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Optimal Control of Chiller Condenser Sub-cooling, Compressor Speed, Tower Fan and Pump Speeds, and IGV
Omer Qureshi, Hassan Javed & Peter Armstrong, June 2013
btrc.masdar.ac.ae
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Presentation Outline
Introduction SCADA and Heat Balance Analysis Component Models Chiller System Solver Optimization Conclusion and Future Work
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Introduction
Plant under consideration-(4x2500T).
Collection and analysis SCADA
Development of sub models for Individual chiller components
Validation of model
Development of solver- to execute these sub models and predict
chiller performance.
Optimize the model to produce set of conditions for optimum
power consumption.
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District Cooling Plant
Selected District cool Plant
Capacity (4x2500T)
Shell and tube Evaporator and Condenser
Constant speed single stage centrifugal compressor
Capacity control by Pre-rotation vanes
Surge control Variable geometry diffuser
2-cell cooling tower each with variable speed fan (Fan diameter: 8m)
Variable speed chilled water pump
Constant speed condenser water pump
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Chiller Unit
1. Maintenance manual of York Chiller(Source: Tabreed)
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SCADA & Heat Balance Analysis
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Components ModelsโChiller Unit
Steady-state models based on first principleInputs
Component engineering parametersSCADA Data
Simple models, less computation timeFour Component models for district cooling plant
Evaporator Model----Shell and tubeCondenser Model----Shell and tubeCentrifugal Compressor Model (Isentropic work + loss Mechanism) โข Constant speedโข Variable speed
Variable speed pump model
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Evaporator Model
ENGINEERING PARAMETERS
Tubes Copper
Length of shell 6.6 m
Tube Pass (water) 2
Total no. of tubes 1234
Tube Diameter 0.75" or 1.905x10-2 m
Tube thickness 0.028" or 7.11x10-4 m
Assumptions:
No pressure drop considered for refrigerant side
Thermal resistance from refrigerant side is neglected.
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Evaporator Model
Evaporation Evaporation Superheating
Evaporator
Two regions for refrigerant were modeled:EvaporationSuperheating๐ฎ โ NTU MethodSingle Stream HX for evaporationCrossflow HX for super heating
1st Pass 2nd Pass
๐๐ค ,๐๐ข๐ก ,1 ๐๐ค ,๐๐ข๐ก ,2๐ ๐๐ค ,๐๐ข๐ก ,2๐
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Evaporator Model
Equations utilized in Evaporator Model
h ๐๐ ,๐=0.023๐ ๐๐0.8๐๐
0.4 ๐๐ค
๐ท๐ ,๐
๐๐ด๐=1
1๐ด๐๐ ,๐h๐๐ ,๐
+๐ ๐ ,๐
๏ฟฝฬ๏ฟฝ๐๐๐ยฟmin [๐๐ ,๐ค๏ฟฝฬ๏ฟฝ๐ค ,๐ยฟ ,๐ถ๐ , ๐ ๏ฟฝฬ๏ฟฝ๐ ]ยฟ
๐ด๐๐ ,๐ ,1=๐ ๐ท๐ ,๐๐ฟ๐(๐ยฟยฟ๐ /2)ยฟ๐ด๐๐ ,๐ ,1๐=๐ ๐ท๐ ,๐ ๐ฅ๐๐ฟ๐(๐๐ /2)๐ด๐๐ ,๐ ,1๐=๐ ๐ท๐ , ๐ยฟ
๐๐ค ,๐๐ข๐ก ,๐=๐๐ค ,๐๐ ,๐โ๐๐ก ,๐
๐๐ ,๐ค๐๐ค
Evaporation Evaporation Superheating
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Evaporator Model
Equations utilized in Evaporator Model
๐๐ค ,๐๐ข๐ก ,2๐=๐๐ค ,๐๐ข๐ก ,1โ(๐๐ค ,๐๐ข๐ก ,1โ๐ ๐) (1โ๐โ๐๐๐๐ ,2 ๐ )
๐2๐=1โ๐๐ฅ๐ [( 1๐ถ๐ ) (๐๐๐๐2๐)0.22{exp [โ๐ถ๐ (๐๐๐๐ ,2๐)0.78 ]โ1}]๐๐ค ,๐๐ข๐ก ,2๐=๐๐ค ,๐๐ข๐ก , 2๐โ๐2๐(๐๐ค ,๐๐ข๐ก , 2๐โ๐๐)
๐๐ค ,๐๐ข๐ก ,1=๐๐ค ,๐๐ ,๐โ(๐๐ค ,๐๐ ,๐โ๐๐) (1โ๐โ ๐๐๐๐1 )
๐ฟ๐=8.947 ๐ฅ 10โ3๏ฟฝฬ๏ฟฝ๐
2โ3.6279๐ฅ 10โ1๏ฟฝฬ๏ฟฝ๐โ+7.227
Equation for regressed length:
Equation for temperatures:
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Evaporator Model
1. Maintenance manual of York Chiller(Source: Tabreed)
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Evaporator Model
1.5 2 2.5 3 3.5 41.5
2
2.5
3
3.5
4
Measured Te (C)
Mod
eled
T
e (C
)
Measured Te (C) vs Modeled Te (C)
Measured Te (C)15% error line
-15% error line
RMS 0.2096 C
NRMS 0.0319
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Condenser Model
ENGINEERING PARAMETERS
Tubes CopperLength of shell 6.6 mTube Pass (water) 2Total no. of tubes 937Sub-cooling Section:Tube Diameter 0.75" or 1.905x10-2 mNo. of tubes 180Tube thickness 0.028" or 7.11x10-4 mTube Surface Area 66.78 m2 Condensation & de-superheating Section:Tube Diameter 1" or 2.54x10-2 mNo. of tubes 757Tube thickness 0.035" or 8.89x10-4 mTube Surface Area 376.44 m2
Assumptions:
No pressure drop considered for refrigerant side
Thermal resistance from refrigerant side is neglected.
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Condensation
Sub-cooling
Conden-sation
De-superheating
Condenser
Condenser Model
Three regions for refrigerant were modeled:
Sub-cooling
Condensation
De-Superheating๐ฎ โ NTU Method
1st Pass 2nd Pass
๐๐ค ,๐๐๐ฅ ,๐๐๐ค ,๐๐ข๐ก ,2๐ ๐๐ค ,๐๐ข๐ก ,2๐
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Equations utilized in Condenser Model
1a. Sub-Cooling Section(First Pass):
Condenser Model
h ๐๐ ,๐ , 1๐=0.023๐ ๐๐ 10.8๐๐โ
0.4 ๐๐ค
๐ท๐ 1 ,๐
๐๐ด๐ , 1๐=1
1๐ด๐๐ , ๐, 1๐h ๐๐ ,๐ , 1๐
+๐ ๐ , ๐ ,1๐
๐๐ ,1๐=1โ๐โ๐๐๐๐ ,1๐ (1โ๐ถ๐ ,1 ๐ )
1โ๐ถ๐ , 1๐๐โ๐๐๐๐ ,1 ๐(1โ๐ถ๐ ,1 ๐)
๐ ๐๐ =๐ ๐ 2โ๐๐, 1๐๐ถ๐๐๐ ,1๐(๐ ๐ถ 2โ๐๐ค ,๐๐ , ๐)
๏ฟฝฬ๏ฟฝ๐ ๐๐ ,๐
๐๐ค ,๐๐ข๐ก ,1๐=๐๐ค , ๐๐ ,๐+๏ฟฝฬ๏ฟฝ๐ ๐๐ ,๐ (๐ ๐ถ 2โ๐ ๐๐ถ)๏ฟฝฬ๏ฟฝ๐ค ,๐๐ฅ1 ,๐๐๐ ,๐ค
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1b. Condensation Section (First Pass):
Mixing Section:
Condenser Model
h ๐๐ ,๐ , 1๐=0.023๐ ๐๐ 1๐0.8๐๐โ
0.4 ๐๐ค๐ท๐ 2 , ๐
๐๐ด๐ , 1๐=1
1๐ด๐๐ , ๐ ,1๐h๐๐ ,๐ ,1๐
+๐ ๐ , ๐ ,1๐
๐๐๐ ๐ ,1๐=๐๐ด๐ ,1๐
๏ฟฝฬ๏ฟฝ๐๐๐,๐ค
๐๐ค ,๐๐ข๐ก ,1๐=๐๐ค ,๐๐ ,๐+๐ฅ๐๐๏ฟฝฬ๏ฟฝ๐ (๐ป๐ถ2โ๐ป๐ถ 3)
๏ฟฝฬ๏ฟฝ๐ค ,๐(1โ๐ฅยฟยฟ1๐)๐๐ ,๐ค ยฟ
๐๐ค ,๐๐๐ฅ ,๐=๏ฟฝฬ๏ฟฝ๐ค ,๐๐ฅ1 ,๐๐๐ค ,๐๐ข๐ก1 ,๐โ๏ฟฝฬ๏ฟฝ๐ค ,๐
(1โ๐ฅยฟยฟ1๐)๐๐ค ,๐๐ข๐ก 1๐
๏ฟฝฬ๏ฟฝ๐ค ,๐
ยฟ
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2a. Condensation Section (Second Pass):
2b. De-superheating Section (Second Pass):
Condenser Model
h ๐๐ ,๐ , 2๐=0.023๐ ๐๐ 2๐0.8๐๐โ
0.4 ๐๐ค
๐ท๐ 2 ,๐
๐๐ด๐ , 2๐=1
1๐ด๐๐ , ๐ ,2๐h๐๐ , ๐ ,2๐
+๐ ๐ ,๐ , 2๐๐๐๐ ๐ ,2๐=
๐๐ด๐ , 2๐
๏ฟฝฬ๏ฟฝ๐๐๐,๐ค
๐๐ค ,๐๐ข๐ก ,2๐=๐๐ค ,๐๐๐ฅ ,๐+๐ฅ๐๐๏ฟฝฬ๏ฟฝ๐๐๐ ,๐ (๐ป๐ถ 2โ๐ป๐ถ 3)
๏ฟฝฬ๏ฟฝ๐ค ,๐๐๐ ,๐ค
๐๐ค ,๐๐ข๐ก ,2๐=๐๐ค ,๐๐ข๐ก 2๐+๏ฟฝฬ๏ฟฝ๐๐๐ , ๐ , 2๐(๐ ๐ถ1โ๐ ๐ถ 2)
๏ฟฝฬ๏ฟฝ๐ค ,๐๐๐ ,๐ค
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Condenser Model
22 24 26 28 30 32 3422
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26
28
30
32
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Measured Tc (C)
Modele
d
Tc (
C)
Measured Tc (C) vs Modeled Tc (C)
Measured Tc (C)2.5% error line
-2.5% error line
RMS 0.0949 C
NRMS 0.0225
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Condenser Model
20 25 30 3520
25
30
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Measured Tw.out (C)
Mod
eled
T
w,o
ut (
C)
Measured Tw,out (C) vs Modeled Tw,out (C)
Measured Tw,out (C)5% error line
-5% error line
RMS 0.6481 C
NRMS 0.1471
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Compressor Model
Integral and mathematically most complex part of chillerConstant and variable speed compressor modelNon-Dimensional loss model based on Aungier(2000)
Assumptions
โข Gear efficiency is taken as 90%
โข Velocity profile is assumed as constant, along the hub and tip
โข The kinetic energy of refrigerant entering the diffuser is completely converted to useful energy
โข Diffuser and IGV losses are not modeled
โข Water flow rate for motor cooling is taken as constant
โข Complex engineering parameters in impeller geometry
Centrifugal Compressor Specification
Refrigerant R134A
Rating (Btuh) 2500
Rating (kW input) 1817
Rating discharge pressure (psig) 162
Rating suction pressure psig) 34
Rating suction temperature (F) 33/34
Impeller diameter (outlet diameter) m 0.7
Impeller hub diameter (inlet diameter) 0.3
Impeller Blade Angle (degree) 45/50
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Constant Speed Model
Variable speed Model
Compressor Model-Inputs and Outputs
Input Output
Mass flow rate of refrigerantInlet and outlet pressure of compressorInlet and outlet blade and velocity angles of impeller Impeller Inlet and outlet engineering parameters and dimensionsGear efficiency
Compressor Power Compressor RPMPressure at impeller exitTemperature at compressor outletPressure drop due to Impeller losses
Input Output
IGV PositionsConstant RPMInlet and outlet pressure of compressorInlet and outlet blade and velocity angles of impeller Impeller Inlet and outlet engineering parameters and dimensionsGear efficiency
Compressor Power Pressure at impeller exitTemperature at compressor outletPressure drop due to Impeller losses
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Validation Constant Speed Compressor Model
0 200 400 600 800 1000 1200 14000
200
400
600
800
1000
1200
1400
1600
No. of Observations
Cop
mre
ssor
Pow
er (
KW
)
Actual Power(kW)Model Power(kW)Loss Power(kW)Model Comp Power(kW)
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Validation Constant Speed Compressor Model
400 600 800 1000 1200 1400 1600400
600
800
1000
1200
1400
1600
Measured Power(kW)
Mod
el P
ower
(kW
)
Measured Power(kW) vs Model Power(kW)
Measured Power(kW)10% Error line
-10% Error lineRMS 108.34 KW
NRMS 0.1553
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Variable Speed Compressor Model
๐ผ๐ ๐๐๐ก๐๐๐๐๐ ๐๐๐๐ = ๐ค๐๐ ๐๐ = โ 1 ๐1๐1 เตฌ๐3๐1เตฐ
โ1เต๏ฟฝโ 1 ๐๐๐๐๐เต
๐๐๐ ๐ ๐น๐๐๐ค ๐๐๐ก๐ ๐๐ ๐๐๐๐๐๐๐๐๐๐๐ก= ๐แถ= ๐2๐ด2๐2๐2
RPM is calculated in an iterative process by satisfying the following equation
๐๐๐ ๐ข๐๐ก = ๐แถ๐ ๐๐๐๐ โ ๐แถ๐๐๐
Total Work
๐๐๐๐ก = ๐๐๐๐๐ + ๐๐๐๐ ๐
๐๐๐๐ ๐ = โ๐๐ก๐๐๐
Total Relative Pressure Drop (Due to Losses)
โ๐๐ก๐ = ๐๐(๐๐ก๐1 โ ๐๐ 1) เดฅ๐๐
Loss Model Calculations
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Variable Speed Compressor Model-Benefits/comparison
Variable Speed Compressor (KW)Measured Compressor Power (KW)
Com
pres
sor P
ower
(KW
)
No. of Observations
Operation Conditions:1. mr (kg/s)2. Pout/Pin
Power (KW) 1504.702IGV Position 44.2
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Impeller Loss Model
๐ผ๐๐๐๐๐๐๐๐ ๐ฟ๐๐ ๐ = 1โ ๐๐1๐1 sinแบ๐1แปเตจ2 + ๐ก๐1๐2๐๐1 sinแบ๐1แปเตจ
2
๐ท๐๐๐๐ข๐ ๐๐๐ ๐๐๐ ๐ = 0.81โ ๐1๐โ๐1 เตจ2 โ ๐ผ๐๐๐๐๐๐๐๐ ๐ฟ๐๐ ๐
๐๐๐๐ ๐น๐๐๐๐ก๐๐๐ ๐ฟ๐๐ ๐ = 4๐๐แ๐เดฅ๐1แ2 ๐ฟ๐ต๐ท๐ป
๐ต๐๐๐๐ ๐ฟ๐๐๐๐๐๐ ๐ฟ๐๐ ๐ = (โ๐ ๐1)ฮค 224
๐ธ๐ฅ๐๐๐๐ ๐๐๐ ๐ฟ๐๐ ๐ = แแบ โ 1แป๐๐2๐1 2
๐ถ๐๐๐๐๐๐๐๐ ๐บ๐๐ ๐ฟ๐๐ ๐ = 2๐แถ๐ถ๐ฟโ๐๐ถ๐ฟ๐ แถ1๐12
๐ป๐ข๐โ ๐โ๐๐๐ข๐ ๐ฟ๐๐ ๐ = (เดค๐๐เดค๐เดฅ ๐1)ฮค 26
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Variable Speed Compressor Model-losses profile
20 25 30 35 40 45 500
20
40
60
80
100
120
Refrigerant Mass Flow (kg/s)
Pre
ssu
re D
rop
(kP
a)
Clearance gap loss (kPa)Diffusion loss (kPa)Hub-shroud Loss (kPa)Incident loss (kPa)Skin friction loss (kPa)Blade Loading Loss (kPa)Expansion Loss (kPa)
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Effectiveness NTU Method
Cooling Tower Model
๐ป๐๐๐ก ๐ ๐๐๐๐๐ก๐๐= ๐๐๐๐๐๐๐ก๐๐ = ๐๐คแถโ๐๐๐ค โแบ๐๐๐ค๐ โ ๐๐๐ค๐แป ๐ถ๐๐๐๐๐๐ ๐๐๐ค๐๐ ๐ ๐๐ก๐ข๐๐ ๐๐๐๐๐๐๐๐ก๐ข๐๐= ๐๐๐ค๐ โ ๐๐๐๐๐๐๐ก๐๐๐๐คแถโ๐๐๐ค
๐๐๐๐๐๐๐ก๐๐ = โ๐ถแถ๐๐๐ โแบ๐๐๐ค๐ โ ๐๐ค๐แป = 1โ ๐โ๐๐๐(1โ)1โ ๐โ๐๐๐(1โ)
๐๐๐= ๐_๐คแถ๐_๐แถ ๐๐๐
๐๐๐= ๐พ โ๐โ๐๐_๐คแถ
๐๐๐ ๐ ๐น๐๐๐ค ๐๐ ๐ด๐๐= ๐_๐แถ = ๐๐๐๐ฅแถ โ๐๐ โ๐
Regression Coefficient
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Assumptions, Specifications and Input/ Output Variables
Cooling Tower Model
Assumptions
โข Air exiting the tower is saturated with water
vapor and is only characterized by its
enthalpy
โข Reduction of water flow rate by evaporation is
neglected in the energy balance.
โข Mass flow rate is calculated by considering
linear proportionality of mass flow rate of air
and motor speed.
Inputs Outputs
โข Wet-bulb temperatureโข Cooling tower supply water temperatureโข Dry-bulb temperature โข Mass flow rate of waterโข Cooling tower fan/motor speed
โข Cooling tower return water temperatureโข Merkelโs Number
Cooling Tower Specifications
Rating (RT) 5000
Rating flow rate (GPM) 15300
Rating ambient wet bulb (F) 86
Rating ambient dry bulb (F) 122
Rating entering condenser water
temperature (F)
105
Fan diameter and speed (m, RPM) 8/152.6
Air flow rate (CFM) 776383
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Cooling Tower Model
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Pump Model
Mainly there are two mode of operation for these pumps:
Constant flow pump
Variable flow pump with a variable speed drive
To model a variable pump power following relationship is used:
Where,PMP = pump motor power at rated condition, kWC1, C2, C3 and C4 are pump performance coefficients
Also,PLRi = pump part load ratio defined as follows:
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Pump Model
Validation Graph
+ 5%Error Line
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Solver Description
Qt,e
Tw,in,e
Tw,in,c
Ve
Vc
dTsh,e
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Optimization
Optimization performed with two configurations:
Chiller Water Flow Optimization
Chiller Water Flow And Condenser Water Flow Optimization
Objective Function:
Minimize total power consumption i.e. compressor power and pump(s)
power combined.
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Optimization
Chiller Water Flow Optimization:
Vc Vc Vc VcQe 10000 KW Qe 8000 KW Qe 6000 KW Qe 4000 KW
Power Total (KW)
Ve (m3/s)
COPPower
Total (KW)Ve
(m3/s)COP
Power Total (KW)
Ve (m3/s)
COPPower
Total (KW)Ve
(m3/s)COP
2791.90 0.1419 3.58 1768.81 0.1419 4.52 1102.50 0.1419 5.44 649.15 0.1419 6.162494.66 0.1774 4.01 1617.53 0.1774 4.95 1032.45 0.1774 5.81 626.16 0.1774 6.392325.43 0.2129 4.30 1535.14 0.2129 5.21 997.69 0.2129 6.01 622.12 0.2129 6.432226.70 0.2484 4.49 1492.30 0.2484 5.36 988.83 0.2484 6.07 633.21 0.2484 6.322171.34 0.2839 4.61 1476.36 0.2839 5.42 998.06 0.2839 6.01 657.75 0.2839 6.082145.79 0.3194 4.66 1483.94 0.3194 5.39 1023.13 0.3194 5.86 695.26 0.3194 5.752149.01 0.3548 4.65 1512.07 0.3548 5.29 1065.53 0.3548 5.63 746.65 0.3548 5.362177.04 0.3903 4.59 1559.59 0.3903 5.13 1122.92 0.3903 5.34 811.97 0.3903 4.932227.85 0.4258 4.49 1623.07 0.4258 4.93 1197.94 0.4258 5.01 892.40 0.4258 4.482300.43 0.4613 4.35 1708.17 0.4613 4.68 1288.91 0.4613 4.66 988.98 0.4613 4.042389.48 0.4968 4.19 1809.82 0.4968 4.42 1397.89 0.4968 4.29 1103.05 0.4968 3.63
Tw,in,c = 25 C and Tw,in,e = 14 C0.4795 m3/s 0.4795 m3/s 0.4795 m3/s0.4795 m3/s
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Optimization
Chiller Water Flow And Condenser Water Flow Optimization:
Qe = 10,000 kWVe,opt = 0.349 m3/sVc,opt = 0.408 m3/s
Tw,in,e = 14 C; Tw,in,c = 25 C
Vc (m3 /s)
Vc (m 3/s)
Tota
l Pow
er (K
W)
38
Optimization
Chiller Water Flow And Condenser Water Flow Optimization:
Qe = 8,000 kWVe,opt = 0.296 m3/sVc,opt = 0.355 m3/s
Tw,in,e = 14 C; Tw,in,c = 25 C
Vc (m3 /s)
Vc (m 3/s)
Tota
l Pow
er (K
W)
39
Optimization
Chiller Water Flow And Condenser Water Flow Optimization:
Qe = 6,000 kWVe,opt = 0.249 m3/sVc,opt = 0.332 m3/s
Tw,in,e = 14 C; Tw,in,c = 25 C
Vc (m3 /s)
Vc (m 3/s)
Tota
l Pow
er (K
W)
40
Optimization
Chiller Water Flow And Condenser Water Flow Optimization:
Qe = 4,000 kWVe,opt = 0.205 m3/sVc,opt = 0.251 m3/s
Tw,in,e = 14 C; Tw,in,c = 25 C
Vc (m3 /s)
Vc (m 3/s)
Tota
l Pow
er (K
W)
41
Optimization
Chiller Water Flow And Condenser Water Flow Optimization:
Tw,in,e = 14 C; Tw,in,c = 25 C
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Optimization
Chiller Water Flow And Condenser Water Flow Optimization:
43
Conclusions
Variable Speed compressor provide savings of 30-40%
Variable speed pump for water circulation play an imperative role in
reducing overall power consumption of chiller plant.
Modeling of chiller components can be performed with limited
engineering information from manufactures.
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Future Work
More rigorous compressor loss model
Transient model for the condenser and evaporator
Cooling tower Model
Variable Speed condenser pump
Investigate the effect of pressure drop and resistance from
refrigerant side
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Q&A
45
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