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Page 1: 1 Optimal Control of Chiller Condenser Sub-cooling, Compressor Speed, Tower Fan and Pump Speeds, and IGV Omer Qureshi, Hassan Javed & Peter Armstrong,

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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 Modelsโ€”Chiller 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) โ€ข Constant speedโ€ข 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:EvaporationSuperheating๐žฎ โ€“ NTU MethodSingle Stream HX for evaporationCrossflow HX for super heating

1st Pass 2nd Pass

๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก ,1 ๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก ,2๐‘Ž ๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก ,2๐‘

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Evaporator Model

Equations utilized in Evaporator Model

h ๐‘–๐‘› ,๐‘’=0.023๐‘…๐‘’๐‘’0.8๐‘ƒ๐‘Ÿ

0.4 ๐‘˜๐‘ค

๐ท๐‘’ ,๐‘–

๐‘ˆ๐ด๐‘’=1

1๐ด๐‘–๐‘› ,๐‘’h๐‘–๐‘› ,๐‘’

+๐‘…๐‘ƒ ,๐‘’

๏ฟฝฬ‡๏ฟฝ๐‘š๐‘–๐‘›ยฟmin [๐‘๐‘ ,๐‘ค๏ฟฝฬ‡๏ฟฝ๐‘ค ,๐‘’ยฟ ,๐ถ๐‘ , ๐‘Ÿ ๏ฟฝฬ‡๏ฟฝ๐‘Ÿ ]ยฟ

๐ด๐‘–๐‘› ,๐‘’ ,1=๐œ‹ ๐ท๐‘’ ,๐‘–๐ฟ๐‘’(๐‘ยฟยฟ๐‘’ /2)ยฟ๐ด๐‘–๐‘› ,๐‘’ ,1๐‘Ž=๐œ‹ ๐ท๐‘’ ,๐‘– ๐‘ฅ๐‘’๐ฟ๐‘’(๐‘๐‘’ /2)๐ด๐‘–๐‘› ,๐‘’ ,1๐‘=๐œ‹ ๐ท๐‘’ , ๐‘–ยฟ

๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก ,๐‘’=๐‘‡๐‘ค ,๐‘–๐‘› ,๐‘’โˆ’๐‘„๐‘ก ,๐‘’

๐‘๐‘ ,๐‘ค๐‘š๐‘ค

Evaporation Evaporation Superheating

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Evaporator Model

Equations utilized in Evaporator Model

๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก ,2๐‘Ž=๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก ,1โˆ’(๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก ,1โˆ’๐‘‡ ๐‘’) (1โˆ’๐‘’โˆ’๐‘๐‘‡๐‘ˆ๐‘’ ,2 ๐‘Ž )

๐œ€2๐‘=1โˆ’๐‘’๐‘ฅ๐‘ [( 1๐ถ๐‘Ÿ ) (๐‘๐‘‡๐‘ˆ๐‘’2๐‘)0.22{exp [โˆ’๐ถ๐‘Ÿ (๐‘๐‘‡๐‘ˆ๐‘’ ,2๐‘)0.78 ]โˆ’1}]๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก ,2๐‘=๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก , 2๐‘Žโˆ’๐œ€2๐‘(๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก , 2๐‘Žโˆ’๐‘‡๐‘’)

๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก ,1=๐‘‡๐‘ค ,๐‘–๐‘› ,๐‘’โˆ’(๐‘‡๐‘ค ,๐‘–๐‘› ,๐‘’โˆ’๐‘‡๐‘’) (1โˆ’๐‘’โˆ’ ๐‘๐‘‡๐‘ˆ๐‘’1 )

๐ฟ๐‘’=8.947 ๐‘ฅ 10โˆ’3๏ฟฝฬ‡๏ฟฝ๐‘Ÿ

2โˆ’3.6279๐‘ฅ 10โˆ’1๏ฟฝฬ‡๏ฟฝ๐‘Ÿโ‘+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-Superheating๐žฎ โ€“ NTU Method

1st Pass 2nd Pass

๐‘‡๐‘ค ,๐‘š๐‘–๐‘ฅ ,๐‘๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก ,2๐‘Ž ๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก ,2๐‘

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Equations utilized in Condenser Model

1a. Sub-Cooling Section(First Pass):

Condenser Model

h ๐‘–๐‘› ,๐‘ , 1๐‘Ž=0.023๐‘…๐‘’๐‘ 10.8๐‘ƒ๐‘Ÿโ‘

0.4 ๐‘˜๐‘ค

๐ท๐‘ 1 ,๐‘–

๐‘ˆ๐ด๐‘ , 1๐‘Ž=1

1๐ด๐‘–๐‘› , ๐‘, 1๐‘Žh ๐‘–๐‘› ,๐‘ , 1๐‘Ž

+๐‘…๐‘ƒ , ๐‘ ,1๐‘Ž

๐œ€๐‘ ,1๐‘Ž=1โˆ’๐‘’โˆ’๐‘๐‘‡๐‘ˆ๐‘ ,1๐‘Ž (1โˆ’๐ถ๐‘Ÿ ,1 ๐‘Ž )

1โˆ’๐ถ๐‘Ÿ , 1๐‘Ž๐‘’โˆ’๐‘๐‘‡๐‘ˆ๐‘ ,1 ๐‘Ž(1โˆ’๐ถ๐‘Ÿ ,1 ๐‘Ž)

๐‘‡ ๐‘๐‘ =๐‘‡ ๐‘ 2โˆ’๐œ€๐‘, 1๐‘Ž๐ถ๐‘š๐‘–๐‘› ,1๐‘Ž(๐‘‡ ๐ถ 2โˆ’๐‘‡๐‘ค ,๐‘–๐‘› , ๐‘)

๏ฟฝฬ‡๏ฟฝ๐‘Ÿ ๐‘๐‘ ,๐‘Ÿ

๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก ,1๐‘Ž=๐‘‡๐‘ค , ๐‘–๐‘› ,๐‘+๏ฟฝฬ‡๏ฟฝ๐‘Ÿ ๐‘๐‘ ,๐‘Ÿ (๐‘‡ ๐ถ 2โˆ’๐‘‡ ๐‘†๐ถ)๏ฟฝฬ‡๏ฟฝ๐‘ค ,๐‘๐‘ฅ1 ,๐‘Ž๐‘๐‘ ,๐‘ค

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1b. Condensation Section (First Pass):

Mixing Section:

Condenser Model

h ๐‘–๐‘› ,๐‘ , 1๐‘=0.023๐‘…๐‘’๐‘ 1๐‘0.8๐‘ƒ๐‘Ÿโ‘

0.4 ๐‘˜๐‘ค๐ท๐‘ 2 , ๐‘–

๐‘ˆ๐ด๐‘ , 1๐‘=1

1๐ด๐‘–๐‘› , ๐‘ ,1๐‘h๐‘–๐‘› ,๐‘ ,1๐‘

+๐‘…๐‘ƒ , ๐‘ ,1๐‘

๐‘๐‘‡๐‘ˆ ๐‘ ,1๐‘=๐‘ˆ๐ด๐‘ ,1๐‘

๏ฟฝฬ‡๏ฟฝ๐‘š๐‘–๐‘›,๐‘ค

๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก ,1๐‘=๐‘‡๐‘ค ,๐‘–๐‘› ,๐‘+๐‘ฅ๐‘๐‘Ž๏ฟฝฬ‡๏ฟฝ๐‘Ÿ (๐ป๐ถ2โˆ’๐ป๐ถ 3)

๏ฟฝฬ‡๏ฟฝ๐‘ค ,๐‘(1โˆ’๐‘ฅยฟยฟ1๐‘Ž)๐‘๐‘ ,๐‘ค ยฟ

๐‘‡๐‘ค ,๐‘š๐‘–๐‘ฅ ,๐‘=๏ฟฝฬ‡๏ฟฝ๐‘ค ,๐‘๐‘ฅ1 ,๐‘Ž๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก1 ,๐‘Žโˆ’๏ฟฝฬ‡๏ฟฝ๐‘ค ,๐‘

(1โˆ’๐‘ฅยฟยฟ1๐‘Ž)๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก 1๐‘

๏ฟฝฬ‡๏ฟฝ๐‘ค ,๐‘

ยฟ

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2a. Condensation Section (Second Pass):

2b. De-superheating Section (Second Pass):

Condenser Model

h ๐‘–๐‘› ,๐‘ , 2๐‘Ž=0.023๐‘…๐‘’๐‘ 2๐‘Ž0.8๐‘ƒ๐‘Ÿโ‘

0.4 ๐‘˜๐‘ค

๐ท๐‘ 2 ,๐‘–

๐‘ˆ๐ด๐‘ , 2๐‘Ž=1

1๐ด๐‘–๐‘› , ๐‘ ,2๐‘Žh๐‘–๐‘› , ๐‘ ,2๐‘Ž

+๐‘…๐‘ƒ ,๐‘ , 2๐‘Ž๐‘๐‘‡๐‘ˆ ๐‘ ,2๐‘Ž=

๐‘ˆ๐ด๐‘ , 2๐‘Ž

๏ฟฝฬ‡๏ฟฝ๐‘š๐‘–๐‘›,๐‘ค

๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก ,2๐‘Ž=๐‘‡๐‘ค ,๐‘š๐‘–๐‘ฅ ,๐‘+๐‘ฅ๐‘๐‘๏ฟฝฬ‡๏ฟฝ๐‘Ÿ๐‘๐‘ ,๐‘Ÿ (๐ป๐ถ 2โˆ’๐ป๐ถ 3)

๏ฟฝฬ‡๏ฟฝ๐‘ค ,๐‘๐‘๐‘ ,๐‘ค

๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก ,2๐‘=๐‘‡๐‘ค ,๐‘œ๐‘ข๐‘ก 2๐‘Ž+๏ฟฝฬ‡๏ฟฝ๐‘Ÿ๐‘๐‘ , ๐‘Ÿ , 2๐‘(๐‘‡ ๐ถ1โˆ’๐‘‡ ๐ถ 2)

๏ฟฝฬ‡๏ฟฝ๐‘ค ,๐‘๐‘๐‘ ,๐‘ค

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Condenser Model

22 24 26 28 30 32 3422

24

26

28

30

32

34

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

35

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

โ€ข Gear efficiency is taken as 90%

โ€ข Velocity profile is assumed as constant, along the hub and tip

โ€ข The kinetic energy of refrigerant entering the diffuser is completely converted to useful energy

โ€ข Diffuser and IGV losses are not modeled

โ€ข Water flow rate for motor cooling is taken as constant

โ€ข 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

๐ผ๐‘ ๐‘’๐‘›๐‘ก๐‘Ÿ๐‘œ๐‘๐‘–๐‘ ๐‘Š๐‘œ๐‘Ÿ๐‘˜ = ๐‘ค๐‘–๐‘ ๐‘’๐‘› = โˆ’ 1 ๐‘ƒ1๐œŒ1 เตฌ๐‘ƒ3๐‘ƒ1เตฐ

โˆ’1เต—๏ฟฝโˆ’ 1 ๐œ‚๐‘”๐‘’๐‘Ž๐‘Ÿเต˜

๐‘€๐‘Ž๐‘ ๐‘  ๐น๐‘™๐‘œ๐‘ค ๐‘Ÿ๐‘Ž๐‘ก๐‘’ ๐‘œ๐‘“ ๐‘Ÿ๐‘’๐‘“๐‘Ÿ๐‘–๐‘”๐‘’๐‘Ÿ๐‘Ž๐‘›๐‘ก= ๐‘šแˆถ= ๐œ™2๐ด2๐‘ˆ2๐œŒ2

RPM is calculated in an iterative process by satisfying the following equation

๐‘Ÿ๐‘’๐‘ ๐‘ข๐‘™๐‘ก = ๐‘šแˆถ๐‘ ๐‘๐‘Ž๐‘‘๐‘Ž โˆ’ ๐‘šแˆถ๐‘๐‘Ž๐‘™

Total Work

๐‘Š๐‘Ž๐‘๐‘ก = ๐‘Š๐‘๐‘œ๐‘š๐‘ + ๐‘Š๐‘™๐‘œ๐‘ ๐‘ 

๐‘Š๐‘™๐‘œ๐‘ ๐‘  = โˆ†๐‘ƒ๐‘ก๐‘Ÿ๐‘‰๐‘Ÿ

Total Relative Pressure Drop (Due to Losses)

โˆ†๐‘ƒ๐‘ก๐‘Ÿ = ๐‘“๐‘(๐‘ƒ๐‘ก๐‘Ÿ1 โˆ’ ๐‘ƒ๐‘ 1) เดฅ๐‘–๐‘–

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

๐ผ๐‘›๐‘๐‘–๐‘‘๐‘’๐‘›๐‘๐‘’ ๐ฟ๐‘œ๐‘ ๐‘ = 1โˆ’ ๐‘‰๐‘š1๐‘Š1 sinแˆบ๐‘š1แˆปเตจ2 + ๐‘ก๐‘1๐‘2๐‘Ÿ๐‘š1 sinแˆบ๐‘š1แˆปเตจ

2

๐ท๐‘–๐‘“๐‘“๐‘ข๐‘ ๐‘–๐‘œ๐‘› ๐‘™๐‘œ๐‘ ๐‘ = 0.81โˆ’ ๐‘Š1๐‘‡โ„Ž๐‘Š1 เตจ2 โˆ’ ๐ผ๐‘›๐‘๐‘–๐‘‘๐‘’๐‘›๐‘๐‘’ ๐ฟ๐‘œ๐‘ ๐‘ 

๐‘†๐‘˜๐‘–๐‘› ๐น๐‘Ÿ๐‘–๐‘๐‘ก๐‘–๐‘œ๐‘› ๐ฟ๐‘œ๐‘ ๐‘ = 4๐‘๐‘“แ‰†๐‘Šเดฅ๐‘Š1แ‰‡2 ๐ฟ๐ต๐ท๐ป

๐ต๐‘™๐‘Ž๐‘‘๐‘’ ๐ฟ๐‘œ๐‘Ž๐‘‘๐‘–๐‘›๐‘” ๐ฟ๐‘œ๐‘ ๐‘ = (โˆ†๐‘Š ๐‘Š1)ฮค 224

๐ธ๐‘ฅ๐‘๐‘Ž๐‘›๐‘ ๐‘–๐‘œ๐‘› ๐ฟ๐‘œ๐‘ ๐‘ = แ‰ˆแˆบ โˆ’ 1แˆป๐‘‰๐‘š2๐‘Š1 2

๐ถ๐‘™๐‘’๐‘Ž๐‘Ÿ๐‘Ž๐‘›๐‘๐‘’ ๐บ๐‘Ž๐‘ ๐ฟ๐‘œ๐‘ ๐‘ = 2๐‘šแˆถ๐ถ๐ฟโˆ†๐‘ƒ๐ถ๐ฟ๐‘š แˆถ1๐‘Š12

๐ป๐‘ข๐‘โˆ’ ๐‘†โ„Ž๐‘Ÿ๐‘œ๐‘ข๐‘‘ ๐ฟ๐‘œ๐‘ ๐‘ = (เดค๐‘š๐‘เดค๐‘Šเดฅ ๐‘Š1)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

๐ป๐‘’๐‘Ž๐‘ก ๐‘…๐‘’๐‘—๐‘’๐‘๐‘ก๐‘’๐‘‘= ๐‘„๐‘Ÿ๐‘’๐‘—๐‘’๐‘๐‘ก๐‘’๐‘‘ = ๐‘š๐‘คแˆถโˆ—๐‘๐‘๐‘ค โˆ—แˆบ๐‘‡๐‘๐‘ค๐‘ โˆ’ ๐‘‡๐‘๐‘ค๐‘Ÿแˆป ๐ถ๐‘œ๐‘œ๐‘™๐‘–๐‘›๐‘” ๐‘‡๐‘œ๐‘ค๐‘’๐‘Ÿ ๐‘…๐‘’๐‘ก๐‘ข๐‘Ÿ๐‘› ๐‘‡๐‘’๐‘š๐‘๐‘’๐‘Ÿ๐‘Ž๐‘ก๐‘ข๐‘Ÿ๐‘’= ๐‘‡๐‘๐‘ค๐‘ โˆ’ ๐‘„๐‘Ÿ๐‘’๐‘—๐‘’๐‘๐‘ก๐‘’๐‘‘๐‘š๐‘คแˆถโˆ—๐‘๐‘๐‘ค

๐‘„๐‘Ÿ๐‘’๐‘—๐‘’๐‘๐‘ก๐‘’๐‘‘ = โˆ—๐ถแˆถ๐‘š๐‘–๐‘› โˆ—แˆบ๐‘‡๐‘๐‘ค๐‘ โˆ’ ๐‘‡๐‘ค๐‘แˆป = 1โˆ’ ๐‘’โˆ’๐‘๐‘‡๐‘ˆ(1โˆ’)1โˆ’ ๐‘’โˆ’๐‘๐‘‡๐‘ˆ(1โˆ’)

๐‘๐‘‡๐‘ˆ= ๐‘š_๐‘คแˆถ๐‘š_๐‘Žแˆถ ๐‘€๐‘’๐‘€

๐‘€๐‘’๐‘€= ๐พ โˆ—๐‘Žโˆ—๐‘‰๐‘š_๐‘คแˆถ

๐‘€๐‘Ž๐‘ ๐‘  ๐น๐‘™๐‘œ๐‘ค ๐‘œ๐‘“ ๐ด๐‘–๐‘Ÿ= ๐‘š_๐‘Žแˆถ = ๐‘‰๐‘š๐‘Ž๐‘ฅแˆถ โˆ—๐œŒ๐‘Ž โˆ—๐‘“

Regression Coefficient

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Assumptions, Specifications and Input/ Output Variables

Cooling Tower Model

Assumptions

โ€ข Air exiting the tower is saturated with water

vapor and is only characterized by its

enthalpy

โ€ข Reduction of water flow rate by evaporation is

neglected in the energy balance.

โ€ข Mass flow rate is calculated by considering

linear proportionality of mass flow rate of air

and motor speed.

Inputs Outputs

โ€ข Wet-bulb temperatureโ€ข Cooling tower supply water temperatureโ€ข Dry-bulb temperature โ€ข Mass flow rate of waterโ€ข Cooling tower fan/motor speed

โ€ข Cooling tower return water temperatureโ€ข Merkelโ€™s 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)

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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)

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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)

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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)

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41

Optimization

Chiller Water Flow And Condenser Water Flow Optimization:

Tw,in,e = 14 C; Tw,in,c = 25 C

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42

Optimization

Chiller Water Flow And Condenser Water Flow Optimization:

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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