Optimized Chilled Water Plant Controls...
Transcript of Optimized Chilled Water Plant Controls...
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Optimizing Chilled Water Plant Design & Controls
Steven T. Taylor, PETaylor EngineeringAlameda, CA
November 12, 2013
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Agenda
Chilled Water Distribution System Selection
Determining Optimized Sequences Chilled Water Pump Control Chilled Water Temperature and DP
Setpoint Reset Tower Fan Speed Control Condenser Water Pump Control Chiller Staging Waterside Economizer Control
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Primary Resources Optimized Design & Control of Chilled Water
Plants, ASHRAE Journal• Part 1: Chilled Water Distribution System Selection• Part 2: Condenser Water Distribution System Design• Part 3: Pipe Sizing and Optimizing ∆T • Part 4: Chiller & Cooling Tower Selection• Part 5: Optimized Control Sequences
All are available at no charge from http://www.taylor-engineering.com/publications/articles.shtml
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Optimizing Energy Usage Chillers
• Type, efficiency, size, VSD Cooling Towers
• Fan type, efficiency, approach, range, speed control, flow turndown
Chilled Water Pumps• Arrangement, flow rate (delta-T), pressure drop, VSD
Condenser Water Pumps• Flow rate (delta-T), pressure drop
Air Handling Units• Coil sizing, air-side pressure drop, water-side pressure
drop
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RecommendedChilled Water Distribution Arrangement
Independent Variables Recommended SystemNumber of
Coils/Loads ServedNumber of
ChillersSize of Coils/Loads
ServedControl Valves
Distribution Type
One Any Any None Primary-only single coil
More than one One Small (< ~100 gpm)2-way and 3-way
Primary-only, single chiller
Few coils serving similar loads
More than one
Small (< ~100 gpm) 3-way Primary-only constant flow
Many coils serving similar loads or any serving dissimilar loads
More than one
Small (< ~100 gpm) 2-wayPrimary-Only or
Primary-Secondary
More than one Any Large Campus 2-way Primary−Distributed Secondary
More than one AnyLarge coils (> ~100
gpm)None Primary−Coil Secondary
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CHILLER
CHW PUMP
OPTIONAL STORAGE
TANK
COIL
SUPPLY AIR TEMPERATURE
SUPPLY WATER TEMPERATURE
Single Coil – Single Chiller
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CHILLER
CHW PUMP
COIL2-WAY VALVE
SUPPLY WATER TEMPERATURE
VFD
DP SENSOR
3-WAY VALVE
Primary-only - Single chiller
3-Way Valve• Sized for minimum flow of
chiller• Locate at end of system
• Engage mass• Retain self-balancing
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Primary-only Constant Flow
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Secondary Pump w/ VFD
at Chiller Plant
2-Way Control Valves at AHUs
Secondary Pump w/ VFD
at Chiller Plant
2-Way Control Valves at AHUs
Primary/Secondary
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Primary/Distributed Secondary
Central Plant
Distributed Secondary
Pump w/ VFD -Typical at each
Building
No Secondary Pumps at
Plant
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Distributed P/S versus Conventional P/S or P/S/T
Advantages• Reduced Pump HP - Each Pump Sized for Head
From Building to Plant• Self-balancing• No Over-pressurized Valves at Buildings Near Plant• Reduced Pump Energy, Particularly When One or
More Buildings Are off Line• No Expensive, Complex Bridge Connections Used
in P/S/T Systems• Similar or Lower First Costs
Disadvantages (vs. P/S)• Pump room needed at building • Higher expansion tank pre-charge and size
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Primary/Coil Secondary
Large AHU-1
Distributed Secondary
Pump w/ VFD -Typical at each AHU
No Secondary Pumps at Plant
Large AHU-2
No Control Valves at AHUs
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Hybrid systems
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Advantages of VFD Coil Pumps versus Conventional P/S system
Reduced Pump HP • Each pump sized for head from coil to plant• Eliminated 10 feet or so for control valves
Self-balancing• No need for or advantages to balancing valves, reverse return
Lower Pump Energy• No minimum DP setpoint• Pump efficiency constant
Better Control• Smoother flow control - no valve hysteresis• No valve over-pressurization problems
Usually Lower First Costs Due to Eliminated Control Valves, Reduced Pump and VFD HP
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Disadvantages of VFD Coil Pumps versus conventional P/S system
Cannot Tap into Distribution System without Pump• May be problem with small coils (low flow, high
head pump) Possible Reduced Redundancy/Reliability
unless Duplex Coil Pumps are Added Possible Low Load Temperature
Fluctuations• Minimum speed on pump motor• May need to cycle pump at very low loads
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Primary-only System
BYPASS VALVE
Headered Pumps & Auto Isolation Valves Preferred to Dedicated Pumps:• Allows slow staging• Allows 1 pump/2 chiller operation• Allows 2 pump/1 chiller operation if there is low ∆T
Flow Meter or DP Sensor Across Chiller
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Advantages of primary-only versus primary/secondary system
Lower First Costs Less Plant Space Required Reduced Pump HP
• Reduced pressure drop due to fewer pump connections, less piping
• Higher efficiency pumps (unless more expensive reduced speed pumps used on primary side)
Lower Pump Energy• Reduced connected HP• “Cube Law” savings due to VFD and variable flow
through both primary and secondary circuit
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Pump EnergyPrimary vs. Primary/Secondary (3-chiller plant)
0.00
5.00
10.00
15.00
20.00
25.00
30.00
35.00
40.00
10% 20% 30% 40% 50% 60% 70% 80% 90% 100%
% GPM
Pum
p kW
Primary-only
Primary-secondary
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Disadvantages of primary-only versus primary/secondary system
Failure of Bypass Control• Not as fail-safe - what if valve or controls fail?• Must avoid abrupt flow shut-off (e.g. valves interlocked with
AHUs all timed to stop at same time)• Must be well tuned to avoid chiller short-cycling
Flow Fluctuation when Staging Chillers On• Flow drops through operating chillers• Possible chiller trips, even evaporator freeze-up• Must first reduce demand on operating chillers and/or slowly
increase flow through starting chiller; causes temporary high CHWS temperatures
(Problems above are seldom an issue with very large plants, e.g. more than 3 chillers)
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Primary-only System Staging
1000 GPM
0 GPM
0 GPM
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Primary-only System Staging
500 GPM
500 GPM
0 GPM
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Variable FlowPrimary/Secondary with CHW Storage
Advantages• Peak shaving• Simplifies chiller staging• Provides back-up for chiller
failure• Secondary water source for fire
department• Secondary water source for
cooling towers Disadvantages
• Installed cost• Space
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Primary-only vs. Primary/Secondary
Use Primary-only Systems for:• Plants with many chillers (more than three) and with
fairly high base loads where the need for bypass is minimal or nil and flow fluctuations during staging are small due to the large number of chillers; and
• Plants where design engineers and future on-site operators understand the complexity of the controls and the need to maintain them.
Otherwise Use Primary-secondary• Also for plants with CHW storage
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Optimizing Control Sequences
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Generic Chilled Water Plant 1000 Tons total capacity Dual chillers/pumps/towers Variable speed drives on
everything (optional on CWPs)
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Optimum Sequences All plants are different
• Tower efficiency, approach• Chiller efficiency, unloading control• Pump efficiency, head, unloading control• Number of chillers, pumps, towers
Too many independent variables• CT fan speed• Chiller staging• CW pump speed
What is the optimum control sequence for a given plant?
Can sequences be generalized to apply to any plant based on plant design parameters?
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Equipment Models Chillers
• Hydeman et al, Regression Based Electric Chiller Model• Multi-point calibration using zero-tolerance manufacturer’s
data Towers
• DOE-2.2 model calibrated using manufacturer’s data Pumps
• Multiple piping sections ∆P=C*GPM1.8
• Pump efficiency from regression of manufacturer’s data VFD and motor efficiency
• Part load curves from manufacturer’s data
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Generic Plant Design Options
Plant• Office building • Peak Load = 900 ton• Two chillers each 500 ton• Two CW pumps & towers• Two CHW pumps• All variable speed
Climate: • 3C: Oakland• 4B: Albuquerque• 5C: Chicago
Chillers: • A: two stage R-123 hermetic• B: one stage R-134a open
drive
Tower Approach• -A: 3 ~ 5F• -B: 5 ~ 7F• -C: 7 ~ 10F• -D: 9 ~ 12F
Tower Range: • -1: 9F• -2: 12F• -3: 15F
Tower Efficiency • H: ~90 gpm/hp• M: ~70 gpm/hp• L: ~50 gpm/hp
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Theoretical Optimum Plant Performance (TOPP) Model
Run Time: ~5 hours/run * 216 runs = 1080 hours, not including analysis!
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TOPP Plant Energy: Oakland
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Determining Sequences
Plot TOPP results vs. various independent variables to see if there are trends
Once independent variables are selected, determine correlations
Test the sequence using the models to see how close they are to the TOPP
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Chilled Water Pumps
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Controlling CHW Pumps
Primary-only and Secondary CHW Pumps• Control speed by differential pressure
measured as far out in system as possible and/or reset setpoint by valve demand
• Stage pumps by differential pressure PID loop speed signal:Start lag pump at 90% speedStop lag pump at 40% speedFor large HP pumps, determine flow and speed
setpoints with detailed energy analysis
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VSD Pump Power vs. Setpoint
0%
10%
20%
30%
40%
50%
60%
70%
80%
90%
100%
0 10% 20% 30% 40% 50% 60% 70% 80% 90% 100%
Percent GPM
Perc
ent P
ump
kW
DP setpoint = Design HeadDP setpoint = Head*.75DP setpoint =Head/2DP setpoint =Head/3DP setpoint = 0 (reset)
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Chilled Water Setpoint Reset Reset Impacts
• Resetting CHWST upwards reduces chiller energy but will increase pump energy in VSD variable flow systems
• Dehumidification Reset with “open” or indirect control loops (e.g. OAT) can starve coils
and reduce dehumidification Reset by control valve position will never hurt dehumidification −
humidity of supply determined almost entirely by supply air temperature setpoint, not CHWST
Recommendations• Reset from control valve position using Trim & Respond logic• For variable flow systems with VSDs
Reset of CHWST and VSD differential pressure setpoint must be sequenced − not independent like VAV systems since control valves are pressure-dependent
Sequence reset of CHWST and DP − next slide…
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CHWST/DP Setpoint Reset for VSD CHW System
Back off on CHWST first Then back off on DP setpoint first Reverse this for constant speed chillers
Tmin+ 15ºF
Tmin
DPmax
5 psi
CHW setpoint
CHW setpoint
DP setpoint
DP setpoint
CHW Plant Reset 0 100% 50%
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CHW vs. DP Setpoint Reset
Plant with 150 ft CHW pump head, variable speed chillers
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CHW Pump Staging
Percent of Design Flow
Percent of Pump Speed
Opt
imum
Num
ber o
f P
umps
One Pump: CHWFR <47% Two Pumps: CHWFR >47% Time delays to prevent short-cycling
TOPP Model Results
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Cooling Towers
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Tower Isolation Options
1. Select tower weir dams & nozzles to allow one pump to serve all towers
• Always most efficient• Almost always least
expensive• Usually possible with 2 or 3
cells2. Install isolation valves
on supply lines only• Need to oversize equalizers
3. Install isolation valves on both supply & return
• Usually most expensive • Easiest to design• Valve sequencing issues and
possible failure
COOLINGTOWER #1
COOLINGTOWER #2
COOLINGTOWER #3
COOLINGTOWER #1
COOLINGTOWER #2
COOLINGTOWER #3
COOLINGTOWER #1
COOLINGTOWER #2
COOLINGTOWER #3
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Tower Fan Control
Free Cooling~ 15% of Capacity
Single SpeedFan
Two-Speed orVariable-SpeedFan
% Capacity
% Power
One Cell Tower
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Tower Fan Control
0%
10%
20%
30%
40%
50%
60%
70%
80%
90%
100%
0% 5% 10% 15% 20% 25% 30% 35% 40% 45% 50% 55% 60% 65% 70% 75% 80% 85% 90% 95% 100%
% Capacity
% P
ower
Two 1-Speed Fans
Two 2-Speed Fans
One 1-Speed Fan andOne 2-Speed Fan
Free Cooling Below 15% Capacity
Two Variable Speed
Two Cell Tower
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Tower Efficiency LCC
90 GPM/HP 70 GPM/HP 50 GPM/HP
1000 ton Oakland Office
ASHRAE Efficiency:
The flow rate the tower can cool from 95F to 85F at 75F wetbulb temperature divided by fan power (GPM/HP)
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Tower ApproachOakland Office Oakland Data Center
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Optimum Approach Temperature
0
5
10
15
20
25
30
0 1000 2000 3000 4000 5000 6000 7000 8000 9000 10000
Tower App
roach + Ra
nge
Cooling Degree‐Days ‐ base 50F
OaklandChicago
Albuquerque
Miami
AtlantaLas Vegas
50CWA CDDTT 001.027
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Tower Efficiency Guidelines
Use Propeller Fans • Avoid centrifugal except where high static needed• Consider low-noise propeller blade option and high
efficiency tower where low sound power is required Efficiency
• Minimum 80 gpm/hp for commercial occupancies• Minimum 100 gpm/hp for 24/7 plants (data centers)
Approach• Commercial occupancies: See previous slide
8°F to 9°F for Bay Area
• 24/7 plants (data centers): 3°F
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47
Reset by Wetbulb Temperature?
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“Lift” (CWRT-CHWST) vs. %Load
Lift Reset Best Fit for Offices
Wetbulb reset best for data centers since load does not vary
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Tower Control LIFT = A*PlantLoadRatio + B
• Bounded by minimum LIFT at minimum PLR (from manufacturer) and maximum LIFT (design lift)
• CWRT setpoint = LIFT + CHWST• Control CT fans to maintain CWRT
A and B coefficients • Best optimized by modeling• Rough estimate:
LIFTd= design lift = CWRTdesign – CHWSTdesign LIFTm= Minimum lift at minimum loadA = (LIFTd – LIFTm)/0.7B = LIFTd - A
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Condenser Water Pump
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CW pump Control
Constant speed CW pumps• Stage along with chillers
Variable speed CW pumps?
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%CW Loop Flow vs. %Plant Load
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53
VSD CWP Control Logic
Pump speed control• CWFR = C*PLR + D • CWFSP = CWFR*CWDF• Control speed to maintain CW flow at setpoint
Staging• Same logic as CHW pumps
Disadvantages• Requires flow meter• C and D coefficients only optimized by simulation
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CWLoopFlowRatio = C*PlantLoadRatio + D
C = ‐0.0000811 * CDD55 + ‐0.01293 * WB + 3.486 * NPLV + ‐0.02476 * APPROACH + 0.07400 * RANGE D = ‐0.797 + 2.282 * IPLV + 0.002196 * APPROACH + ‐0.00795 * RANGE
Coefficient C Coefficient D
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Even Optimum Savings are Small
OaklandMiami AtlantaLas
Vegas Albuquerque Chicago
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Answer: VFDs on CWPs are Not Cost Effective for Office Buildings
Life
Cyc
le C
osts
, $
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Energy Use May Increase!Performance in Miami using C and D optimized for Oakland
Oakland
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58
Miami
Oakland :Miami:
y = 0.9069x + 0.0388
0%
10%
20%
30%
40%
50%
60%
70%
80%
90%
100%
0% 10% 20% 30% 40% 50% 60% 70% 80% 90% 100%
CW gpm
% Total Plant Design Capacity
CW gpm vs % Load
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59
Recommendations
For offices etc., use constant speed pumps
For data centers and other 24/7 plants• Use VFDs• Determine C and D coefficients through
modelingOther logic may increase energy usage
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Chiller Staging
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Staging Fixed Speed Chillers
Fixed Speed Chillers• Operate no more chillers than required to meet
the load • Stage on when operating chillers maxed out as
indicated by measured load (GPM, T), CHWST, flow, or other load indicator.
• For primary-secondary systems w/o check valve in the common, start chiller to ensure Primary-flow > Secondary-flow
• Stage off when measured load/flow indicates load is less than operating capacity less one chiller – be conservative to prevent short cycling
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62
Staging Variable Speed Chillers
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Part Load Chiller Performancew/ Zero ARI Tolerance
0%
10%
20%
30%
40%
50%
60%
70%
80%
90%
100%
0% 10% 20% 30% 40% 50% 60% 70% 80% 90% 100%
% Load (with Condenser Relief)
%kW
Fixed SpeedVariable Speed
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64
Two-Chiller Plant Performance at Low Load
0%
10%
20%
30%
40%
50%
60%
0% 10% 20% 30% 40% 50%
% Plant Load
%P
lant
kW
(in
clud
ing
PC
HW
& C
W p
umps
)
Variable Speed - one ch illerFixed Speed - one chillerVariable Speed - two chille rsFixed Speed - two chille rs
Running two VFD chillers is more efficient until 35% load
Running two fixed speed chillers always uses more energy
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Cautionary Note
Staging logic must limit possibility for surge operation for centrifugal chillers
Some variable speed chillers don’t dynamically measure surge conditions• You will lose some of the savings with primary-
only variable flow systems because minimum speed may have to be increased to avoid surge
• You may have premature tripping due to onset of surge otherwise
• This is only an issue with variable evaporator flow systems (like primary-only variable flow)
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Surge Region
Ref
riger
ant H
ead
Load
100% speed90%
80%
70%
60%
Ref
riger
ant L
ift
Load
Staging & Surge
One ChillerTwo Chillers
One ChillerTwo Chillers
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Correlation with Lift & Load
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Generic Control Sequences All-variable speed plant
FTTESPLR CHWSCWR )(
Stage Chillers on
Nominal Capacity Stage up to next stage if either: Stage down to
lower stage if:
0 All off 0 −
Any Chiller Plant Requests and
OAT>LOT and schedule is active
−
2 Lead chiller 50%
for 15 minutes load greater than
SPLR
CHW Plant Reset = 100 for 15
minutes, and load greater than 30%
No Chiller Plant Requests for 5
minutes or OAT<(LOT-5F)
or schedule is inactive
3 Both chillers 100% − −
for 15 minutes load less than
SPLR
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Determining E and F
TE Correlations• E = 0.057 - 0.000569*WB - 0.0645*IPLV -
0.000233*APPROACH - 0.000402*RANGE + 0.0399*KW/TON
• F = -1.06 + 0.0145*WB + 2.16*IPLV + 0.0068*APPROACH + 0.0117*RANGE -1.33*KW/TON
Need to test for reasonablenessDefault values
• E=0.004 and F = 0.30
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Example
Oakland office building All variable speed plantTOPP model coefficients
• A = 47, B =5.2• C = 1.3, D = 0.13• E = 0.009, F = 0.21
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TOPP vs. Real Sequences
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Waterside Economizers
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PLATE & FRAMEHEAT EXCHANGER
CHILLER #1
CHILLER #2
COOLINGTOWER #2
COOLINGTOWER#1
Non-Integrated
Economizer
65F
Twb 34F
44F
47F
47F
44F
Hours in SF Bay Area with Twb <= 34F??
10 hrs/yr
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PLATE & FRAMEHEAT EXCHANGER
CHILLER #1
CHILLER #2
EITHER PUMPOR VALVE
(NOT BOTH)
COOLINGTOWER #2
COOLINGTOWER#1
MODULATINGVALVE Integrated
Economizer Primary/Secondary
65F
Twb 52F
59F
47F
62F
59F
Hours in SF Bay Area with Twb <= 52F??
4000 hrs/yr
9%
47F41%
0%
50%load
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COOLINGTOWER #2
COOLINGTOWER#1
PLATE & FRAMEHEAT EXCHANGER
CHILLER #1
CHILLER #2
BYPASSWSE-ONLY
MODULATINGVALVE
Integrated Economizer Primary Only
65F
Twb 52F
59F
47F
62F
59F
15%
47F38%
38%
90%load
75%load
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Integrated WSE Control Sequences
Run all air handlers, including redundant units with variable speed drives
Reset CHWST setpoint based on valve demand Enable WSE if CHWRT > predicted HXLWT + 2
• Predicted HXLWT = Ambient wetbulb + HX_Approach + Tower_Approach HX_Approach = Design HX approach * %HX-Load Tower_Approach = Design Tower approach for office type occupancies
= Adjust based on WBT from manufacturer’s data for data center– see slide 5
Disable WSE if HXLWT > CHWRT - 2 Disable chiller(s) when HXLWT ≤ CHWST setpoint Enable chiller(s) when CHWST > setpoint Run as many tower cells as minimum flow will allow Tower speed:
• When WSE is disabled control speed “normally”• When WSE and chiller(s) are enabled run 95% speed• When chiller is disabled control speed to maintain CHWST setpoint76
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Summary
In this seminar, you have learned how to• Select optimum chilled water distribution system• Optimally controlChilled Water PumpsChilled Water Temperature and DP Setpoint ResetTower FansCondenser Water PumpsChiller StagingWaterside Economizers
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Questions