Final Presentation Witterman-Jason
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Transcript of Final Presentation Witterman-Jason
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McCarran Internat ional A irport
Term inal 3
as egas,
Evaluation of Underfloor Air Distribution The Pennsylvania State University
,
Jason A. WittermanMechanical Option
Facult Advisor:William Bahnfleth, PhD, P.E.
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L a s V e g a s , N V
ut ne• Building Background and Existing Mechanical Conditions
•
Mechanical Redesign• Access Floor Design Breadth
• Acoustical Breadth
•
onc us ons
J a s o n A . W i t t e r m a n | 2
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L a s V e g a s , N V
Term na 3 ac groun
Location
,
Owner
Department of Aviation
Size
1.8 Million SF
Construction
April 2007 – Mid 2012
J a s o n A . W i t t e r m a n | 3
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L a s V e g a s , N V
Ex st ng Mec an ca
on t ons
Waterside
5 2 200 ton centrifu al chillers Variable primary flow
(6) 21,000 MBH water tube boilers
Airside (88) air handling units
15,000 ‐55,000 CFM
J a s o n A . W i t t e r m a n | 4
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L a s V e g a s , N V
ut ne• Building Background and Existing Mechanical Conditions
• Mechanical Redesign▫ Introduction
▫ Goals and applications
▫ Revised load calculations
▫ New SA quantities and temperatures
▫ System equipment
▫ Initia cost impacts
▫ Annual energy consumption and cost
• Access Floor Design Breadth
• Acoustical Breadth
• Conclusions
J a s o n A . W i t t e r m a n | 5
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L a s V e g a s , N V
Mec an ca
e es gn Intro uct on
Focus on level 2 airside
14 ate holdrooms and ad acent concourse Area ≈ 170,250 SF
Ceiling slopes from 12’‐6” above finished floor to 30’‐6”
Level 2 Key Plan
J a s o n A . W i t t e r m a n | 6
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L a s V e g a s , N V
Interior Rendering
Interior Rendering of Redesigned Area (Courtesy PGAL, LLC)
J a s o n A . W i t t e r m a n | 7
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L a s V e g a s , N V
Mec an ca
e es gn Intro uct on
Existing system is a traditional overhead mixing type
VAV s stem served b 11 air handlin units Linear ceiling diffusers in holdrooms
Sidewall jet nozzle diffusers in airside concourse
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L a s V e g a s , N V
e es gn
oa s
Create a comfortable indoor environment
Thermal comfort Indoor air quality
Minimize energy consumption
Reduce annual operating costs
J a s o n A . W i t t e r m a n | 9
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L a s V e g a s , N V
ystem App cat ons
Potential Benefits of UFAD and DV Systems
Better ventilation effectiveness Reduced SA quantities
Increased economizer operation
UFAD reserved for holdrooms Conceal floor diffusers
DV used in airside concourse
Low sidewall diffusers
J a s o n A . W i t t e r m a n | 10
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L a s V e g a s , N V
ev se
Loa
a cu at ons
Must separate occupied and unoccupied zone loads:
Occu ied zone extends 6‐8 feet above the floor Loads must be conditioned through SA to the space
Unoccupied zone is above the occupied zone
Stratification eliminates need for SA to this zone Coil must still handle both load types
There are many different opinions on the percentage of load
transferred to each zone.
J a s o n A . W i t t e r m a n | 11
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L a s V e g a s , N V
ev se
Loa
a cu at ons
The UFAD load factors used for the redesign are based on
various ASHRAE publications.
Occupied Zone Load Factors Minimum Maximum
Occupants 0.65 0.75 0.75
Component of Load According to Various Research
Factor Used for Design
. . .
Equipment 0.67 0.70 0.67
Envelope Conduction 0.70 0.82 0.77
Envelope Solar 0.70 1.00 1.00
J a s o n A . W i t t e r m a n | 12
l l
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L a s V e g a s , N V
ev se
Loa
a cu at ons
The DV load factors used for the redesign are based on the
ASHRAE Design Guide.
Occupied Zone Load Factors Minimum Maximum
Occupants 0.295 0.670 0.295
Component of Load According to Various Research
Factor Used for Design
. . .
Equipment 0.295 0.500 0.295
Envelope Conduction 0.185 0.820 0.185
Envelope Solar 0.185 1.000 0.185
J a s o n A . W i t t e r m a n | 13
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t T e r m i n a l 3
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L a s V e g a s , N V
Vent at on Mo cat ons
Minimum outdoor air flow rates calculated in accordance with
ASHRAE Standard 62.1‐2007. Breathing zone outdoor air flow rate (VBZ) remains unchanged
Zone air distribution effectiveness (E ) varies
EZ = 1.0 for existing systems EZ = 1.2 for redesigned systems
onsequen y, zone ou oor a r ow OZ var es
V &&
Z
OZ E
=
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L a s V e g a s , N V
Vent at on Mo cat ons
Increased ventilation effectiveness and re‐zoning allows for 40%
reduction in zone outdoor air flows at louver.
Vot, Outdoor Air Intake Flow Required [CFM]
Exisitng Overhead Systems 129,760
Redesigned UFAD and DV Systems 77,083
,
J a s o n A . W i t t e r m a n | 16
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L a s V e g a s , N V
A
uant t es an
Temperatures
UFA
Higher UFAD SA temperatures are required to maintain thermal
comfort in the s ace. Minimum advisable SA temperature is 64 °F
Air temperature increases 4‐7 °F directly above floor outlets
ASHRAE Standard 55 Maximum 5 °F gradient between ankle and head
Calculations assume SA temperature of 65 °F for UFAD systems
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t T e r m i n a l 3
L a s V e g a s , N V
A
uant t es an
Temperatures
UFA
Supply air quantities calculated using occupied zone loads only:
( ) ( )][int
,][
08.1V
UFADCool,F SASetpo
neOccupiedZoTotalCFM
T T °−×=&
Return air temperatures based on total space load:
( ) ( )][
][][
08.1T
CFM SA
otaF SAF RA
V T
&×+= °°
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t T e r m i n a l 3
L a s V e g a s , N V
A
uant t es an
Temperatures
V
Higher SA temperatures are also required for DV systems,
thou h the must actuall be calculated. Air supplied slightly above the floor
Occupants more sensitive to temperature from lower
velocities
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p
L a s V e g a s , N V
A
uant t es an
Temperatures
V
Supply air quantities calculated using occupied zone loads only:
( ) ( )][
,][
08.1V
UFADCool,F hf
neOccupiedZoTotalCFM
T °Δ×=&
Supply and return air temperatures based on total space load:] / [][ HR BTU TotalSF Q A ×
−− °°°
/ HR BTU
( ) ( ) ( ) ( ) ( )][][
2
][
int
08.133.2 CFM SASF CFM SA
hf SetpoSA
V AV && ××+×
( ) ( )][
][][
08.1T
CFM SA
o aF SAF RA
V T
&×+= °°
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p
L a s V e g a s , N V
A
uant t es an
Temperatures
Higher SA flow rates are required for both system types.
Lower ΔT for redesigned systems Not enough reduction in occupied zone loads
Existing Supply Air Redesigned Supply Difference Flow Rate [CFM] Air Flow Rate [CFM] [CFM]
Underfloor Air
Distribution 160,650 253,182 92,532
Displacement Ventilation 130,335 162,497 32,162
, , ,
Average SA temperatures: ≈ 65 °F for both UFAD and DVAverage RA temperatures: ≈ 80 °F for UFAD and ≈85 °F for DV
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L a s V e g a s , N V
A r Han ng
Equ pment
Nine additional air handling units are required to provide the
increased su l air uantities. Separate units to serve various system types
7 for UFAD, 8 for DV, 5 for overhead mixing
Additional space found above egress stairs
Location of Egress Stairs
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L a s V e g a s , N V
A r Han ng
Equ pment
Elevated mechanical space
within e ress stair towers 45’‐6” x 29’‐0”
8 units serving airside
concourse Up to 25,000 CFM each
Louvers located at low roof
to maintain architecture
Section Through Egress Stairs
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L a s V e g a s , N V
UFA
Equ pmentPerimeter diffusers
Linear floor grilles provide cooling
or ea ng
Used in Sterile Circulation and
Interior diffusers Linear Floor Grilles
Distributor baskets for debris
Underfloor terminal units
VAV terminal units for all diffusersRound Floor Diffuser and Basket
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L a s V e g a s , N V
V Equ pment
Displacement diffusers
Sidewall rectan ular diffusers Coverage area 20’‐0” x 20’‐0”
Traditional terminal units
VAV terminal unitsDuct covers when necessary
Architectural integration Displacement Diffuser and Cover
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L V N V
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L a s V e g a s , N V
In t a
ost Impacts
Air handling units
Cost data is obtained from actual design estimate
System Type Total Cost
Existing System Air Handling Units $2,023,580.00
Capacity [CFM]
460,000
Redesigned UFAD and DV Air Handling Units $2,740,000.00
$716,420.00
Total Cost Difference per SF 170,251 SF $4.21
560,000
Total Cost Difference
UFAD and
DV
equipment
os a a s o a ne rom manu ac urer s u ge pr c ng
J a s o n A . W i t t e r m a n | 26
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L a s V e g a s N V
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L a s V e g a s , N V
In t a
ost Impacts
Total initial cost difference
= $716,420.00
= $104,369.36
Air handling units
UFAD components
= , .
≈ $1,051,287.00
components
Total
Total existing mechanical system cost ≈ $80.6 million
Reasonable increase given total project cost
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L a s V e g a s N V
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L a s V e g a s , N V
Annua
Energy an
ost
Impacts
Economizer savings
Hi her su l and return air tem eratures allow for increased economizer operation
Increase of 5 ‐ 10°F in OA temperature range
Bin analysis allows for estimate of energy savings
J a s o n A . W i t t e r m a n | 28
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L a s V e g a s N V
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L a s V e g a s , N V
Annua
Energy an
ost
Impacts
Economizer savings
UFAD s stems 2,735,358,255 BTU/yr
39,385.4 BTU/SF‐yr
DV systems 2,998,765,000 BTU/yr
29,650.4 BTU SF‐yr
Potential for large savings in annual energy consumption
J a s o n A . W i t t e r m a n | 29
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L a s V e g a s N V
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L a s V e g a s , N V
Annua
Energy an
ost
Impacts
Trane TRACE is used to simulate the existing and redesigned
s stems takin into account: Economizer operation
Outdoor air flow rates
Supply air flow rates Other factors
Zoning
Fan static etc.
J a s o n A . W i t t e r m a n | 30
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L a s V e g a s , N V
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L a s V e g a s , N V
Annua
Energy an
ost
Impacts
Annual operating costs
Annual Cost erUtility
Annual Cost [$/yr]
Square Foot [$/(SF*yr)]
Existing System
Electricity $627,893 $3.69
Natural Gas $5,227 $0.03
Existing System Annual Cost $633,120 $3.72
Electricity $778,054 $4.57
Natural Gas 13 707 0.08
Redesigned System
Redesigned System Annual Cost $791,761 $4.65
Total Difference Between Systems $158,641 $0.93
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g ,
Annua
Energy an
ost
Impacts
TRACE actually indicates an increase in energy consumption:
Increase of 0.93 er SF‐ r in area of focus Increase of $0.09 per SF‐yr for the total building area
Again, reasonable increases given building size
J a s o n A . W i t t e r m a n | 32
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g ,
ut ne• Building Background and Existing Mechanical Conditions
• Mechanical Redesign
• Access Floor Design Breadth
• Acoustical Breadth
• onc us ons
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L a s V e g a s , N V
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Access
F oor
rea t
Required for implementation of UFAD system
Plenum height of 1’‐0” to 1’‐6” Maintain carpet finish
Line Number Item Description Quantity Unit Total Cost
09 69 13.10 Access Floors
0250 Panels, particle
board
or
steel,
1250#
load,
no
covering; Over 6,000 SF69,451 SF $316,696.56
0600 For car et coverin add 69 451 SF 576 443.30
0910 For snap on strigner system, add 69,451 SF $139,596.51
1050 Pedestals 17,365 Each $257,870.25
‐‐Minus
Existing
Carpet 69,451 SF
‐$296,555.77
, .
$983,116.29
$14.16
Tota
Adjusted For Location (0.989)
Total Per Square Foot
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Access
F oor
rea t
Cost
≈ 1 million
Architectural impacts
Transition to concourse
Two slab elevations required Jet bridges and baggage handling dictate elevation
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L a s V e g a s , N V
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ut ne• Building Background and Existing Mechanical Conditions
• Mechanical Redesign
• Access Floor Design Breadth
• Acoustical Breadth
• onc us ons
J a s o n A . W i t t e r m a n | 36
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L a s V e g a s , N V
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Acoust ca
rea t
Existing conditions
Sound attenuators for su l and return ductwork Duct lagging
Ambient noise
Highly occupied, transient space Jet noise from exterior
Fan noise likely minimal
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
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Acoust ca
rea t
Noise criteria (NC)
Lar e ublic s aces circulation NC‐45
Trane Acoustics Program (TAP)
Used to model duct layouts Fans, ductwork, fittings, terminal units, diffusers, etc.
Critical fan only
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Acoust ca
rea t
esu s
Supply: NC‐33 Return: NC‐31
NC Graphs for AH‐5R Supply and Return FansJ a s o n A . W i t t e r m a n | 39
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Acoust ca
rea t
Results
Redesi n within tar et NC Eliminate existing attenuation
Savings of at least $50,000 in initial cost
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M c C a r r a n I n t e r n a t i o n a l A i r p o r t – T e r m i n a l 3
L a s V e g a s , N V
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F na onc us ons
Initial cost
Mechanical e ui ment 1 051 285≈ Addition of access floor
Sound attenuation
$983,115
‐$50,000
≈
≈
Total increase in costAnnual cost
$1,984,400≈
Approximately $158,640 per year
Both are significant, though within reason
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F na onc us ons
Benefits
mprove roug s ra ca on
Increased economizer operation
Disadvantages
Additional equipment
Com lexities with access floor
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F na onc us ons
As designed, UFAD and DV are likely not appropriate for these
s aces in Terminal 3.
Supply air quantities must be minimized
Reduced fan energy → Lower annual cost Reduced equipment → Lower initial cost
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F na onc us ons
Strategies to reduce SA quantities
Use sensible coolin anels Reduce solar load transmission
Better applications Less densely occupied areas
Interior zones
Less critical areas
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uest ons
Interior Rendering of Redesigned Area (Courtesy PGAL, LLC)
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