high performance-chilled-water-systems ashrae-chicago
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High-Performance Chilled Water Systems - IllinoiTRANSCRIPT
© 2011 Ingersoll Rand
High Performance Chilled Water Systems
High Performance Chilled Water Systems
Mick Schwedler, PE, LEED® APManager Applications EngineeringTrane
Normal Performance Chilled Water Systems ASHRAE/IESNA 90.1 (LEED Prerequisite)
System configuration
Design parameters
System control
ASHRAE Standard 90.1-2007 Purpose
“… Provide minimum requirements for the energy-efficient design of buildings except low-rise residential buildings”
Purpose ofANSI/ASHRAE/IESNA Standard 90.1-2010
To establish minimum energy efficiency requirements of buildings, other than low-rise residential buildings for:
1. design, construction, and a plan for operation and maintenance, and
2. Utilization of on-site renewable energy resources.
Publication and Final Savings Estimates Performed by Pacific Northwest National
Laboratory (PNNL) Savings of 90.1-2010 compared to
90.1-2004
Savings shared are modeled as of January 2011
Include ventilation changes in ASHRAE 62.1 between 1999 and 2007 versions
90.1 Progress Indicator Including receptacle loads in modeling
Including receptacle load in % savings calculation
24.0
Energy cost savings %
25.5Ventilation rate changes
between 62.1-1999 and 62.1-2007
Energy savings %
90.1 Progress IndicatorExcluding receptacle loads in % savings calculation only
Including receptacle loads in modeling
Excluding receptacle load in % savings calculation
30.1
Energy cost savings %
32.6Ventilation rate changes
between 62.1-1999 and 62.1-2007
Energy savings %
LEED Energy and Atmosphere LEED 200910% energy cost savings beyond 90.1-2007
LEED 2012Public Review 2: September 2011 EA Prerequisite: 10% average energy cost and source
energy savings beyond 90.1-2010 (new construction) EA Credit: Credit for reductions beyond 10%
90.1-2010Chiller EfficienciesPaths A & B
Equipment Type Size CategoryUnits
Before 1/1/2010 As of 1/1/2010c Test Procedureb
Path A Path Bd
Full Load IPLV
Full Load IPLV
Full Load IPLV ARI 550/590
Air-cooled<150 tons EER ≥9.562 ≥10.416 ≥9.562 ≥12.50 NA NA
≥150 tons EER ≥9.562 ≥10.416 ≥9.562 ≥12.75 NA NA
Water Cooled Electrically Operated, Positive Displacement
<75 tons kW/ton≤0.790 ≤0.676
≤0.780 ≤0.630 ≤0.800 ≤0.600
≥75 tons and < 150 tons kW/ton ≤0.775 ≤0.615 ≤0.790 ≤0.586
≥150 tons and < 300 tons kW/ton ≤0.717 ≤0.627 ≤0.680 ≤0.580 ≤0.718 ≤0.540
≥300 tons kW/ton ≤0.639 ≤0.571 ≤0.620 ≤0.540 ≤0.639 ≤0.490
Water Cooled Electrically Operated,
Centrifugal
<150 tons kW/ton ≤0.703 ≤0.669≤0.634 ≤0.596 ≤0.639 ≤0.450≥150 tons and
< 300 tons kW/ton ≤0.634 ≤0.596
≥300 tons and < 600 tons kW/ton
≤0.576 ≤0.549≤0.576 ≤0.549 ≤0.600 ≤0.400
≥600 tons kW/ton ≤0.570 ≤0.539 ≤0.590 ≤0.400
Must meet both full and part load requirements
Heat rejection equipment Fan speed control 7.5 and
greaterCapability to operate at 2/3
fan speed or less
ExceptionsClimates > 7200 CDD50
(e.g. Miami)
1/3 of fans on multiple fan application
Hydronic system design and control Pump isolation
Chilled and hot water reset if >300,000 BtuhException: Variable flow systems that
reduce pumping energy
90.1-2007Hydronic System Design & ControlThese provisions apply if pump system power > 10 hp:
Must be variable flow unless … Pump power ≤ 75 hp ≤ 3 Control valves
Limit demand of individual variable-flow pumps to 30% of design wattage at 50% flow (e.g., use VSD) Pump head > 100 ft Motor > 50 hp
WatersideEnergy Recovery required Service Water Heating24 hrs per day and
Heat rejection > 6 MMBtuh and
SWH load 1 MMBtuh
Recover smaller of60% of heat rejection
Preheat water to 85°F
ConfigurationNormal Performance Chilled Water
productionpumps
two-way valve
distributionpump
distributionloop
productionloop
Design ParametersNormal Performance Chilled Water Plant ARI 550/590 Standard Conditions44°F chilled water
2.4 gpm/ton chilled water (10°F T)
3.0 gpm/ton condenser water (10°F [9.3] T)
ControlNormal Performance Chilled Water Plant Chilled water distribution pump
P at most remote load
Cooling tower fans55°F (as cold as possible)
Constant speed condenser water pumps
All these “normal” assumptions will be examined
High PerformanceChilled Water Plants Standard high performance
Reduced flow rates, increased ∆Ts
Variable primary flow
Advanced high performance Equipment capabilities
System configurations
System control
a history ofChiller Performance
8.0
ASHRAE Standard 90
chill
er e
ffic
ien
cy,
CO
P
6.0
4.0
2.0
0.0NBI “best”
available90-75(1977)
90-75(1980)
90.1-89 90.1-99
centrifugal>600 tons
screw150-300 tons
scroll<100 tons
reciprocating<150 tons
chilled water plant design …ProvocationAre our “rules of thumb” …
44 F chilled water supply
10 F T for chilled water system
3 gpm/ton condenser water flow
… in need of repair?
High Performance Design Parameters ASHRAE GreenGuide and CoolTools™
Chilled water T: 12°F to 20 °F
Condenser water T: 12°F to 18 °F (multi-stage)
Kelly and Chan Chilled water T: 18°F
Condenser water T: 14.2°F(3.6 - 8.3% energy savings in various climates)
chilled water plant …humid climateBase Design: 450 Tons 0.5% design
wet bulb: 78 F
Entering condenser water temperature (ECWT): 85 F
Evaporator and condenser temperature differences: 10 F
Coil, valve and chilled water piping pressure drop: 80 ft
Condenser water piping pressure drop: 30 ft
Pump efficiency: 75%
Pump motorefficiency: 93%
traditional design …humid climateSystem Energy Consumption
2.4/3.0
Chilled /Condenser Water Flows, gpm/ton
Ener
gy C
onsu
mpt
ion,
kW
TowerCondenser Water PumpChilled Water PumpChiller (100% Load)
0
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150
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250
300
350
traditional vs. low-flow design …System Summary At Full Load
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350
2.4/3.0 1.5/2.0
Chilled /Condenser Water Flows, gpm/ton
Ener
gy C
onsu
mpt
ion,
kW
TowerCondenser Water PumpChilled Water PumpChiller (100% Load)
comparison …humid climateSystem Summary At 75% Load
0
50
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250
300
350
2.4/3.0 1.5/2.0
Chilled /Condenser Water Flows, gpm/ton
Ener
gy C
onsu
mpt
ion,
kW
TowerCondenser Water PumpChilled Water PumpChiller (75% Load)
comparison …humid climateSystem Summary At 50% Load
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350
2.4/3.0 1.5/2.0
Chilled /Condenser Water Flows, gpm/ton
Ener
gy C
onsu
mpt
ion,
kW
TowerCondenser Water PumpChilled Water PumpChiller (50% Load)
comparison …humid climate System Summary At 25% Load
0
50
100
150
200
250
300
350
2.4/3.0 1.5/2.0
Chilled /Condenser Water Flows, gpm/ton
Ener
gy C
onsu
mpt
ion,
kW
TowerCondenser Water PumpChilled Water PumpChiller (25% Load)
traditional vs. low-flow design …humid climateSavings Summary
0
10.0
20.0
25% 50% 75% 100%
Load
Ope
ratin
g C
ost S
avin
gs, %
3.8%
6.7%
10.3%
16.5%
High PerformanceDesign Parameters
0
200
400
600
41/16 42/14 43/12 44/10
Chilled water supply temperature/DeltaT
kWh/
ton/
year
Chilled waterpumpChiller
Pipe Size Example90.1-2010 Table 6.5.4.5
Past DesignPractice
ASHRAE GreenGuide
∆T (°F)
Flow(gpm)
Pipe Size
∆T (°F)
Flow(gpm)
Pipe Size
Chilled Water
10 1920 10 16 1200 8
Condenser Water
9.4 2400 14 14 1600 12
800 ton system
3,000 hours of operation
Chilled water, variable flow
Condenser water, constant flow
High PerformanceDesign OptionsEither …
Take full energy (operating cost) savings
Or …
Reduce piping size and costExperienced designers use pump,piping and tower savings to select aneven more efficient chiller
Reduced flow works for all chiller manufacturers Logan Airport - Boston:
$426,000 Construction cost savings
7.3% operating cost savings
Large Chemical Manufacturer -Greenville $45,000 Excavation and concrete savings
6.5% Operating cost savings
Computer Manufacturer - San Francisco Existing tower, pipe savings
2% Operating cost savings (tower not changed)
Low flow works for retrofit applications Chilled water side
Coil It’s a simple heat transfer device Reacts to colder entering water
by returning it warmer
Ideal for system expansion
Low flow works for retrofit applications
Condenser side retrofit opportunity Chiller needs to be
replaced
Cooling needs haveincreased by 50%
Cooling tower wasreplaced two years ago
Condenser pump and pipes are in good shape
Condenser side retrofit opportunity
Existing Retrofit
Capacity (tons) 500 750
Flow rate (gpm) 1500 1500
Condenser Entering WaterTemperature (F)
85 88
Condenser Leaving WaterTemperature (F)
95 103
Design Wet Bulb (F) 78 78
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100.0
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300.0
350.0
25% 50% 75% 100%
System Load
Ener
gy C
onsu
mpt
ion
(kW
h)
3.0 gpm/ton2.0 gpm/ton
Humid climatesLow flow works for short piping runs too
Condenser Water Side Only - original
0.0
50.0
100.0
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350.0
25% 50% 75% 100%
System Load
Ener
gy C
onsu
mpt
ion
(kW
h)
3.0 gpm/ton2.0 gpm/ton
Humid climatesLow flow works for short piping runs too
Condenser Water Side OnlyZERO piping pressure drop
High Performance Design Parameters Low flow benefits systems - no
matter whose chiller is being used
Low flow works extremely well on existing systems
Low flow works on short piping runs
always, always,Always Remember …
Oh, by the way...
You may also do this with air
Variable-Primary-Flow Systems
variable-flowpumps
controlvalve
checkvalves
VPF Savings First cost: 4-8%
Annual energy: 3-8%
Life-cycle cost: 3-5%
http://www.arti-21cr.org/ARI/util/showdoc.aspx?doc=1085
Flow requirementsVPF System Limits (consult manufacturer)
Absolute flows - Minimum and maximum
Flow rate changes 2% of design flow per minute
not good enough 10% of design flow per minute borderline 30% of design flow per minute
many comfort cooling applications 50% of design flow per minute
best
Always need a way to ensure minimum flow (bypass)
Chiller ControlVariable W ater Flow
30
40
50
60
70
80
90
100
110
120
130
3:50:00 3:55:00 4:00:00 4:05:00 4:10:00Tim e (hour:m in:sec)
Wat
er T
emp
[deg
F]
-500
-300
-100
100
300
500
700
900
1100
1300
1500
Flow
[gpm
]Evaporator W ater F low
Evap Entering W ater Tem p
Evap Leaving W ater Tem p
More informationVPF System Http:/trane.com/commercial
/library/newsletters.asp (1999 and 2002)
“Primary-Only vs. Primary-Secondary Variable Flow Systems,” Taylor, ASHRAE Journal, February 2002
“Don’t Ignore Variable Flow,” Waltz, Contracting Business, July 1997
“Comparative Analysis of Variable and Constant Primary-Flow Chilled-Water-Plant Performance,” Bahnfleth and Peyer, HPAC Engineering, April 2001
“Campus Cooling: Retrofitting Systems,” Kreutzmann, HPAC Engineering, July 2002
High Performance Chilled Water Plants Standard high performance
Reduced flow rates, increased ∆Ts
Variable primary flow
Advanced Equipment capabilities
System configurations
System control
Equipment CapabilitiesHigh Performance Chilled Water Plant Constant speed0.570 FL / 0.479 IPLV
Higher efficiency “same price” optionsVariable speed (spend money on drive)
Constant speed (spend money on copper)
Purchase both a drive and more heat exchange surface
Down to 0.45 kW/ton FL available (22% reduction)
Same-price Chiller: Example Performance
Option Full Load(kW/ton)
IPLV(kW/ton)
VSD 0.572 0.357High Efficiency 0.501 0.430
Same-price Chiller: Example Performance
0
50
100
150
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300
350
400
0% 20% 40% 60% 80% 100%
kW
% Load
600-ton Replacement Chiller Performance
High_efficiency_85°FVSD_85°FHigh_efficiency_75°FVSD_75°FHigh_efficiency_65°FVSD_65°F
Example Office building
Two 400-ton chillers
Comparisons Base system - constant speed
AFD on both chillers
High efficiency for both chillers
AFD on one chiller
High efficiency for one chiller
What is the actual utility rate? Utility costs ‘Combined’ utility rates ($0.10 / kWh)
Actual utility rates ($12 / kW and $0.06 / kWh)
Utility rate comparison
Simple paybacks, humid climate
Combined rate Actual rate
AFD 6.1 10.8on one chiller High efficiency 6.3 7.7
AFD 7.2 12.7on both chillers High efficiency 7.1 8.3
Using incorrect “combined” rate leads to incorrect decisions
Rule 1
Use actual utility rates
Temperate climatewith economizer
Annual operating cost
$20,000
$40,000
$60,000
$80,000
$100,000
Base case AFD on both chillers
High efficiency both chillers
AFD on one chiller
High efficiencyone chiller
0
5
10
15
20
25
30
Simple payback
Chiller plant operating costSimple payback
Temperate climate,no economizer
Annual operating cost
$20,000
$40,000
$60,000
$80,000
$100,000
Base case AFD on both chillers
High efficiency both chillers
AFD on one chiller
High efficiencyone chiller
0
2
4
6
8
10
12
Simple payback
Chiller plant operating costSimple payback
Humid climate,no economizer
Annual operating cost
$20,000
$40,000
$60,000
$80,000
$100,000
Base case AFD on both chillers
High efficiency both chillers
AFD on one chiller
High efficiencyone chiller
2
4
6
8
10
12
14
Simple payback
Chiller plant operating costSimple payback
Dry climate with economizer
Annual operating cost
$20,000
$40,000
$60,000
$80,000
$100,000
Base case AFD on both chillers
High efficiency both chillers
AFD on one chiller
High efficiencyone chiller
Simple payback
Chiller plant operating costSimple payback
024681012141618
Rule 2
Model ROI of each investment
Guidance: VSD or High Efficiency? High efficiency
Significant demand charges, especially ratchet charges
Climates where the wet bulb doesn’t vary substantially
Multiple chillers in the plant
Economizer that reduces low load/low lift operating hours
VSD Many hours at low
condenser water temperature – and low load
Perhaps only on one chiller
Factor replacement cost of VSD when performing life cycle assessment
High Performance Chilled Water Plants Standard high performance
Reduced flow rates, increased ∆Ts
Variable primary flow
Advanced Equipment capabilities
System configurations
System control
VPF System Minimum flow and bypass control
Single chiller
Retrofit
P
Controller
P
What may not be a good VPF application? Two packaged chillers
Limited evaporator configurations
Assume minimum flow is about 1.2 gpm/ton
In parallel
Wide ∆T (low flow) e.g 18°F ∆T is 1.33 gpm/ton
Why isn’t it a good application? Flow can only be turned down 10%
Variable-Volume Pumping System(series chillers)
57°F41°F
48.4°F
Bypass alternatives
Upstream chiller operating at higher temperature is more efficient
Series ChillersManual service bypass
Series Chiller Advantages Simplifies pumping and
sequencing No flow rate transitions
Makes VPF simple
Upstream chiller operates at elevated temperature Efficiency increases
Capacity increases 10% or more for
absorption
Simple preferential loading of chillers Adjust upstream
chiller’s setpoint Upward to unload Downward to load
High PerformanceChilled Water Plants Standard high performance
Reduced flow rates, increased ∆Ts
Variable primary flow
Advanced Equipment capabilities
System configurations
System control
ControlNormal Performance Chilled Water Plant Chilled water distribution pump
P at most remote sensor
Cooling tower fans55°F (as cold as possible)
Somewhere else
Constant volume condenser water pumps
High PerformanceChilled Water Pump Control
Valve position Pump Pressure Sensor
Communicating BAS Pump Speed
Position (% open)of critical valve
75%
65%
Increase pump static pressure setpoint
Reduce pump static pressure setpoint
No action
pump-pressure optimizationControl Logic 90.1-2007 Addendum ak
High Performance Chiller-Tower Control
Plant Power vs CWS
0.0
200.0
400.0
600.0
800.0
1,000.0
1,200.0
60 62 64 66 68 70 72 74 76 78 80 82 84 86 88
Condenser Water Setpoint (°F)
Pow
er (k
W)
Lowest condenser water temperature available from tower at this load and wet-bulb temperature
Chillers cannot meet load above this condenser water temperature
Optimal operation
1,550 tons, 65°F Wet-bulb T t
1,160 tons, 59°F Wet-bulb T
730 tons, 54°F Wet-bulb Temperature
Hydeman, et. al. Pacific Gas and Electric. Used with permission.
Cooling tower basicsFan energy consumption
0
20
40
60
80
100
0 20 40 60 80 100% Airflow
% Full load power
ambient wet bulb, °F
0.0
4.0
8.0
12.0
16.0
50 60 70 80
tow
er a
pp
roac
h,
deg
100% load
50% load
approach = 4
approach = 9
cooling tower performance factorsApproach and Wet Bulb
simple case: constant water flowOperating Dependencies
Wet bulb Condenser water
temperature Load Tower design
Load Condenser water
temperature Chiller design
condenser water control“Normal” Setpoint
Hot?e.g., 85°F, minimizes towerenergy consumption
Cold?e.g., 55°F, minimizes chillerenergy consumption
Optimized?
optimal condenser water controlChiller–Tower Interaction
condenser water temperature, °F
400
74
ener
gy
con
sum
pti
on,
kW
76 78 80 8272
300
200
100
084
tower
chiller
total
optimalcontrol point
High Performance Chiller-Tower Control Braun, Diderrich
Hydeman, Gillespie, Kammerud
Schwedler,ASHRAE Journal
Cascia
Crowther and Furlong
chiller–tower optimizationAn Example …
720,000 ft² hotel
2 chillers, 2 tower cells
Control strategies Make leaving-tower water cold
as possible (55F)
Optimize system operation
Entering-condenser setpoint equals design …85°F for humid climates80°F for dry climates
chiller–tower control strategiesNorth America
350K
ann
ual
op
erat
ing
cos
t, $
US
D
300K
250K
200K
150K
100K
50K
0Mexico City Orlando San Diego Toronto
55°F lvg toweroptimal controldesign ECWT
control strategy:
ann
ual
op
erat
ing
cos
t, $
US
D
500K
400K
300K
200K
100K
0Dubai Paris Sao Paulo Singapore
55°F lvg toweroptimal controldesign ECWT
control strategy:
chiller–tower control strategiesGlobal Locations
chiller–tower optimizationOperating Cost Savings
oper
atin
g c
ost
savi
ng
s, %
14
0
12
10
8
6
4
2
location
Du
bai
Du
bai
Par
isP
aris
Sao
Pau
loS
ao P
aulo
Sin
gap
ore
Sin
gap
ore
Mex
ico
Cit
yM
exic
o C
ity
Orl
and
oO
rlan
do
San
Die
go
San
Die
go
Toro
nto
Toro
nto
chiller–tower optimizationPerspective on SavingsFor centrifugal chillers ≥ 300 tons, ASHRAE 90.1 requires …
0.576 kW/ton at full load
0.549 kW/ton at IPLV
… using ARI standard rating conditions
chiller–tower optimizationPerspective on Savings
EquivalentSavings, % chiller efficiency
0.0 0.576
2.8 0.560
4.5 0.550
6.2 0.540
14.0 0.495
Where’s the Meter?On theBUILDING
chiller–tower optimizationFinding “Near Optimal” Tower design
(flow rate, range, approach)
Chiller design Refrigeration cycle
(vapor compression vs. absorption)
Compressor type
Capacity control (variable-speed drive)
Changing conditions(chiller load, ambient wet bulb)
chiller–tower optimizationNecessities
System-level controls
Variable-frequency driveon tower fans
High-quality dewpoint sensor
Number of chillers operating Operate one at nearly full load or two at
part load?
Examine IPLV assumptions
VSDs and centrifugal chillersA Closer Look at IPLV
VSDs improve part-lift performance, so running two chillers with VSDs at part load seems more efficient than one chiller at double the same load, but …is dependent on condenser water temperature
Load ECWTWeighting kW/Ton
100% 0.01 85°F 0.572
75% 0.42 75°F 0.420
50% 0.45 65°F 0.308
25% 0.12 65°F 0.372
Chiller power only45% Plant load
0
50
100
150
200
250
300
350
55 60 65 70 75 80 85
Available Tower Water Temperature (ºF)
Chi
ller k
W
1@90% Load2@45% Load
Operate 1 or 2 Chillers?Chiller kW Only
Chillers plus pumps45% Plant load
0
50
100
150
200
250
300
350
400
55 60 65 70 75 80 85Available Tower Water Temperature (ºF)
Chi
ller P
lus
Pum
p kW
1@90% Load2@45% Load
Operate 1 or 2 Chillers?Chiller Plus Pump kW
Operate 1 or 2 chillers?Run 1 or 2 VSD Chillers?
0
50
100
150
200
250
300
350
400
60 65 70 75 80 85Available Tower Water Temperature (ºF)
Tota
l Chi
ller P
lus
Pum
p kW
1@90% Load2@45% Load1@80% Load2@40% Load1@70% Load2@35% Load1@60% Load2@30% Load1@50% Load2@25% Load
Operate multiple chillers here,otherwise single chiller
Operate 1 or 2 chillers? 45% plant load: One chiller until tower
temperature is < 65°F
40% plant load: One chiller until tower temperature is < 60°F
35% plant load and below: One chiller
High PerformanceCondenser Water Pump Control – Variable? Pump speed limits Tower static lift
Tower nozzles (minimum flow)
Condenser minimum flow
Pump speed reductions result in Increased leaving condenser water
temperature
Decreased cooling tower effectiveness
Possible chiller surge
High PerformanceCondenser Water Pump Control – Variable? The condenser water pump is the hardest
place to properly utilize a variable frequency drive during operation
There are successful installations
variable-flow condenser waterPump Speed Determining minimum speed
Variable flow affects:Pump
Cooling tower
Chiller
condenser water pumpMinimum SpeedDeterminants:
Minimum condenser flow Tower static lift Minimum tower flowNozzle selection
Performance
reducing flow & fan speedEffect on System
100
syst
em p
ower
, kW
50
150
200
250
300
condenser water flow, %50 60 70 80 90 100
0
conditions:• 70% load• 50°F WB
fan speed
Varying fan and pump speed together
variable condenser water flowGuidance Can provide savings …Finding proper operating
points requires more time,more fine-tuning
Two-step process:1 Reduce design pump power
2 Is variable condenser-waterflow still warranted?
ROIHigh Performance Chilled Water Plants
EnergyPlus
Non-bin
Schematic tools that analyze in 30-45 minutes are available
High PerformanceChilled Water Plants Standard high performance
Reduced flow rates, increased ∆Ts
Variable primary flow
Advanced high performance Equipment capabilities
System configurations
System control
High performance chilled water plantWinchester Medical Center
Medical CenterWinchester, Virginia Five 750-ton chillers
0.571 kW/ton full load
Chilled water 58 to 42°F
Condenser water84 to 95°F(missed opportunity)
VFD’s
Variable primary flow
VFD’s on Chilled water pumps
Cooling tower fans
Condenser water pumps
Sophisticated control system with lots of Programming
Commissioning
Winchester Medical Center Working togetherOwner
Operators
Consulting engineer
Equipment provider
Controls provider
Service provider
Applications engineering
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s)0.00
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cien
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W/to
n)
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WMC - August 12Chiller plant
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03 10:3
0
8/8/20
03 9:30
8/8/20
03 8:30
8/8/20
03 7:30
8/8/20
03 6:30
8/8/20
03 5:30
8/8/20
03 4:30
8/8/20
03 3:30
8/8/20
03 2:30
8/8/20
03 1:30
8/8/20
03 0:30
8/7/20
03 23:3
0
8/7/20
03 22:3
0
8/7/20
03 21:3
0
8/7/20
03 20:3
0
8/7/20
03 19:3
0
8/7/20
03 18:3
0
8/7/20
03 17:3
0
8/7/20
03 16:3
0
8/7/20
03 15:3
0
Time/Date
Load
(ton
s)
0.00
0.10
0.20
0.30
0.40
0.50
0.60
0.70
0.80
Effic
ienc
y (k
W/to
n)
tonskW/ton
WMC - Sept 1-7Chiller plant Weekly-Summary
0.0
200.0
400.0
600.0
800.0
1000.0
1200.0
1400.0
1600.01/
0/19
00 0
:00
1/0/
1900
0:0
01/
0/19
00 0
:00
1/0/
1900
0:0
01/
0/19
00 0
:00
9/1/
2003
14:
009/
1/20
03 1
9:30
9/2/
2003
1:0
09/
2/20
03 6
:30
9/2/
2003
12:
009/
2/20
03 1
7:30
9/2/
2003
23:
009/
3/20
03 4
:30
9/3/
2003
10:
009/
3/20
03 1
5:30
9/3/
2003
21:
009/
4/20
03 2
:30
9/4/
2003
8:0
09/
4/20
03 1
3:30
9/4/
2003
19:
009/
5/20
03 0
:30
9/5/
2003
6:0
09/
5/20
03 1
1:30
9/5/
2003
17:
009/
5/20
03 2
2:30
9/6/
2003
4:0
09/
6/20
03 9
:30
9/6/
2003
15:
009/
6/20
03 2
0:30
9/7/
2003
2:0
09/
7/20
03 7
:30
Time
Tons
0.00
0.10
0.20
0.30
0.40
0.50
0.60
0.70
0.80
kW/to
n
tonskW/ton
Winchester Medical Center - Mark Baker
“Please use our data, names, etc. We're proud of our facility!”
“By the way, we're now operating @ -0.20 kW/ton. The power company just sent us our 1st check. Ha..Ha…”
Remember...
Without controls,it’s not a system.Without controls,it’s not a system.
The meter is on the building!
It’s a great time to be in this business!