminated and HFC’s must
be used
Packaged and Split system unit efficiencies
2005 Energy Act
ASHRAE 2001
Federal Limit (Today)
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13.0 (06)
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13.0 (06-08)
(ASHRAE 2010)
Federal Limit (2010)
ASHRAE 1989
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11.2 (2010)
11.0 (2010)
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10.3
9.7 9.7
9.7 9.7
9.7
10.0 (2010)
9.5
8.9
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8.5
8.5
9.7 (2010)
(2010)9.2
8.3
8
7
<5 Tons 1P
<5 Tons 3P
SEER
5 to 11.2 Tons 11.2 to 20 Tons 20 to 63 Tons
>63 Tons
EER/IPLV
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IEER
Addendum s
There are also additional Tables for
water cooled, and heat pumps
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PTAC & PTHP
Addenda t,bw
• On October 7, 2008, the
Department of Energy (DOE)
completed a rulemaking and
published a final rule establishing
new federal minimum energy
efficiency standards for package
terminal air conditioners (PTACs) and
heat pumps (PTHPs).
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Liquid-to-Liquid Heat Exchangers
Addendum ad
• This addendum adds a requirement for liquid
to liquid heat exchangers
A future addendum will add minimum efficiency requirements
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Pump Head Calculation
Addendum v
• Addendum v added a requirement that pump head must be
calculated. A reference to the Handbook of Fundamentals
was deleted and an ANSI/ASHRAE/ACCA standard inserted.
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Radiant Panels
Addendum ae
• This addendum adds a requirement for insulating the
surfaces of radiant panels that do not face
conditioned spaces.
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Pipe Sizing
Addenda af,cc
• These addenda add a requirement for pipe sizing based on a table which
is a function of the flow and number of operating hours. It currently only
applies to chilled water and condenser water
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Pipe Insulation-Heating
Addendum bi
• This addendum makes significant changes to the
requirements for pipe insulation
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Pipe Insulation-Cooling
Addendum bi
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Non-Metallic Piping
Addendum ba
• This addendum clarifies how to apply the
piping insulation to non-metallic piping
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Hydronic
Addendum ak
This addendum makes changes to the pumping requirements including dropping
the HP from 10 HP to 7.5 for variable speed pump plus and eliminates the pump
head requirement
It includes some new requirements for WSHP loops
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Demand Control Ventilation
Addendum ap
• This addendum corrects a loop hole for the
requirements of demand control ventilation in the
simplified section of chapter 6
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Dampers
Addendum at
• Revises the requirements for dampers and damper leakage as
defined in section 6.4.3.4
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Dampers
Addendum cb
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This addendum addresses a number of issues with dampers
– The simplified approach now matches the prescriptive requirements
– Allows backdraft dampers only on exhaust and relief, not outside air
– Requires low leak dampers in Zone 5a
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Economizer Trade-Off
Addendum au
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This addendum complements
the addendum g to the 2004
standard and addendum s to
the 2007 standard which
increased the efficiency of
packaged equipment and added
the IEER
This addendum implements a
new requirement for the
elimination of the air
economizer in applicable zones
and is based on the new IEER
metrics
The full load metrics stay the
same but the IEER levels
increase to compensate for the
lost energy savings without the
economizer
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Economizers
Addendum cy
This addendum makes several revisions to the economizer
requirements in section 6.5.1 and in section 6.3.2.
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With increased envelope insulation levels and higher internal plug loads commercial
buildings are operating in cooling at lower ambient temperatures. This allows for greater air
and water economizers to be used instead of mechanical cooling.
Using the ASHRAE benchmark building models a detailed energy and economic analysis was
conducted and found that
– requirements for the use of economizers can be justified in additional zones including
2a, 3a, and 3b.
– the threshold limit on the size of the unit above which economizers are required can be
decreased from 135,000 and 65,000 Btu/h to 54,000 Btu/hr.
Integrated economizers allow for the use of economizers and mechanical cooling to meet
the cooling loads of the building. With advanced controls for economizers it is now possible
to eliminate the exception 6.5.1.3c which exempted zones 1, 2, 3a, 4a, 5a, 5b, 6, 7 and 8
from using integrated economizers.
Tables 6.5.3.1.1 A & B have eliminated fixed dry-bulb control in zones 1a,2a,3a,4a
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Economizers
Addendum cy
As part of this addendum
the table 6.3.2 which allows
for the elimination of
economizers thru the use of
higher efficiency HVAC
equipment was also
updated . The table has
been modified to reflect the
new ASHRAE benchmark
building models and to
expanded to allow it to be
used for any type of HVAC
system and not just Unitary
air cooled equipment
currently covered by the
table.
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Water-Water HP
Addendum bg
•
This proposal establishes for the first time a product class for water- to-water heat pumps.
The intent is to recognize the technology in Standard 90.1 by requiring minimum energy
efficiency standards. Cooling EERs and heating COPs are established for products with
cooling capacities below 135,000 Btu/h at standard rating conditions listed in ISO standard
13256-2.
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Kitchen Exhaust Hoods
Addendum ax
• This addendum replaces the existing the requirements for kitchen
exhaust hoods in 6.5.7.1.
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Supply Air Reset
Addendum bh
• This addendum adds a requirement for supply air
temperature reset at part load conditions. This can result in
significant energy savings. It does include exceptions for
humid applications
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Data Centers-Computer Room Units
Addendum bu
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This addendum adds efficiency requirements for computer room units.
There are several new requirements added as well as a new rating metric (SCOP),
test procedure, and efficiency table
Note: This is only part of the table
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Data Centers- Economizer Requirements
Addendum bu
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Data Centers- Essential Facilities
Addendum bu
This area will be refined
over time
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Single Zone VAV Fan Power
Addendum ca
This change closes a loophole in the fan power allowances for Variable Air
Volume (VAV) systems. A VAV system without terminal units (typically
serving a single zone) does not need this added fan power allowance and
should reasonably comply with the constant volume fan power
requirements.
• 6.5.3.1.1 Each HVAC system at fan system design conditions shall not
exceed the allowable fan system motor nameplate hp (Option 1) or fan
system bhp (Option 2) as shown in Table 6.5.3.1.1A. This includes supply
fans, return/relief fans, exhaust fans, and fan-powered terminal units
associated with systems providing heating or cooling capability. Single
zone variable-air-volume systems shall comply with the constant volume
fan power limitation.
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VAV Ventilation Optimization
Addendum ck
This addendum addresses demand control in multiple space VAV systems
and adds ASHRAE Standard 62.1-2007 as a reference
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6.5.3 Air System Design and Control. Each HVAC system having a total fan system motor nameplate hp
exceeding 5 hp shall meet the provisions of Sections 6.5.3.1 through.6.5.3.3.
6.5.3.3 Multiple-zone VAV System Ventilation Optimization Control
Multiple-zone VAV systems with DDC of individual zone boxes reporting to a central control panel shall
include means to automatically reduce outdoor air intake flow below design rates in response to changes
in system ventilation efficiency as defined by ASHRAE Standard 62.1, Appendix A and as determined in
part by the zone requiring the highest fraction of outdoor air in the zone discharge air stream, and in part
by variations in zone-level discharge airflow and outdoor air intake flow requirements.
Exceptions to 6.5.3.3
(a) Dual-path systems which recirculate plenum air locally, as defined by Standard 62.1. 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.
(b) Systems required to have Exhaust Air Energy Recovery complying with Section 6.5.6.1.
(c) Systems where total design exhaust airflow is more than 70% of total design outdoor air intake flow
requirements.
6.5.6.1 Exhaust Air Energy Recovery
Exceptions to 6.5.6.1
(h) Single-path multiple-zone VAV systems meeting the ventilation control requirements in 6.5.3.3.
Modify the following reference in Section 12
ANSI/ASHRAE Standard 62.1-2007 Ventilation for Acceptable Indoor Air Quality
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Unitary Efficiency
Addendum co
• This addendum makes three major amendments to Table
6.8.1A.
– it updates EER and IEER values for all condensing units and
water and evaporatively cooled air conditioners with
cooling capacities greater than 65,000 Btu/h.
– establishes a separate product class for evaporatively
cooled air conditioners with different energy efficiency
standards
– replaces the IPLV descriptor for condensing units with the
new IEER metric and amends the EER’s with more stringent
values
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New
Class
IEER & Higher EER
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Unitary Efficiencies-VRF
Addendum cp
This addendum addresses VRF
systems and sets efficiency
requirements and references
AHRI Standard 1230
•
Adds definition for VRF systems in
Section 3 as follows:
Variable Refrigerant Flow (VRF)
System. An engineered direct
expansion (DX) multi-split system
incorporating at least one variable
capacity compressor distributing
refrigerant through a piping network
to multiple indoor fan coil units each
capable of individual zone
temperature control, through
integral zone temperature control
devices and common
communications network. Variable
refrigerant flow utilizes three or more
steps of control on common, interconnecting piping.
1. This is not the complete table
2. IEER increases 7/1/2012
50
Duct Leakage
Addendum cq
This addendum:
• Addresses Duct Sealing and
Leakage and eliminates the B/C
classes of duct and Tables 6.4.4.2
A&B
• Adds a definition for ductwork and
seal class A
• Includes a reference for SMACNA
Duct Leakage Test Procedures 1985 HVAC Air Duct Leakage Test
Manual
– Sections 3, 5, and 6
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Garage Ventilation
Addendum di
This addendum relates to garage ventilation. In 2001 this type of requirement was removed from
the standard due to liability concerns. Sensors and controls have improved and again allow
inclusion of this energy savings in the 2010 standard.
Add new definition to section 3.2:
Ventilation system motor nameplate hp: the sum of the motor nameplate horsepower
(hp) of all fans that are required to operate as part of the system.
Modify Section 6 as follows:
6.4.3.4.6 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.
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Motor Efficiencies
Addendum aj
• This addendum adds new
efficiency requirements for
motors. They are actually
defined by DOE but have been
added it to section 8 for
clarification
• Note that DOE has
implemented changes to
increase the motor efficiencies
for integral HP motors to
premium levels.
• They go into effect on Dec 19
2010
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Motors
Addendum bk
•
This addendum adds 2 new definitions and clarifies some of the requirements and
exemptions to addendum aj which added the motor efficiencies
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Water Booster Systems
Addendum cv
This is an example of an energy savings idea submitted outside the committee by CMP
Service water (domestic water) booster pump systems can waste substantial energy in three ways:
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It is common to boost pressure beyond the pressure needed under most conditions and then
to reduce that pressure with one or more pressure reducing valves.
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Even relatively efficient systems incorporating variable speed drives may be controlled in ways
that require the pumps to run even when there is no service water flow.
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The pressure maintained may be more than needed during low flow conditions when there is
less piping pressure loss to account for.
10.4.2 Service Water Pressure Booster Systems. Service water pressure booster systems
shall be designed such that:
a. One or more pressure sensors shall be used to vary pump speed and/or start and stop
pumps. The sensor(s) shall either be located near the critical fixture(s) that determine the
pressure required, or logic shall be employed that adjusts the setpoint to simulate operation
of remote sensor(s).
b. No device(s) shall be installed for the purpose of reducing the pressure of all of the water
supplied by any booster system pump or booster system, except for safety devices.
c. No booster system pumps shall operate when there is no service water flow.
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Elevators
Addendum df
This is an example of an energy savings idea generated by a cross-functional WG with members from
at least 2 subcommittees and stakeholders outside the committee
ACEEE and the European E4 committee estimate elevator energy to be in the range of 2-5% of
building electric consumption. Elevators waste energy in several ways:
1. Ventilation fans often run 24/7 regardless of load or occupancy
2. Cab lighting often operates 24/7 regardless of occupancy
3. The energy consumption of the elevator moving apparatus varies over a range of around
5:1 between the least and most efficient units.
This addendum takes a first step in addressing the first two sources of inefficiency listed above.
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10.4.3 Elevators. Elevator systems shall comply with the requirements of this
section:
10.4.3.1 Lighting. All cab lighting systems shall have efficacy of not less than 35
lumens per Watt.
10.4.3.2 Ventilation Power Limitation. Cab ventilation fans for elevators without
air-conditioning shall not consume over 0.33 Watts per cfm at maximum speed.
10.4.3.3 Standby Mode. When stopped and unoccupied with doors closed for
over 15 minutes, cab interior lighting and ventilation shall be de-energized until
required for operation.
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Thank You