Full Thesis - Bangladesh University of Engineering and ...

ANALYTICAL INVESTIGATION FOR THE SOLARHEAT DRIVEN COOLING AND HEATING SYSTEMFOR THE CLIMATIC CONDITION OF DHAKA

Submitted byRIFAT ARAROUF

Student nOP040909400 1PSession April- 2009

111111 1111 111 III III113260

Department of MathematicsBANGLADESH UNIVERSITY OF ENGINEERING AND

TECHNOLOGY DHAKA-IOOOJuly-2014

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This thesis entitled Analytical Investigation for the Solar Heat Driven Coolingand Heating System for the Climatic Condition of Dhaka submitted by RifatAra Rouf Roll nOP0409094001P Registration no 0403447 Session April-2009 hasbeen accepted as satisfactory in partial fulfillment of the requirement for the degree ofDoctor of Philosophy in Mathematics on 12th July 2014

Board of Examiners

1

2

-~tY

Dr Md Abdul Hakim KhanProfessorDepartment of MathematicsBUET Dhaka-lOOO(Supervisor)

At~Dr K C Amanul AlamAssociate ProfessorDepartment of Electronics and Communication EngineeringEast-West University Dhaka-1212(Co-Supervisor)

Chairman

Member

3 _HeadDepartment of MathematicsBUET Dhaka-lOOO

4D~ProfessorDepartment of MathematicsBUET Dhaka-1 000

11

Member (Ex-Officio)

Member

5 Dr MdManiml AlamSarkerProfessor

Departl11ent of Mathematics aUETJ)haka-1 000

Member

~ I 7bull _

6 (dJ~[)r~MdQuamml Islam

bullProfessor OepaTtrrentof MechaniCalEngineeringBOOT lgthaka-IQOO

-

Member

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)n-~~7bull~_(_~-_v_) _

DrAKJvL Sadml IslamPrOfessor Department of Mechanical EngineeringBUET Dhaka-IOOO(Professor Dept ofMechariical and Chemical Engineering

IslarnicUniversity of Technology Gazipur)

)

DLMd Abdur RazzaqAkhandaPrOfessorDepartment of Mechanical and Chemical EngineeringIslamic University of Technology Gazipur

Member (External)

iii

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DEDICATION

This work is dedicatedto

My beloved parents Khaleda Begum and Md Abdur Rouf

tV

Candidates Declaration

It is hereby declared that this thesis or any part ofit has not been submitted elsewhere(Universities or Institutions) for the award of any degree or diploma

~A~Rifat Ara Rouf

12th July 2014

v

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Acknowledgement

Praise be to Allah the most gracious the most merciful

I convey my deep respect and gratitude to Dr Md Abdul Hakim Khan Professor

Department of Mathematics Bangladesh University of Engineering and Technology

Dhaka for his support guidance and cooperation throughout the thesis work

I am grateful and express my profound appreciation to Dr K C Amanul Alam

Associate Professor Department of Electronics and Communication Engineering

East-West University Bangladesh for his generosity continuous guidance during the

whole period of my research work Also I am indebted to him for his valuable time

and patience in thepreparation of this thesis paper

I express my profound gratitude to my collaborative researchers Dr Francis Meunier

Professor Emeritus at Conservatoire National des Arts et Metier (Paris) France Dr

Bidyut Baran Saha Professor at Interdisciplinary Graduate School of Engineering

Sciences and International Institute for Carbon-Neutral Energy Research (WPI-

I2CNER) Kyushu University Japan and Dr Ibrahim 1 EI-Sharkawy Associate

Professor Mechanical Power Engineering Department Faculty of Engineering

Mansoura University Egypt and Research Fellow Faculty of Engineering Sciences

Kyushu University Japan for sharing their knowledge support and above all their I

acceptance My gratitude towards all of my teachers Department of Mathematics

Bangladesh University of Engineering and Technology Dhaka for the lessons and

philosophy they shared with me throughout these years Specially Dr Md Mustafa

Kamal Chowdhury Professor Department of Mathematics Bangladesh University of

Engineering and Technology Dhaka Dr Md Manirul Alam Sarker Professor

Dhaka for their guidance encouragement and support Dr Md Abdul Alim

Professor Department of Mathematics Bangladesh University of Engineering and

Technology Dhaka for his-recognition and support whenever I needed My immense

appreciation to Dr Md Quamrul Islam Professor Department of Mechanical

VI

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Engineering Bangladesh University of Engineering and Technology Dhaka Dr A

K M Sadrul Islam Professor Department of Mechanical Engineering Bangladesh

University of Engineering and Technology Dhaka (BUET) for their valuable remark

and advice

My special appreciation towards Dr Mohammed Anwer Professor School of

Engineering and Computer Science Independent University Bangladesh for his

encouragement My respected teachers Professor A F M Khodadad Khan Professor

Department of Physical Sciences School of Engineering and Computer Science

Independent University Bangladesh Professor Dr M ~war Hossain Ex President(

Bangladesh Mathematical Society Dr Amal Krishna Halder Professor Department

of Mathematics University of Dhaka for their confidence in me affection throughout

my student life and guidance whenever I needed I want to remember my respected

mentor Late Professor Dr Farrukh Khalil who would have been greatly happy over

this achievement 1thank his departed soul for his affection and encouragement in my

professional and student life

I acknowledge Renewable Energy Research Center (RERC) University of Dhaka for

providing insolation (solar irradiation) data of Dhaka station and Bangladesh

Meteorology Department (BMD) for providing climatic data

I would like to thank all of my friends and colleagues for their rally round and

understanding specially Khaled Mahmud Sujan in organizing this thesis and Md

Abdur Rahman for data collection Last but not the least my parents and my family

My absolute gratitude towards my parents without their advice and support it was

impossible to continue and complete this thesis I express my heartfelt thanks to myt

husband Ahsan Uddin Chowdhury and daughters Maliha Tanjurn Chowdhury and

Nazifa Tasneem Chowdhury for their encouragement support patience and

understanding

Vll

_ _--_--- -

Abstract

Solar powered adsorption cooling system had been investigated with different

adsorbateadsorbent pair For the climatic condition of Tokyo utilizing silica gel-

water pair at least 15 collectors with cycle time 1500s have been found to be

necessary to get required bed temperature of 85degC Thus maximum cyclic average

cooling capacity has been reported as 10kW at noon Following this investigation a

similar scheme has been taken in to consideration to utilize the climatic data of Dhaka

for solar heat driven room cooling purpose As Dhaka (Latitude 23deg46N Longitude

9023E) isa tropical region and shortage in energy sector is a burning issue for this

mega city if solar insolation can be properly utilized for space cooling or cold storage

purposes country could gain a reasonable backup in energy sector Based on these

possibilities an analytical investigation of solar heat driven adsorption cooling system

has been done based on the climatic condition of Dhaka where a two bed basic

adsorption chiller with silica gel-water pair as adsorbent and adsorbate have been

considered The climatic data of a typical hot day of summer has been chosen in order

to investigate for the optimum projection area performances based on different

collector number and cycle time For the climatic condition of Dhaka 22 solar

thermal collectors consisting of a gross 0(5313m2 projection area with 800s cycle

time is needed for maximum cooling capacity of 119 kW For enhancement of

chiller working hours a storage tank has been added with the adsorption cooling

system in two different ways It is observed that storage tank not only supports the

chiller to remain active for a longer time till 220h at night but also prevents loss of

heat energy Furthermore installed solar thermal collectors along with the hot water

storage tank could be utilized for hot water supply for house hol~ use during the

winter season which could again save notable amount of energy from primary energy

sources like natural gas and electricity which are used for cooking and for water

heating purposes

VIp

CONTENTS

Board of Examiners

Acknowledgements

Abstract

Nomenclature-

List of Tables

List of Figures

ii

v

vi

viii

xiii

xiv

xv

CHAPTERl (

Introduction11 Introduction

12 History of Ancient Refrigeration

121 Nocturnal Cooling

122 Evaporative Cooling

123 Cooling by Salt Solutions

124 Time Line

13 Science in Adsorption Process

131 Adsorption Equilibria

132 Adsorbates and Adsorbents

J 33 Heat of Adsorption134 Adsorbent Used in The Thesis Work

14 Literature Review

15 Refrigeration Cycle and Their Development

151 Thermodynamics of Refrigeration

Cycle

152 Traditional Vapor Compression Cycle

153 Absorption Refrigeration Cycle

154 Basic Adsorption CyCle

IX

1

2

3

5

6

7

8

10

11

13

14

17

16 Advanced Adsorption Refrigeration Cycle

161Heat Recovery Adsorption(

Refrigeration Cycle

162 Mass Recovery Adsorption

Refrigeration Cycle

163 Multi-stage and Cascading Cycle

17 Solar Adsorption Cooling

171 Solar Thermal Collector

18 Importance of The Present Thesis Work

19 Objectives of The Present Thesis Work

110 Outline of The Thesis

CHAPTER 2

Solar Adsorption Cooling Based on the

Climatic Condition of Dhaka21 Introduction

22 System Description

23 Formulation

231 Solar System

232 Simulation Procedure

24 Result and Discussion

241 Adsorption Unit Performances for Different

Number of Collectors

Cycle Time

243 Effect of Operating Conditions

25 Summary

x

18

26

27

353537

3738

39

4041

45

4750

51

54

6071

r ~-I

I j

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CHAPTER 3

Yearly Analysis of the Solar Adsorption

Cooling for the Climatic Condition of

Dhaka

31 Introduction

33 Summary

CHAPTER 4

Implementation of Heat Storage with Solar

Adsorption Cooling Enhancement of

System Performance

41 Introduction

43 Mathematical Formulation

45 Summary

CHAPTERS

Hot Water Supply During Winter Season

Utilization of Solar Thermal Collectors51 Introduction

52 System Description and Mathematical Equations

54 Summary

CHAPTER 6

Conclusion and Future Work

Xl

73

88

89

899094

95

119

121

122

124

127

128

-

Future work

References

Publications from this Thesis Work

Xli

131

133137

r

Nomenclature

A Area (m2)

q Concentration (kg refrigerant kgadsorbent)

Eo Activation energy (Jkg-J) bull Concentration at equilibriumq(kg refrigerant kg adsorbent)

L Latent heat of vaporization Jkg-1) QSI Isosteric heat of adsorption (Jkg-1)m Mass flow rate (kgs-I Pc Condensing pressure (Pa)P Pressure (Pa) PE EVaporating pressure (Pa)Ps Saturated vapor pressure (Pa) T Temperature (K)RgoS Gas constant (Jkg-tK-t) t Time (s)

Rp Average radius of a particle (m) U Overall heat transfer coefficient(Wm-2K-t)

W Weight (kg) Dso Pre-exponential constant (1112 S-l )Cp Specific heat (Jkg-t K-1)

AbbreviationCACC Cyclic average cooling capacity (kW) THs High temperature

COP Coefficient of performance QHS Heat in high temperature

Tcs Intermediate temperature Qcs Heat in intermediate temperature

V Valve SE AdsorptionDesorption bed

S b tu sen 01Sads Adsorber or adsorption des Desorber or desorptionCond condenser eva EvapotatorChill Chilled water Hex Heat exchangercw Cooling water Hw Hot waterIn inlet out Outlets Silica gel w Waterf3 Affinity coefficient e Fractional loading0 vanance

XliI

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I

r~-I

i

List of Tables

21 Numerical values of the coefficients ais and bits 45

22 Design and the operating conditions used in the simulation 49

23 Design of cycle time 61

24 Performance of different design of cycle time 65

31 Climatic data for several months 78

41 Design of the solar adsorption cooling system with storage t~ 9142 Choices of the cycle time 91

-

43 Design of Reserve tank

XIV

94

I

List of Figures

II

Figure 11

Figure 12

Figure 13

Figure 14

Figure 15

Figure 16

Figure 17

Figure 18

Typical single stage vapor compression refrigeration source

Heat pump and refrigeration cycle Wikipedia [2014]

Source Heat pump and refrigeration cycle Wikipedia [2014]

The vapor absorption system source Images of absorption

refrigeration cycle [2014]

a) Clapeyron and schematic diagram of heating and

pressurization mode Source Principle of adsorption cycles

for refrigeration or heat pumping [2014]

b) Clapeyron and schematic diagram of heating and

desorption condensation mode Source Principle of

adsorption cycles for refrigeration or heat pumping [2014]

c) Clapeyron and schematic diagram of cooling and

depressurization mode Source Principle of adsorption

cycles for refrigeration or heat pumping [2014]

d) Clapeyron and schematic diagram of cooling and

adsorption mode Source Principle of adsorption cycles for

refrigeration or heat pumping [2014]

Clapeyron diagram of ideal adsorption cycle source Farid

[2009]

Schematic diagram of single stage two bed basic adsorption

cooling system

Schematic diagram of heat recovery two-bed adsorption

refrigeration system at heat recovery mode when heat is

transported from desorber SE2to adsorber SEI

Clapeyron diagram of mass recovery cycle source Farid

[2009]

xv

15

16

19

20

21

22

23

24

25

28

Figure 19 Conceptual P-T-X diagram for conventional and two stage 30

adsorption cycles ( source Alam et al [2004])

Figure 110 Schematic diagram of a two stage adsorption chiller 31

Figure 111 Schematic diagram of four bed adsorption refrigeration 33

cascading cycle of mass recovery (source Akahira et al

[2005])

Figure 112 Artists view of compound parabolic concentrator (CPC) 36

collector Source Alamet al [2013]

Figure 21 Schematic diagram of Solar cooling adsorption installation 42 Figure 22 Solar insolation simulated and measured for the month of 48

April

Figure 23 Performance of the chiller for different number of collectors 52 (a) Cooling capacity for different number of collectorsII Figure 23 Performance of the chiller for different number of collectors 53

~ (b) Coefficient of performance in a cycle for differentrnumber of Collectors

Figure 23 Performance of the chiller for different number of collectors 53

(c ) COPsc for different number of collectors

Figure 24 Solar adsorption cooling for different collectors amp their 56

optimum cycle time (a) Cooling capacity of adsorption unit

for different collectors amp their optimum cycle time

optimum cycle time (b) Coefficient of performance in a

cycle of adsorption unit for different collectors amp their

optimum cycle time

optimum cycle time (c) Solar coefficient of performance in a

optimum cycle time

XVI

Figure 24

Figure 25

(

Solar adsorption cooling for different collectors amp theiroptimum cycle time (d) COP solarnet for differentcollectors amp their optimum cycle timeAdsorbed temperature of the collector outlet and adsorbent

bed for (a) 24 collectors cycle time 600s

Adsorbed temperature of the collector outlet and adsorbent

bed for (b) 22 collectors cycle time 800s

Figure 26 Temperature histories of the evaporator outlet for different

collector number and cycle time at peak hours

Figure 27 Temperature history of different heat exchangers for 22

collectors for different choices of cycle time (a) uniform

cycle 800s

57

58

59

62

Figure 27

Figure 28

Figure 29

Temperature history of different heat exchangers for 22

collectors for different choices of cycle time (b) 22 collectors

with non uniform cycle starting from 800s decreasing from

140h

collectors for different choices of cycle time (c) 22 collectors

nonuniform cycle starting from 550s increasing till 140h

then decreasing

Performance of solar adsorption cooling for 22 collectors

with different choices of cycle time (a) Cyclic average

cooling capacity

Performance of solar adsorption coolingfor 22 collectors

with different choices of cycle time (b) Coefficient of

Performance in a cycle

with different choices of cycle time (c) Coefficient of

Performance of solar in a cycle

Evaporator outlet for different choice of cycle time at peak

XVII

62

63

64

66

rttI

-

Figure210

Figure 710

Figure 211

Figure 212

Figure 31

hours

Te~perature history different heat exchangers with 22

collectors cycle time 800s for (a) chilled water flow 03 kgs

Temperature history different heat exchangers with 22

collectors cycle time 800s for (b) chilled water flow 1 kgs

Performance of solar -adsorption cooling for 22 collectors

cycle time 800s with different chilled water flow (a) CACC

cycle time 800s with different chilled water flow (b) COP

cycle -

cycle time 800s with different chilled water flow (c) COPsc

Evaporator outlet for different amount of chilled water flow

Solar radiation data for several months ofthe year

(a) March

Solar radiation data for several months of the year

(b) April

(c) June

(d) August

68

69

70

74

75

Figure 31

bullbullbull

(e) October

Figu re 31 Solar radiation data for several months of the year

(t) December

Figure 32 Temperature profile of the heat exchangers for

-different months with 22 collectors cycle time 800s (a)

March

XVIII

76

80

Figure 32 Temperature profile of the heat exchangers for different 80

months with 22 collectors cycle time 800s (b) April

( Figure 32 Temperature profile of the heat exchangers for different 81

months with 22 collectors cycle time 800s (c)June

months with 22 collectors cycle time 800s (d) August

months with 22 collectors cycle time 800s (e) October

months with 22 collectors cycle time 800s (f) December

Figure 33 Comparative Performances of the chiller for different 83

months (a)CACC

I Figure 33 Comparative Performances of the chiller for different 84

months (b) eOPcycle)

months (c) COPse

Figure 34 Chilled water outlet temperature for different month and 85

different cycle time-(a) March

different cycle time (b) April

different cycle time (c) June

different cycle time (d) August

different cycle time (e) October

different cycle time (f) December

Figure 41 Schematic diagram of solar adsorption cooling run by 92

XIX

gt

storage tank design 1

gt Figure 43 Schematic diagram of solar adsorption cooling run by 93

Figure 44 Temperature histories of collector outlet bed and reserve 97

tank for different number of collectors andcycle time on the

first day design 1 (a) 20collectors cycle time 1400s

tank for different number of collectors and cycle time on the

first day design 1 (b) 22 collectors cycle time 1400s

first day design 1 (c) 22 collectors cycle time 1800s

first day design 1 (d) 30 collectors cycle time 1400s

Figure 45 Temperature histories of different heat transfer units for 100three consecutive days for design 1 (a) 22 collectors cycle

time 1400s

Temperature histories of different heat transfer units forFigure 45 100

three consecutive days for design 1(b) 30 collectors cycle

time 1400s

Figure 46 Temperature histories of the heat transfer units at steady 101

statewith (a) 22 collectors and cycle time 1400s design 1

state with (b22 collector and cycle time 1800s design 1

xx

~I

state with (c) 30 collector and cycle time 1400s design 1

Figure 47 Performance of solar adsorption cooling system with storage

tank design 1 (a) cyclic average cooling capacity

Figure 47 performance of solar adsorption cooling system with storage

tank design 1(b) COPcycle

tank design 1 (c) COP solarnet

Figure 48 (a) Comparative CACC with optimum collector area and

cycle time for direct solar coupling and storage tank design 1

Figure 48 (b) Comparative COPsolarnet with optimum collector area

and cycle time for direct solar coupling and storage tank

design 1

Figure 49 Temperature histories of different heat transfer units for

three consecutive days with 30 collectors cycle time 1400s

for design 2

Figure 410 Temperature histories of the heat transfer units at steady

state with (a) 22 collector and cycle time 1400s design 2

state with (b) 30 collector and cycle time 1400s design 2

Figure 411 The adsorption chiller for different number of collectors

and different cycle time at steady state design 2 (a) cyclic

average cooling capacity

- and different cycle time at steady state design 2 (b) COP

cycle

Figure 411 The adsorption chiller for different numb~r of collectors

and different cycle time at steady state design 2 (c)

COPsolarnet

XXI

104

105

106

107

109

110

III

111

Figure 412

Figure 413

Figure 414

Figure 415

Figure 4J5

and different cycle time at steady state design 1 amp 2 (a)

cyclic average cooling capacity

The adsorption chiller for different number of collectors 112

and different cycle time at steady state design 1amp 2 (b)

COP cycle

and different cycle time at steady sta~e design 1 amp 2 (c)

COPsolarnet

The solar adsorption cooling chiller for different choices of 113

cycle time at steady state design 2 (a) cyclic average

cooling capacity

cycle time at steady state design 2 (b) COP cycle

cycle time at steady state design 2 (c) COPsolarnet

Temperature history of different heat exchangers for 30 114

collectors with increasing cycle starting from 800s

Evaporator outlet (a) different design and cycle time 115

Evaporator outlet (b) design 2 and different choices of cycle 115

time

Figure 416

Figure 417

Figure 418

Collector outlet design 1 and design 2 with 30 collectors

and cycle time 1400s

Collector efficiency at steady state for (a) storage tank

design 1

Collector efficiency at steady state for (b) storage tank

design 2

Cooling production by system with direct solar coupling 22

collectors cycle time 800s and with storage tank design 1 amp

2 collector number 30 cycle time 1400s

XXII

116

117

118

b

Figure 419

Figure 51

Figure 52

Figure 53

Figure 54

Figure 55

Heat used in cooling production by the system with direct 118

solar coupling 22 collectors cycle time 800s and with

storage tank design I amp 2 collector number 30 cycle time

1400s

Schematic diagram of hot water chain between collector 123

tank and household use

Schematic diagram of closed hot water chain between 123

collector and tank

Temperature history of collector outlet and bed for direct 125

solar coupling

Temperature history of reserve tank when 22 collectors 126

supply hot water to tank tank supply hot water for

household and supply water fill up the tank

supply hot water to tank no supply of hot water for

household

XXIII

CHAPTER

Introduction

11 Introduction

The life of 20th century dramatically changed due to the new inventions The use of

refrigerator helps one to preserve food for a 10Jgperiod and save time for the

preparation of food On the other hand use of cooling system not only increased the

working potential of people by facilitating them to work with comfort but also helps

to change the architectural design of public places and living places Dozens of

innovations made it possible to transport and store fresh foods and to adapt the

environment to human needs Once luxuries air conditioning and refrigeration are

now common necessities which greatly enhance our quality of life

At present air conditioning and refrigeration systems became more efficient

controllable and mobile It grew from an invisible luxury to a common necessity

Now people can live and work in glassed-in or windowless buildings in porch less

houses or in the warmest and most humid places In an air conditioner air is cooled

and conditioned by units that are similar to domestic refrigerators (Greatest

Engineering Achievments-l 0 Air Conditioning and Refrigeration [2014 D Cold liquidrefrigerant at low pressure flows through coils on one side A centrifugal fan draws

warm air from the room over the coils The cooled and conditioned air is returned to

the room The warmed refrigerant evaporates and then passes into a compressor

where it is pressurized The hot pressurized gas enters a second set of coils on the

exterior side A second fan draws cool external air over the hot coils to dissipate their

heat In the process the refrigerant is cooled to below its boiling point and condenses

into a liquid The refrigerant then passes through an expansion valve where its

pressure is suddenly reduced As this happens its temperature drops and the cooling

cycle begins again

I

In ancient period refrigeration was achieved by natural means such as the use of ice or

evaporative cooling Ice was either

i) Transported from colder regions

ii) Harvested in winter and stored in ice houses for summer use

iii) Made during night by cooling of water by radiation to stratosphere

In 1806 Frederic Tudor began the trade in ice by cutting it from Hudson river and

ponds in Massachusetts and exported it to various countries including India (History

of Refrigeration IIT Kharagpur [2014]) In order to insulate the container sawdust

wood shavings or cork were utilized Making ice naturally by evaporative cooling

known as Nocturnal cooling was another means In India Tudors ice was cheaper than

the locally manufactured ice by nocturnal cooling Other than nocturnal cooling

evaporative cooling and cooling by salt solution were also in use

The art of making ice by nocturnal cooling was perfected in India In this method ice

was made by keeping a thin layer of water in a shallow earthen tray and then

exposing the tray to the night insolation to the stratosphere which is at aroun~ ~55degC

and by early morning hours the water in the trays freezes to ice (History of

Refrigeration lIT Kharagpur [2014])

Evaporative cooling is the process of reducing the temperature of a system by

evaporation of water Evaporative cooling has been used in India for centuries to

obtain cold water in summer by storing the water in earthen pots The water

permeates through the pores of earthen vessel to its outer surface where it evaporates

to the surrounding absorbing its latent heat in part from the vessel which cools the

water Human beings perspire and dissipate their metabolic heat- by evaporative

cooling if the ambient temperature is more than skin temperature It is said that

Patliputra University situated on the bank of river Ganges used to induce the

2

--

f

evaporative-cooled au from the river Suitably located chimneys in the rooms

augmented the upward flow of warm air which was replaced by cool air

Certain substances such as common salt when added to water dissolve in water and

absorb its heat of solution from water (endothermic process) this reduces the

temperature of the solution (water+salt) Sodium Chloride salt (NaCl) can yield

temperatures upto -20degC and Calcium Chloride (CaCh) upto -50degC in properly

insulated containers However this process has limited application

At present refrigeration is produced by artificial means In 1755 a Scottish professor

William Cullen made the first refrigerating machine It could produce a small quantity

of ice in the laboratory Professor William Cullen of the University of Edinburgh

demonstrated this in 1755 by placing some water in thermal contact with ether under a

receiver of a vacuum pump Due to the vacuum pump arid the evaporation rate of

ether increased and water could be frozen This process involves two thermodynamic

concepts the vapor pressure and the latent heat A liquid is in thermal equilibrium

with its own vapor at a preSsure called the saturation pressure which depends on the

temperature alone Oliver Evans in the book Abortion of a young Engineers Guide

published in Philadelphia in 1805 described a closed re(rigeration cycle to produce ice

by ether under vacuum Jacob Perkins an American living in London actually

designed such a system in 1835 In Evans patent he stated I am enabled to use

volatile fluids for the purpose of producing the cooling or freezing of fluids and yet at

the same time constantly condensing such volatile fluids and bringing them again

into operation without waste James Harrison in 1856 made a practical vapor

compression refrigeration system using ether alcohol or ammonia Charles Tellier of

France patented a refrigeration system in 1864 using dimethyle ether which has a

normal boiling point of -236degC Later improvements were made by a number of

researchers throughout the century

The pioneering gemus for mechanical refrigeration system an engmeer Willis

Carrier worked out the basic principles of coding and humidity control (Greatest

3

Engineering Achievments-IO Air Conditioning and Refrigeration [2014]) And

before his idea became a real benefit to the average people it took innovations by

thousands of other engineers This invention of Carrier made many technologies

possible where highly controllable environment is needed such as medical and

scientific research product testing computer manufacturing and space travel The

history of Carriers invention is dramatic According to the claim in the year of 1902

while standing in a train station in Pittsburgh one night Carrier realized that air could

be dried by saturating it with chilled water to induce condensation And the first air

conditioner was built by him on that year for a Brooklyn printer The cooling power

of thisfirst air conditioner was 108000pounds of ice a day

A refrigerator operates in much the sameway as an air conditioner It moves heat

energy from one placeto another Constant cooling is achieved by the circulation of a

refrigerant in a closed system in which it evaporates to a gas and then condenses back

again to a liquid in a continuous cycle If no leakage occurs the refrigerant lasts

indefinitely throughout the entire life of the system

In 1907 Carrier first patented a temperature and humidity control device for

sophisticated industrial process Room cooler was first introduced by Frigidaire

engineers in 1929 In 1930 Thomas Midgley (Greatest Engineering Achievments-l0

Air Conditioning and Refrigeration [2014]) solved the dangerous problem of toxic

flammable refrigerants by synthesizing the worlds first chlorofluorocarbon which has

a trade mark name as Freon Thomas Midgley and Charles Kettering invented Freon

12 (dichlorodifluoromethane) adopted by Frigidaire division of general motors

Packard in 1938 introduced the first automobile air conditioner which was run by the

waste heat of the engine In 1938 Philco-York successfully marketed the first window

air conditioner Refrigeration technology led to certain frozen food technology By

1925 Birdseye and Charls Seabrook developed a deep freezing process for cooked

foods In 1930 Birds Eye Frosted Foods were sold for the first time in Springfield

Massachusetts As the century unfolded improvisation of the refrigeration and air

conditioningsystem went on

e

4

I

i1

The time line of air conditioning and refrigeration system is enclosed below (Greatest

Engineering Achievments-l 0 Air Conditioning and Refrigeration [2014 D

124 TimelineWillis Haviland Carrier designs a humidity control process and pioneers

modem air conditioning

First overseas sale of a Carrier system was made to a silk mill in Yokohama

Japan

Carrier presents his paper Rational Psychometric Formulae to the American

Society-of Mechanical Engineers and thereby forms the basis of modem air-

conditioning

Clarence Birdseye pioneers the freezing of fish of later defrosting and

cooking

1915 Carrier Corp is founded under the name Carrier Engineering

1920s Carrier introduces small air-conditioning units for small businesses and

residences

1922 Carrier develops the centrifugal refrigeration machine

1925 Clarence Birdseye and Charles Seabrook develop a deep-freezing process for

cooked foods that Birdseye patents in 1926

1927 General Electric introduces a refrigerator with a monitor top containing a

hermetically sealed compressor

1929 U S electric re~rigerator sales top 800000 and the average pnce of a

refrigerator falls to $292

1930s Air conditioners are placed III railroad cars transporting food and other

perishable goods

1931 Tranes first air conditioning unit Was developed

1931 GMs Frigidaire division adopts Freon 12 (dichlorodifluoromethane)

refrigerant gas invented by Thomas Midgley of Ethyle Corp and Charles

Kettering of GM

1931 Birds Eye Frosted Foods go on sale across the US as General Foods expands

distribution

5

1937 Air conditioning lis first used for mmmg in the Magma Copper Mine m

Superior Arizona

1938 Window air conditioner marketed by philco-York

1939 The first air-conditioned automobile is engineered by Packard

1947 Mass-produced low-cost window air conditioners become possible

1969 More than half of new automobiles are equipped with air conditioning

1987 Minimum energy efficiency requirements set- The National Appliance Energy

Convertion Act mandates minimum energy efficiency requirements for

refrigerators and freezers as well as room and central air conditioners

1987 The Montreal Protocol- The Montreal Protocol serves as an international

agreement to begin phasing out CFC refrigerants which are suspected to the

thinning of the earths protective high-altitude ozon shield

1992 Minimum energy efficiency standards set for commercial buildings- The US

Energy Policy Act mandates minimum energy efficiency standards for

commercial buildings using research and standards developed by the

American Society of Heating Refrigeration and Air Conditioning Engineers

Adsorption is the adhesion of atoms ions biomolecules of gas liquid or dissolved

solids to a surface This process creates a film of the adsorbate (the molecules or

atoms being accumulated) on the surface of the adsorbent It differs from absorption

in which a fluid permeates or is dissolved by a liquid ot solid The term sorption

encompasses both processes while desorption is the reverse of adsorption It is a

surface phenomenon

During the adsorption process unbalanced surface forces at the phase boundary cause

changes in the concentration of molecules at the solidfluid interface This process

involves separation of a substance from one phase accompanied by its accumulation

or concentration at the surface of another In adsorption process the adsorbing phase is

the adsorbent and the material concentrated or adsorbed at the surface of that phase is

the adsorbate

6

t

--l

Adsorption is a process where molecules atoms or ions accumulate on the surface of

a liquid or a solid material This is different from the absorption process where

molecules or atoms diffuse into the liquid or solid For C02 02 or H2 capture are solid

materials primarily used these materials are referred to as dry sorbents or adsorbents

Molecules atoms or ions accumulate in small quantities per surface area of the

adsorbent therefore are porous solids with a large area per unit volume favoured

Adsorption process can be classified in two

i) Physical adsorption or physisorption and

ii) Chemical adsorption or chemisorptions

The adsorption process that is used in our study is a physisorption Physisorption

occurs at the solid phase these intermolecular forces are same as ones that bond

molecules to the surface of a liquid The molecules that are physically adsorbed to a

solid can be released by applying heat therefore the process is reversible

-Adsorption is an exothermic process accompanied by evolution of heat The quantity

of heat release depends upon the magnitude of the electrostatic forces involved latent

heat electrostatic and chemical bond energies

The heat of adsorption is usually 30-100 higher than the heat of condensation of

the adsorbate The process of adsorption is stronger than condensation to liquid phase

There are fo~r basic theories proposed and used to define the main isotherms of an

adsorption process They are (i) Henrys law (ii) Langmuirs approach (iii) Gibbs

theory and (iv) Adsorption potential theory

(i) Henrys law On an uniform surface for an adsorption process at

sufficiently low concentration (ie all molecules are isolated from their

nearest neighbors) where the equilibrium relationship between the fluid

phase and adsorbed phase concentration will always be linear

(ii) Langmuirs approach In order to understand the monolayer surface

adsorption on an ideal surface this approach is used The approach is

7

based on kinetic equilibrium ie the rate of adsorption of the molecules is

assumed to be equal to the rate of adsorption from the surface

(iii) Gibbs theory Based on ideal gas law The adsorbate is treated in

croscopic and bidimensional form and provides a general relation between

spreading pressure and adsorbed phase concentration Here the volume in

the bulk phase is replaced by the area and the pressure by the spreading

pressure Relating the number of moles of adsorbate the area and the

spreading pressure and using them in the Gibbs equation a number of

fundamental equations can be derived such as linear isotherm and Volmer

isotherm etc

(iv) Adsorption potential theory In order to describe adsorption of gases and

vapor below the capillary condensation region equations such as

Freundlich Langmuir-Freundlich (Sips) Toth Unilan and Dubinin-

Radushkevich (DR) have been used

In chemistry and surface s~ience an adsorbate is a substance adhered to a surface (the

adsorbent) The quantity of adsorbate present on a surface depends on several factors

including adsorbent type adsorbate type adsorbent size adsorbate concentration

temperature pressure etc

The performance of adsorbents used in physisorption IS governed by surface

properties such as surface area micro-pores and macro-pores size of granules in

powders crystals or in pellets If a fresh adsorbent and adsorbate in liquid form co-

exist separately in a closed vessel the adsorbate in liqu~dphase is transported to the

adsorbent This transportation of adsorbate to the adsorbent occurs in the form of

vapor The adsorbent adsorbs heat therefore the adsorbate loses temperature This

phenomenon is used to obtain a cooling effect in air -conditioning and refrigeration

system The heat of adsorption for different adsorbent is either derived from

8

f

Iadsorption isotherms generally referred to as either the isosteric heat (the energy

released in adsorption process) or as the differential heat of adsorption determined

experimentally using a calorimetric method

Based on the polarity of the adsorbents they can be classified in two

i) hydrophilic and ii) hydrophobic Silica gel zeolites and porous or active

alumina have special affinity with polar substances like water These are called

hydrophilic On the other hand non-polar adsorbents like activated carbons polymer

adsorbents and silicalites have more affinity for oils and gases than for water these

are called hydrophobic

Surface properties of the adsorbents ie surface area and polarity characterizes the

adsorbents For large adsorption capacity large surface area is needed Therefore in

need of large surface area in a limited volume large number of small sized pores

between adsrption surface is need~d To characterize adsorptivity of adsorbate the

pore size distribution of the micro- pores to increase the accessibility of adsorbate

molecules to the internal adsorption surface is important

The working pair for solid adsorption is chosen according to their performance at

different temperatures For any refrigerating application the adsorbent must have high

adsorptive capacity at ambient temperatures and low pressures but less adsorptive

capacity at high temperatures and high pressures The choice of the adsorbent depends

mainly on the following factors

(i) High adsorption and desorption capacity to attain high cooling effect

(ii) Good thermal conductivity in order to shorten the cycle time

(iii) Low specific heat capacity

(iv) Chemically compatible with the chosen refrigerant

(v) Low cost and wide availability

The chosen adsorbate (working fluid) must have most of the following desirable

thermodynamics and heat transfer properties

(i) High latent heat per unit volume

9

(ii) Molecular dimensio11s should be small enough to allow easy adsorption

(iii) High thermal conductivity

(iv) Good thermal stability

(v) Low viscosity

(vi) Low specific heat

(vii) Non-toxic non-inflammable non-corrosive and

(viii) Chemically stable in the working temperature range

Based on the above criteria some appropriate working pairs are activated carbon-

methanol zeolite-water zeolite - ammonia activated carbon-ammonia silica gel-

water etc

133 Heat of Adsorption

All adsorption processes are accompanied by heat release ie they are exothermic

processes In adsorbed phase adsorbate molecules are in more ordered configuration

In this process entropy decreases

134 Adsorbent Used in The Thesis Work

In analytical investigation of solar heat driven cooling system for the climatic

condition of Bangladesh hydrophilic adsorbent silica gel is used with water as the

adsorbate due to its straightforward availability Silica gel is prepared from pure silica

and retains chemically bonded traces of water silica gel (Si02 x H20) (about 5) If

it is over heated and loses water its adsorption capacity is lost and it is generally

used in temperature applications under 2000 C Silica gel is available in various pore

size The greater is the surface area per unit mass which is typically 650 m2 gm the

higher is its adsorption capacity Silica gel has a large capacity for adsorbing water

specially at high vapor pressure The heat of adsorption of water vapor on silica gel is

predominantly due the heat of condensation of water The adsorption refrigeration

system with silica gel-water pair can be run with lower temperature heat source (less

than 1000 C) and no harmful chemical extraction occurs during the process Silica gel

is available and comparatively inexpensive to use in mass level

10

-

io-(

In the late 1980s chlorofluorocarbons were found to be contributing to the

destruction of earths protective ozone layer Therefore the production of these

chemicals was phased out and the search for a replacement began Moreover the

increased use of the vapor compressor driven refrigeration devices made us more

dependent on the primary energy resources As the primary energy once used up

cannot be used in the same form again Therefore it is necessary to reduce the

consumption of these resources and introduce renewable energy for the sustainable

development in the global energy sector Thermally driven sorption technology is one

of the probable altem~ives At present absorption (liquid vapor) cycle is most

promising technology Nevertheless adsorption (solid vapor) cycle have a distinct

advantage over other systems in their ability to be driven by heat of relatively low

near-environmental temperatures so that the heat source such that waste heat or

solar heat below 1000 C can be utilized Kashiwagi et al [2002] in determination of

conservation of heat energy carried out investigation on heat driven sorption and

refrigeration system

For the last three decades investigations have been carri~d out both mathematically

and experimentally about different features of this system It is well known that the

performance of adsorption cooling heating system is lower than that of other heat

driven heating cooling systems Different choices of adsorbateadsorbent pairs have

been investigated to study about the optimum driving heat source Zeolite - water pair

studied by Rothmeyer et al [1983] Tchemev et al [1988] and Guilleminot et al

[1981] In these studies the driving heat source was reported as 20WC A cascading

adsorption cycle has also been analyzed by Douss et al [1988] where an activated

carbon - methanol cycle is topped by a zeolite - water cycle Driving heat was

supplied by a boiler and heat source was 200ce In the study of Critoph [1998] a

lower heat source temperature was observed that is over 150cC with activated carbon

- ammonia pair The use of driving heat source with temperatures of less than 100cC

was reported in the study of silica gel - water pair investigated by Saha et al [1995a]

Chua et al [1999] Alam et al [2000a] and Saha et al [1995b2000]

11

I~

f

IIII[

f

I

i

1

Kashiwagi et al [2002] and Chen et al [1998] studied basic cycle of adsorption

cooling for the operating condition of the cycle Where basic cycle with different

adsorber and adsorbent had also been studied Rothmeyer et al [1983] studied the

basic adsorption refrigeration cycle for Zeolite-water pair and Douss and Meunier for

active carbon-methanol pair While Saha et al [1995a] Chua et al [1999] Alam et

al [2000a] and Kashiwagi et al [2002] studied basic cycle with silica gel-water pair

Many researchers studied the advanced cycle either to improve the performance or to

drive the system with relatively low temperature heat source Heat recovery cycle has

been studied by Shelton et al [1990] to improve the COP of the adsorption cooling

system in similar contest Meunier [1986] studied heat recovery cycle with cascaded

adsorption cycle where active carbon - methanol cycle was topped by a zeolite -

water cycle Pons et al [1999] studied mass recovery process in conventional two

beds adsorption cycle to improve the cooling capacity Mass recovery cycle is also

investigated by Akahira et al [2004 2005] While Wang [2001] investigated the

performance of vapor recovery cycle with activated carbon - methanol pair These

investigations indicated that mass recovery cycle is effective for relatively low

regenerative temperature compared with that of basic cycle

Lately investigation has been carried out in order to utilize low driving heat source

As a result multistage and cascaded cycles are proposed Saha et al [2000] discussed

two stage and three stage silica gel-water adsorption refrigeration cycle and Alam et

al [2003] multi-stage multi beds silica gel water cooling cycle to investigate the

operating temperature level of single double and triple stage cycle respectively Later

Alam et al [2004] studied the influence of design and operating conditions for two

stage cycle And Khan et al [2007] investigated the system performance with silica

gel - water pair on a re-heat two-stage adsorption chiller analytically The driving

source temperature for this system was less than 70degC All these investigations show

that heat source temperature level can be reducedby adopting multistage cycle And

cooling capacity can be improved for low temperature heat source Solar coupling

could be one of the attractive and alternative ways to produce necessary cooling

instead of conventional energy source Various researchers have utilized adsorption

12

Mechanical refrigeration is accomplished by continuously circulating evaporating

and condensing a fixed supply of refrigerant in a closed system

technology with direct solar coupling for space cooling and ice-making Clauss et al

[2008] studied adsorptive air conditioning system utilizing CPC solar panel under the

climatic condition of Orly France At the same time Zhang et al [2011] investigated

the operating characteristics of silica gel water cooling system powered by solar

energy utilizing lump~d parameter model Later Alam et al [2013a] utilized lumped

parameter model to investigate the performance of adsorption cooling system driven

by CPC solar panel for Tokyo Solar data Afterwards Rouf et al [2011] performed a

similar study based on the climatic condition of a tropical region Dhaka in search of

the optimum collector number and cycle time As a continuation Rouf et al [2013]

investigated the operating conditions of basic adsorption cooling system driven by

direct solar coupling for the climatic conditions of Dhaka Bangladesh Recently in

anticipation of both enhancement of the working hour and improvement of the system

performance heat storage has been added with the solar heat driven adsorption cooling

system by Alam et al [2013b]

15 Refrigeration Cycl~s and Their Development

151 Thermodynamics of Refrigeration Cycle

I

t f

I

i

~~

The vapor-compression cycle is used in most household refrigerators as well as in

many large commercial and industrial refrigeration systems Figure -11 provides a

schematic diagram of the components of a typical vapour-compression refrigeration

system (Heat pump and refrigeration cycle Wikipedia [2014 D

The thermodynamics of the cycle can be analyzed on a diagram as shown in the figure

below In this cycle a circulating refrigerant such as Freon enters the compressor as a

vapor The vapor is compressed at constant entropy and exits the compressor

superheated The superheated vapor travels through the condenser which first cools

13

lt A ~ -

and removes the superheat and then condenses the vapor into a liquid by removing

additional heat at constant pressure and temperature The liquid refrigerant goes

through the expansion valve (also called a throttle valve) where its pressure abruptly

decreases causing flash evaporation and auto-refrigeration of typically less than half

of the liquid

That results in a mixture of liquid and vapo~at a lower temperatUre and pressure The

cold liquid-vapor mixture then travels through the evaporator coil or tubes and is

completely vaporized by cooling the warm air (from the space being refrigerated)

being blown by a fan across the evaporator coil or tube~ The resulting refrigerant

vapor returns to the compressor inlet to complete the thermodynamic cycle Typically

for domestic refrigeration the coefficient of performance (COP) of compression

cycles lie around 3

The most frequent refrigerants used in these cycles are hydrochlorofluorocarbons

(HCFCs) chlorofluorocarbons (CFCs) hydrobromofluorocarbons (HBFCs) etc

These refrigerants restrain ozone depleting substances On the other hand sorption

refrigeration system makes use of natural refrigerants such as ammonia methanol

water etc Besides these systems can be run by low- grade energy such as waste heat

and solar energy As a result many researchers have made significant efforts to study

typical adsorption refrigeration cycles

In the absorption refrigeration system refrigeration effect is produced mainly by the

use of energy as heat (Images of absorption refrigeration cycle [2014]) In such a

system the refrigerant is usually dissolved in a liquid A concentrated solution of

ammonia is boiled in a vapor generator producing ammonia vapor at high pressureThe high pressure ammonia vapor is fed to a condenser where it is condensed to

liquid ammonia by rejecting energy as heat to the surroundings Then the liquid

ammonia is throttled through a valve to a low pressure During throttling ammonia is

partially vaporized and its temperature decreases

14

f

Condenser May bewater-cool ed orair-cooled Gpor

CompressorQpor

~vaporator

lH bullbull_Wa_nTl_~ air

Expansion

Condenser

Uquid + porValve

Figure 11 Typical single stagevapor compression refrigeration source Heatpump and refrigeration cycle Wikipedia [2014J

15

-Isobars

( ~

t

~

1

~-

-I--

1 _

1-

f

----4-isobar

1gt1 Y Liquid

)Specific Entropy (s)

--_ 1 Vapor

Figure 12 Source Heat pump and refrigeration cycle Wikipedia [2014]

CondenserThrott~evalve

EvaporatorPressureReducing valve

High Pr

i NH3 Vapour

VapQufc ~

~~n~~t~

Q T j1gt~

1 1~ ~-~- ~ -

Strong Absorb~r -

NHJ solution

Low pressmNH3 vapour

Figure 13 The vapor absorption system source Images of absorption

16

This low temperature ammonia is fed to an evaporator where it is vaporized removing

energy from the evaporator Then this low-pressure ammonia vapor is absorbed in the

weak solution of ammonia The resulting strong ammonia solution is pumped back to

the vapour generator and the cycle is completed T~e COP of the absorption system

can be evaluated by considering it as a combination of a heat pump and a heat engine

(Figurel3)

154 Basic Adsorption Cycle

An adsorption cycle for refrigeration or heat pumping does not use any mechanical

energy but only heat energy (Principle of adsorption cycles for refrigeration or heat

pumping [2014]) Moreover this type of cycle basically is a four temperature

discontinuous cycle An adsorption unit consists of one or several adsorbers a

condenser an evaporator connected to heat sources The adsorber -or system

consisting of the adsorbers- exchanges heat with a heating system at high temperature

-HS- and a cooling system at intermediate temperature -CS- while the system

consisting of the condenser plus evaporator exchanges heat with another heat sink at

intermediate temperature (not necessarily the same temperature as the CS) and a heat

source at low temperature Vapour is transported between the adsorber(s) and the

condenser and evaporator

The cycle consists of four periods a) heating and pressurization b) heating and

desorption condensation c) cooling and depressurization and d) cooling and

adsorption evaporation

a) Heating and pressurization during this period the adsorber receives heat while

being closed The adsorbent temperature increases which induces a pressure increase

from the evaporation pressure up to the condensation pressure This period is

equivalent to the compression in compression cycles

b) Heating and desorption condensation During this period the adsorber continues

receiving heat while being connected to the condenser which now superimposes its

pressure The adsorbent temperature continues increasing which induces desorption

of vapor This desorbed vapor is liquefied in the condenser The condensation heat is

17

released to the second heat sink at intermediate temperature This period is equivalent

to the condensation in compression cycles

c) Cooling and depressurization During this period the adsorber releases heat while

being closed The adsorbent temperature decreases which induces the pressure

decrease from the condensation pressure down to the evaporation pressure This

period is equivalent to the expansion in compression cycles

d) Cooling and adsorption evaporation during this period the adsorber continues

releasing heat while being connected to the evaporator which now superimposes its

pressure The adsorbent temperature continues decreasing which induces adsorption

of vapor This adsorbed vapor is vaporized in the evaporator The evaporation heat is

supplied by the heat source at low temperature This period is equivalent to the

evaporation in compression cycles

Basically the cycle is intermittent because cold production is not continuous cold

production proceeds only during part of the cycle When there are two adsorbers in

the unit they can be operated out of phase and the cold production is quasi-

continuous When all the energy required for heating the adsorber(s) is supplied by

the heat source the cycle is termed single effect cycle Typically for domestic

refrigeration conditions the coefficient of performance (COP) of single effect

adsorption cycles lies around 03-0AWhen there are two adsorbers or more other

types of cycles can be processed In double effect cycles or in cycles with heat

regeneration some heat is internally recovered between the adsorbers which

enhances the cycle performance

161 Heat Recovery Adsorption Refrigeration Cycle

Heat recovery process leads to a higher system COP (investigated by Wang et al

[2001]) But experimentally operating with the system would be a little complicated

Mathematically to attain higher COP multiple beds could also be adopted It is a semi-

continuous system operated with two adsorption beds The adsorber to be cooled

18

-~

LoP

II

~ ~ ~HfJatinc+ 1essilation~

I

~~

~

Cooling +~ ~a4s0lJltioh

-lIT

-

AdsomedI

vapour

Ie

-~oCondensel

Figure 14 a) Clapeyron and schematic diagram of heating and pressurization

mode Source Principle of adsorption cycles for refrigeration or

heat pumping [2014J

19

~

--

~

LnP

-lff

Q-

ht Qcs~---II

IIIII

bullbullII_~- -

Figure JA b) Clapeyron and schematic diagram of heating and desorptioncondensation mode Source Principle of adsorp~ion cycles forrefrigeration or heat pumping [2014]

20--_bullbull_--------_- -- _ --_-

-~ -

-

LnP

~

COtliBS + ltii

tlqmssumtttibn -lIT

Figure 14 c) Clapeyron and schematic diagram of cooling and depressurization

modesource Principle Qfadsorption cycles for refrigerati()n or

heat pumping [2014]

21

LnP

-lIT

QcsTcs ===

IIIIIIIIIII_---

Figure 14 d) Clapeyron and schematic diagram of cooling and adsorption

modeSource Principle of adsorption cycles for refrigeration or

heat pumping [2014]

22

I ~ _

I -

i ~i

Ci Pc- bull Wo- InP

bull

PE

I)-

T-o

Figure 15 Clapeyron diagram of ideal adsorption cycle Source Farid [2009]

23

vm

Condenser

SE2

V8

EvaporatorV2 i

II i

r-------

VIrt

i =

Cooling load

Figure 16 Schematic diagram of single stage two bed basic adsorption cooling

system

24

deg IIIIII V4

vs

r -~---~- deg

__ e~ bullr-------Condenser

VI IIi

~

i (IIi= Ii~Ii~ 0

~

V2 V8

Evaporator

----------t-~-~-Cooling load

Figure 17 Schematic diagram of heat recovery two-bed adsorption refrigeration

system at heat recovery mode when heat is transported from desorber SE2 to

adsorbero

SEl

25

transfers its heat to the adsorber to be heated which includes sensible heat as well as

heat of adsorption The system is represented by Figure 17

Between the two adsorbers while adsorber 1 is cooled connected to the evaporator to

realize adsorption refrigeration in evaporator the adsorber 2 connected to the

condenser is heated to obtain heating-desorption-condensation The condenced

refrigerant liquid flows into evaporator via a flow control valve The operating phase

can be changed and the go between will be a short time heat recovery process Two

pumps are used to drive the thermal fluid in the circuit between two adsorbers (the

connection to the heater and cooler are blocked during this process)

Compared to the basic cycle heat recovery in this process is only effective if the heat

transfer fluid temperature leaving the adsorbers is sufficiently high Simulation results

have shown that maximum COP depends on the number of adsorbers and desorbers

installed

1 condenser is heated to obtain heating-desorption-condensation The condenced

refrigerant liquid flows into evaporator via a flow control valve The operating

phase can be changed and the go between will be a short time heat recovery

process Two pumps are used to drive the thermal fluid in the circuit between

two adsorbers (the connection to the heater and cooler are blocked during this

process)

2 Compared to the basic cycle heat recovery in this process is only effective if the

heat transfer fluid temperature leaving the adsorbers is sufficiently high

Simulation results have shown that maximum COP depends on the nllmber of

adsorbers and desorbers installed

162 Mass Recovery Ad~orption Refrigeration Cycle

This process can also be called as an internal vapor recovery process and is reported

to enhance the cooling power Mass recovery is also very effective for heat recovery

adsorption heat pump operation In this process like the previous heat recovery

process at the end of each half cycle one adsorber is cold and the other one is hot

Mean while in addition the former one which is at low pressure e - e must be

pressurized up to the condenser pressureE and similarly the other one which is atC

high pressure must be depressurized down to the evaporator pressure PiJ This process

26

~

of pressurization and depressurization of the adsorbers partially can be conducted

with just one tube between the adsorbers and a vapor valve Through this tube vapor

is transferred from the later adsorber to the former one

The figure below Figure 18 (Farid [2009]) describes an ideal heat and mass recovery

cycle The heat recovery state for a two bed system is shown by the state points e - e

The mass recovery cycle (a2 - a3 - gJ - gl - g2 - g3 - ai - al - a2) is an extended

form of a two bed basic cycle or two bed heat recovery cycle

(a2 - gl - g 2 - al - Q2) shown in figure and the cycles mass is increased from 6x to

6x +8x which causes the refrigeration effect to increase

The principle of these cyCles can be described using Figure 18 The very first part of

each half cycIeis the mass recovery process (path g2 - g3 and a Q2 - a3) Then the

heat recovery process proceeds Heat is transferred from the hot adsorber to the cold

one (path g3 - e) As a consequence the hot adsorber is first depressurized (path

g3 - Q1 ) it then adsorbs vapor from the evaporator ( path al - a2) At the same

time the cold adsorber is first pressurized (path a3 - at ) then vapor that is desorbed

passes into the condenser (path gl - e) Theoretically the heat recovery process

develops until the adsorbers reach the same temperature Actually there still remains

a temperature difference between the adsorbers at the end of this period Then for

closing each half cycle the adsorbers are respectively connected to the heat source

and heat sink (path e - g 2 and e - a2) bull The second half cycle is performed the same

way except that the adsorbers now exchange their roles Due to this process about

35 of the total energy transmitted to each adsorber can be internally recovered

including part of the latent heat of sorption

The single stage cycle that is discussed in the prevIOUS sections have certain

limitations It does not perform well at very low temperatures To improve the system

performance under the above situations advanced cycles with adsorption processes

can be adopted such as i) multi-stage cycle ii) cascading cycle

27

8x+amp

- - - - bullbullbull ~~jt ~~- bullbull i bullbull IIgtbullbull bullbull I~il~I bull-bullbullbullbull

lnP

~ ~

a2e a1 a1

bullbull1--T

Figure 18 Clapeyron diagram-of mass recovery cycle Source Farid [2009]

28

1i) Multi-stage cycle the basic idea of a multi-stage cycle is to perform the

desorption condensation processes at different temperaturepressure levels by using

the same working pair The pressure lift for multistage cycles were divided into two

or more stages As a result system can run by relatively low temperature heat source

Here for an example the working principle of a two-stage adsorption chiller is

discussed by Alam et al [2004] The following Duhring diagram (Figure 14) shows

that a conventional silica gel -water adsorption cycle cannot be operational with the

driving heat source temperature of 50 C if the heat sink is at 30 C

From the Figure 17 it is clear that the cycle allows reducing regeneration

temperature (pressure) lift of the adsorbent (Tdes - Tads) by dividing evaporating

temperature (pressure) lift (Tcon - Teva) into two smaller lifts Thus refrigerant (water

vapor) pressure rises into two consecutive steps from evaporating to condensation

level In order to achieve this objective an additional pair of adsorberldesorber heat

echangersto the conventional two-bed adsorption chiller is added

An advanced two-stage adsorption cycle consists of six heat exchangers namely a

condenser an evaporator two pairs of adsorbent bed heat exchangers as shown in

Figure 19 In an adsorption refrigeration system adsorbent beds are operated in a

cycle through the four thermodynamic states a) preheating b) desorption c)

precooling and d) adsorption These are denoted as cycle A cycle B cycle C and

cycle D respectively

To describe the cycle of the system it is assumed thatHXl and HX4 are in cooling

position at temperature Tc while HX2 and HX3 are in heating position at temperature

Thbull In the beginning of the cycle all valves are closed The desorbers (HXl and HX4)

are heated by hot water while the adsorbers (HX2 and HX3) are cooled by cooling

water During a short intermediate process no adsorptiondesorption occurs After this

short period valves 2 4 and 6 are opened to allow refrigerant to flow from HXl to

the condenser from the evaporator to HX2 and from HX4 to HX3 When

refrigeration concentrations in the adsorbers and desorbers are close to their

29

100Condenser pressure

)~ 737t tlOr~ lir ~ ~ t 4~24l

bull~f

1~8 234

~

]f~ 123~

o10 20 30 40 50 60 70 80

40

bullbullu30 L

4JI-

2~I-~p

fi20 -

1-ec~gt01)

10 bullbullCd3Cd

r

0

90~ilica Gel Temperature (Ye]

Figure 19 Conceptual P-T-x diagram for conventional and two stage

adsorption cycles (source Alam et al [2004])

30

et)c~- (JJ-~deg0o~u

5

~

Heatrejected

VIO

Condenser

V8----

Evaporator

r------- J~~ ~_~ IIIIII V4

VI

V2

~

i=1

J- -t=---~~~Cool~ngload

I

Figure 110 Schematic diagram of a two stage adsorption chiller

31

---_-bull_----_ - --

equilibrium level the flows of hot and cooling water are redirected by switching the

valves so that the desorber can change its mode into adsorber and ad sorber into

desorber The adsorptiondesorption process can be continued by changing the

direction of hot and cooling water flow

ii) Multibed Cascading cycle mass recovery process utilizes the pressure difference

between adsorber and desorber Therefore the bigger the difference of pressure the

more the refrigerant that could be moved from desorber to adsorber A multistage

mass recovery cycle proposed to increase the pressure difference was investigated by

Akahira et al [2004] In a cascading cycle ho~ and cooling water is used with

cascading flow from one desorber or adsorber to other desorber or adsorber where the

movement of refrigerant from desorber to ad sorber is accelerated

t iii) The schematic diagram of a two stage mass recovery cycle is shown in the figure lt

below The cycle consists of two single stage adsorption cycles ie four pairs of heat

exchangers namely an evaporator (EVAI)-arlsorber (HEXI) and a condenser

(CONNDI)-desorber (HEX2) EVA2-HEX3 COND2-HEX4 HEX2 connects HEX3

thro~gh valve V9 and HEXI connects HEX4 through valve VIO Upper part of mode

A of fig 1 (HEX 1-HEX2 COND 1 and EVA 1) is denoted as upper cycle as well as

lower part (HEX3 HEX4 COND2 and EVA2) is denoted as lower cycle Hot water

used in upper cycle flows into the lower cycle and the cooling water used in the lower

cycle flows into upper cycle

Upper part of the four-bed mass recovery cycle (HEXI HEX2 CONDI and EVAI)

is similar to single-stage cycle When HEXI and HEX2 are connected with a valve it

is a two-bed mass recovery cycle which consists three operational modes These four-

bed mass recovery cycles consist six operational modes Figure 110 shows half cycle

of four-bed mass recovery cycle that have only three operational modes The second

and fourth modes are mass recovery process Four-bed mass recovery cycle utilizes

the same principle of mass recovery of two-bed that is the pressure difference

between the adsorber and desorber Moreover in these processes the refrigerant mass

circulation will be higher than the conventional two-bed mass recovery cycle due to

32

--_ bull__-----~----------__-__ __ _- -

jiJ

~iAff~l

CONO

(b) ModcB

CONOl

CONOI

(a) ModeA

ChillcdwalCr In Chillcdwalcr Out f bull(c) IVlodcC

Figure 111 Schematic diagram of four bed adsorption refrigeration cascading

cycle of mass recovery (source Akahira et aL [2005])

33

the higher pressure difference in the present cycle with cooling water cascading on

condenser Figure 110 (a) presents the mode A where valves VI V4 V5 V8 V9

and VIO are closed in such a manner that EVAI-HEXI and EVA2-HEX3 are in

adsorption process and CONDI-HEX2 and COND2-HEX4 are in desorption process

Refrigerant (water) in evaporator is evaporated at the temperature (Tva) and thus

removing Qeva from the chilled water The evaporated vapor is adsorbed by adsorbent

(silica-gel bed) and cooling water circulated to the beds removes the adsorption heat

Qads The desorption-condensation process takes place at pressure (~ond) The

desorbers (HEX2 and HEX4) are heated upto the temperature (Tdes) by Qdes provided

by the driving heat source The resulting refrigerant vapor is cooled down to

temperature (~ond) in the condenser by the cooling water which removes the heat

Qcond When the refrigerant concentrations in the adsorber as well as in the de sorber

ltrre at near their equilibrium levels the cycle is continued by changing into mode B

In mode B adsorber (HEXI) and desorber (HEX2) of upper cycle are connected with

desorber (HEX3) and adsorber (HEX4) through the valves V9 and VIa respectively

In this mode no bed interact with the evaporator or condenser The pressures of

adsorber and desorber at the beginning of mode B are equal to those in mode A each

bed in mode A operates at different pressure levels

Mode C is a warm up process In this mode all valves are closed HEX and HEX3

are heated up by hot water HEX2 and HEX4 are cooled by cooling water When the

pressures of desorber and adsorber are nearly equal to the pressures of condenser and

evaporator respectively then valves between adsorbers and evaporators as well as

desorbers and condensers are opened to flow the refrigerant The later niode is

denoted as mode D

It is noted that the right side of the system is in desorption process and left side is ingt

adsorption process In next mode the mode E is simila~ as modeB Mode F is warm

up process as mode C The mode is the last process and after the mode it returns to

mode A

34--_bull_ bull_-----------------__- _

Solar energy was first investigated to use for automobile cooling by Pons and

Guilleminot [1986] and Zhang and Wang [2011] later by Saha et al [2000] and Alam

et al [2000a] for waste heat utilization Sokolov and Harsagal [1993] Vargas et at

[1996] Chen and Schouten [1998] Alam et al [2001] investigated optimal conditions

to optimize the system performances Besides in the developing or underdeveloped

countries where there is scarcity of electricity energy yet refrigerators or cold storages

are needed to preserve food and medicine solar driven adsorption cooling could be an

effective and vital alternative From this point of view Sakoda and Suzuki [1986] Li

and Wang [2002] investigated for simultaneous transport of heat and adsorbate and

the effect of collector parameters on th~ performance of closed type solar driven

adsorption cooling system Lumped parameter model was first exploited for two beds

adsorption cycle driven by solar heat where flat plate collector were used by Yang and

Sumanthy [2004]

Recently Clausse et at [2008] investigated the performances of a small adsorption

unit for residential air conditioning in summer and heating during the winter period

for the climatic condition of Orly France A similar study has been conducted by

Alam et at [2013a] for the performances of adsorption system based on the climatic

data of Tokyo Japan Both of the investigations are done by utilizing Compound

Parabolic Collector (CPC) solar panel

Utilizing the climatic conditions of Dhaka Bangladesh the performances of a basic

adsorption chiller coupld with CPC solar thermal collector Rouf et al [2011 2013]

is discussed in detail in the next chapters

In the study of solar adsorption cooling system solar thermal collectors are used One

of such collector is discussed in Clauss et al [2008] According to manufacturers

claim the reflector of the enhanced compound parabolic concentrator (CPC) collector

is made from the cylindrical high gloss rolled galvanically anodized pure aluminum

35

(1) Collector tray(2) Absorber

(3) Refledor(4) Solar safety glass

(5) S~ei91 SC91 (6)eilass holding strip

(7) Surface ~Iing joint (8) N~-g~dhcpcS~J1C rclicf ah

(9) Annular gap air vent

Figure 112 Artists viewof compound parabolic concentrator (CPC) collector

Source Alam et aJ [2013J

36

reflector concentrates the penetrating solar insolation onto the vertically installed

absorber The area of each collector is 2415 m2 The design insures that maximum

87 of diffuse part of the light can be absorbed The absorber of the collector is made

from the highly selective coated copper with ultrasonic welded heat transfer medium

pipe Artists view of compound parabolic concentrator (CPC) collector is given in

Figure 112

Under the perspective of developing countries to mitigate the basic need of food and

medicine in the rural region cold storage facilities are essential ill order to deal yvith

the shortage in available electrical energy an alternative energy source need to playa

vital role As the non-renewable energy such as the fossil fuels are limited and is not

compatible with the growing need of modem life renewable energy including wind

biomass and solar energy can provide a practical solution for the shortage of

conventional energy sources Nowadays waste heat driven adsorption cooling and

heating systems have gained considerable attention not only for utilization of waste

heat to produce useful cooling instead of releasing it to the ambient could playa vital

role in reduction of global warming and thermal pollution but also due to its ability to

be driven by low temperature heat source as well as for environmental aspect as)t

uses environment friendly refrigerants

Energy is the key sources towards the development of a country Recently renewable

energy has become a burning topic in Bangladesh as well as in the present world

Since Bangladesh is a tropical country solar heat based cooling system has a good

potential in this part of the world The present research is on the subject of exploring

mathematically

bull the prospect of solar energy to be used for i) air conditioning ii) refrigeration and iii)

ice making purpose

bull To minimize installation cost and the size of the collector device

37

~

f ~

bull The critical relationship between various parameters mathematically

Investigate the option to imply advanced level adsorption cooling systems to utilize

lower heat source

bull Investigate the prospect of utilizing the solar heat based cooling unit to exploit as a

source of hot water during the Winter season

Mathematical and logical programming language FORTRAN has been utilized to

simulate Solar and envir~nmental data for Bangladesh to study the feasibility of heat

driven cooling system

In Chapter 2 a basic single stage two bed adsorption cooling system fU11 by silica gel-

water pair with a direct solar coupling is investigated The investigation is carried out

for the climatic condition of Dhaka Bangladesh In this chapter a thorough

investigation has been carried out about the implementation of solar heat driven

adsorption cooling system for the typical hot humid days in Dhaka Also an yearly

analysis have been carried out in order to study the maximum number of collector and

optimum cycle time needed to run solar driven adsorption cooling system for the

climatic condition of Dhaka throughout the year in Chapter 3

Furthermore in Chapter 4 a storage tank is added with the system to enhance the

working hour of the system beyond the sunset time The utilization of the proposed

~hiller during Winter season as a source of hot water supply is discussed in Chapter 5

In chapter 6 conclusion of the thesis is enclosed

38

CHAPTER 2

Solar Adsorption Cooling Based on the Climatic Condition

ofDhaka

21 IntroductionThe improvement of energy efficiency is now generally viewed as the most important

option to reduce the negative impacts of the use of energy and of fossil fuels in the

near term In Bangladesh per capita energy consumption is one of the lowest (321

kWH) in the world (Electricity sector in Bangladesh Wikipedia [2014]) Bangladesh

has small reserves of oil and coal but very large natural gas resources Commercial

energy consWllption is mostly natural gas (around 66) followed by oil hydropower

and coal Bangladeshs installed electric generation capacity was 10289 MW in

January 2014 Only three-fourth of which is considered to be available Only 62 of

the population has access to electricity with a per capita availability of 321 kWH per

annum According to the report of 2011 79 natural gas wells are present in the 23

operational gas fields which produce over 2000 Millions of Cubic Feet of gas per Day

(MMCFD) It is well short of over 2500 MMCFD that is demanded a number which

is growing by around 7 each year In fact more than three quarters of the nations

commercial energy demand is being met by natural gas This sector caters for around

40 of the power plan~ feedstock 17 of industries 15 captive power 11 for

domestic and household usage another 11 for fertilizers 5 in compressed natural

gas (CNG) activities and 1 for commercial and agricultural uses Natural gas

reserves are expected to expire by 2020 The only coal mine of the country is

expected to dry up anywhere fmm 75 to 80 years after the start of their operations

Therefore it is necessary to reduce the dependency on the conventional power source

Bangladesh has 15 MW solar energy capacity through rural households and 19 MW

wind power in Kutubdia and Feni It is possible to lessen the consumption of

electricity for the air conditioningice making purpose if we can adopt an alternative

source such as waste and solar energy

39

-~--_ ---_ _ _

Sorption heating and air-conditioning is one possible way to reduce building fossil

fuel consumption and greenhouse gas emission in low-energy buildings (Clauss et al

[2008]) Moreover heat driven sorption heat pumpl refrigeration systems have drawn

considerable attention due to the lower environmental impact and large energy saving

potential as the system neither use ozone depleting gases nor the fossil fuel and

electricity as driving source (Akahira et ai [2005]) Adsorption refrigeration and air

conditioning cycles have drawn considerable attention due to its ability to be driven

by low temperature heat source and for its use of environment friendly refrigerants

Bangladesh as a tropical country has a greater potential of solar energy during the

hot summer and dry winter season According to RERC (Renewable Energy Research

Center University of Dhaka) 792W 1m 2 Iday averagemaximum insolation is available

in the month of April During April the summer starts and the sky is apparently clear

since the monsoon will start from the month of May

In this chapter the performance of an adsorption cooling system which is run by solar

thermal collector is analyzed mathematically Investigation is done on the collector

size to get optimum performance Also the performance of the chiller had been

studied fQr different cycle time for a typical hot day in April

22 System DescriptionA conventional two bed single stage basic adsorption chiller has be~n considered in

the present study A panel of solar thermal collectors has been utilized as heater As

for adsorbehtadsobate pair silica gel and water has been considered Silica gel-water

pair as adsorbentl adsorbate is well examined for air-conditioning process driven by

low temperature (less than 1000 C) heat source There are four thermodynamics steps

in the cycle namely (i) Pre-cooling (ii) AdsorptionEvaporation (iii) Pre-heating and

(iv) Desorption-condensation process No heat recovery or mass recovery process is

considered in the present study The adsorber (SElSE2) alternatively connected to

the solar collector to heat up the bed during preheating and desorption-condensation

process and to the cooling tower to cool down the bed during pre-cooling and

adsorption-evaporation process The heat transfer fluid from the solar thermal

40

I

collector goes to the desorber and returns the collector to gain heat from the collector

The valve between ~dsorber and evaporator and the valve between desorber and

condenser are closed during pre-coolinglpre-heating period While these are open

during adsorption-evaporation and desorption-condensation process The schematic of

the adsorption cooling with solar thermal collector panel is presented in Figure 21

The characteristics of adsorbentadsorbate (silica gel-water) are utilized to produc~

use(U1cooling effect run by solar powered adsorption chiller

23 FormulationThe system is similar to the system that Wasdeveloped for the SoCold project (Clauss

et al [2008]) where methanol and AC-35 activated carbon were used as working pair

for refrigeration The chiller configurations are similar as Saba et al [1995b] and the

computational model is same as Alam et al [2013a] In this study Silica gel and

water pair is used for air conditioninR as this compound is environment friendly and

the driving tempeature is between 500 to 80degC Though using MeOHlAC-35 pair

appears to be cost effective b~t water has lesser pressure and density compared with

methanol for the same operating conditions

The half cycle time is considered as 550s The pre-heating and pre-cooling time are

same and is 30s The pre-coolingpre-heating time is considered based on in view of

enhancement of the performance according to Miyazaki et at [2009] The

temperature pressure and concentration throughout the bed are assumed to be

uniform Thus based on these assumptions the energy balance of the adsorbent bed

duiing the desorption is represented by

d ~dt (W MCaM + WsiCSi + W5iqdc pJTd= Q5IM~i d + 11HwC pHW (THWouI - Tmvi~)(21)

The energy balance of the adsorbent bed during the adsorption is represented by

d ~( ~ dq a C dq a ( T )- WMCdM +WsiCSi +WsiqaCplw a =Q5tMSi --+Mi SiCpvw-- Tev - adt dt dt

+ mew Cpew (rew in ~ Tewaul ) (22)

41

-_ __-__-----__----__ __ ~

V4btgt~c- ()- ~0

VIO 00U-

5

VI

V2 ~ V8~ --~-_u Evaporator~

~-~-----l_-_t=-=-==-==tJ=c=oo=li=ng=l=oa=d[]

- ~~

bull t~

Figure 21 Schematic diagram of Solar cooling adsorption installation

42

(23)

Left hand side of both equations (21) and (22) stand for the sensible heating of

adsorbent material vapor inside adsorbent metal used in adsorbent bed The first

term of right hand side of equations (21) and (22) is adsorptiondesorption heat the

second term is for energy transport due to vapor transfer from evaporator to adsorbent

bed during adsorption-evaporation process and the third term is for energy outin

during adsorptiondesorption process

Based on the same assumptions the energy balance for the condenser is represented

by

d ~( ~ dqd dqd ( )- MCedM +MCcw ed =-LMs--+Mscpvw-- Ted -Tddt dt dt

+m c (T -T )edw pedw wedm wedout

Here left hand side of equation (23) represents sensible heat of materials used inr condenser heat exchanger and the condensed refrigerant inside condenser The first

term of right hand side is energy released by the vapor during condensation The

second term is for the energy transportation due to vapor transfer from bed to

condenser and third term is for energy release from condenser through the heat

transfer fluid

Similarly the energy balance for the evaporator is represented by

d r( ~ dq a dq d ( )-tMCeM +MCew e =-LMs--+MsCplw-- Te -Teddt dt dt

(24)

Here left hand side is as the previous cases corresponds to sensible heat of materials

used in evaporator heat exchanger and the amount of refrigerant inside evaporator

The first term of right hand side of equation (24) is for the energy extracted by

evaporated vapor during evaporation process due to the characteristics of latent heat

of vaporization the second term is for the energy transportation due to the transferred

condensed refrigerant from condenser to evaporator and third term is for energy

extraction from the inlet chilled water which is actually Hie cooling production

43

However the surface diffusivity is dependent on diffusion coefficient of the adsorbent

where the overall mass transfer coefficient function is k a dependent on adsorbents p

(silica gel) surface diffusivity Ds and particle diameter R p

(27)

(26)

(25)

The next equation is used to calculate the outlet temperature of the different water

loops

ToUl

=T+(Tjn -T)exp(-UAmCpJ

The adsorption rate for silica gel-water is dependent on a nonlinear function ksapandbullof difference between concentration of equilibrium state q and that of the present

state q

Dso and activation energy Eo

(28)D~= Dso exp(-Eo RT)

q = equilibrium concentration at temperature T which is calculated by

(29)

This is known as modified Freundich equation to provide a concise analytical

expression of experimental data

Here B = bo + bIT + b2T2 + bT3 A = ao + 0IT + a2T2 + 03T3 The saturation pressure is

calculated according to the Antonies equation where the experimental values of

coefficients Aj s and Bjs are given in table 21 The saturation pressure of water is

calculated by

Ps(T) = 13332 e [183-3820 1(1-461)] (21 0)

The cooling capacity is calculated by the equation

44

(213)

(212)

endojcyclelime

JmcwcpcW(Tcwin - Tcwou)atCOP = beginofcycletime

cycle endofcycletime

JmHWcpHW(THWoul -THWin)atbeginofcyclelime

endofcycletime

Jmcwcpcw (TCwin - Tcwou)atCOP = beginofcyclelime

sc endofcycletimeIn Acdtbeginofcyclelime

cycle

CA CC = m chill C IV f (rchillin - Tchill OUI it t cycle bullbull (211 )o

The cycle COP (coefficient of performance) and solar COP in a cycle (COPsJ are

calculated respectively by the equations

~~ In equation (213) I is the solar irradiance Acr is each projected area and n is the f

number of collector

Table 21 Numerical values of the coefficients ai s and bi s

coefficients value coefficients value

ao -15587 bo -65314

aj 015915 bl 072452E-Ol

a2 -050612E-03 b2 -023951 E-03

a3 053290E-06 b3 025493E-06

231 Solar System

Measured monthly average global insolation (solar irradiation) data for the station of

Dhaka has been used This data is supported by the Renewable Energy Research

Center University of Dhaka (Latitude 2373deg N Longitude90AOdeg E) The monthly

45

maximum and minimum average temperature (OC)at Dhaka station is supported by

Bangladesh Meteorological Department

A series of enhanced compound parabolic concentrator (CPC) collectors is attached

with the cooling unit as heater The geometry of the collector is described in Chapter

1 Heat transfer fluid (water) is assumed to enter the collectors parallel That is total

flow rates are divided equally and enter to each collector There are nine pipes in

each collector Heat transfer fluid enters the nine pipes serially That is the outflow of

the first pipe enters the second pipe outflow of the second pipe enters the third pipe

and so on the outflow of the ninth pipe of each collectors combine and enters to the

desorption bed Therefore nine equal subsections have been considered for each

collector Under these assumptions the energy balance for each collector can be

expressed as

[ UcpiAcpi Jwith Teriout= ~ri + (Teriin - ~ri )exp - mJere J

where

1= 1 S ( 7 (I - t sunrise ) Jmax zn ------t sunset - 1sunrise

(214)

(215)

(2 f6)

Here 17sc is the efficiency of the CPC as a function of the ambient temperature

The solar system considered during this mathematical study consist enhanced

compound parabolic concentrator (CPC) This study investigates the prospect of the

scheme for the global position of Bangladesh Therefore for the collection of the

solar insolation the model of the CPC considered here is same as the above mentioned

project The compound parabolic concentrator (CPC) developed by Solarfocus-GmbH

with area 2415 m 2with efficiency

(- J (- J2T -T T -T 17sc = 075 - 257 HW J am - 467 HW J am (manufacturersdata)

46

(217)

Where THW is the heat transfer fluid mean temperature

The set of differential equations appeared from (21) to (24) and (210) has been

solved by implicit finite difference approximation method The water vapor

concentration in a bed is represented in equation (26) Where the concentration q is a

nonlinear function of pressure and temperature It is almost unfeasible to divide the

concentration in terms of temperature for the present time and previous time Hence

to begin with the temperature for present s~ep (beginning of the first day) is based on

assumption The pressure and concentration is then calculated for the present step

based on this assumption of temperature Later gradually the consequent steps are

calculated based on the primary concentration with the help of the finite difference

approximation During this process the newly calculated temperature is checked with

the assumed temperature if the difference is not less than convergence criteria then a

new assumption is made Once the convergence criteria are fulfilled the process goes

on for the next time st~p The cycle is in unstable conditions in the beginning

however it reaches its cyclic steady state conditions after few cycles Therefore the

program is allowed to run from the transient to cyclic steady state The tolerance for

all the convergence criteria is 10-4 bull

The equations for desorber collector and reserve tank are completely dependent on

each other Therefore those equations are discretized by the finite difference

approximations which form a set of linear equations in terms of temperature and their

47

900800

f1E 700

~ 600c2 500+(U-o 400IIIs - 300_(U

0 200til

100o

bull

=Simulated data Ii 16042008 RERC

[l 06042009 RERC [JI

5 7 9 11 13 17 19

Day Time (Hoursl

Figure 22 Solar insolation simulated and measured for the month of

April

48

Table 22 Design and the operating conditions used in the simulation

Symbol Descriotion Value

Abed Adsorbent bed heat transfer area 2415m2

Ud Heat transfer coefficient of bed 172414W Im2K

WtmHeat exchanger tube weight (Cu) 512kg

Wfm Heat exchanger fin weight (AI) 6404kg

A Evaporator heat transfer area 191m2

Ubullbullbull Evaporator heat transfer coefficient 255754W m2 K

WM Evaporator heat exchanger tube weight (cu) 1245kg

A Condenser heat transfer area 373m2

Vee Condenser heat transfer coefficient 411523W m2 K

WM Condenser heat exchanger tube weight (cu) 2428kg

AcrEach collector area 2415m2

Wcp Weight of each pipe including absorber sheet O4913kg

Np Number of pipe in each collector 9

rilhotTotal mass flow rate to CPC panel or to desorber 13kg Is

feooCooling water flow rate to adsorber 13kg s

WS1Weight of silica gel in each bed 47kg

Wvar Liquid refrigerant inside evaporator initially 50kg

m IcondCold water flow rate to condenser 13kg Is

fchlll Chilled water flow rate O7kgls

Weobullbullr Condenser refrigerant inside condenser OOkg

Qst Heat of adsorption (silica gel bed) 281E + 06J I kg

Rgas Water gas constant 462E + 02J I kgK

pounda Activation energy 233pound + 06J kg

Dso Diffusion coefficient 254pound - 04m2 s

Rp Particle diameter (Silica gel) 035pound - 03m

T Cooling source temperature 30C

TchlllChilled water inlet temperature WC

c bull Specific heat of water (liquid phase) 418E + 03J I kgK

c Specific heat of water (vapor phase) 1 89 E +-03J kgK

Cebull Specific heat of copper (Cu ) 386J kgK

Co Specific heat of aluminum (AI) 905J kgK

C Specific heat of silica gel (Si ) 924J kgK

L Latent heat of vaporization (water) 26pound + 06J I kg

49

where i equals to the time difference between the maximum insolation and maximum

temperature of the day

outlets A Gaussian elimination method is exploited to solve the system of linear

equations In t~e beginning all initial conditions are set on ambient temperature

however concentrations have been taken slightly less than its sa~uration conditions

which allow the program run steadily

(218)

The ambient temperature is calculated as

T__Tmax + Tmin Tmax = - Tmin S (1f (Daytime - Sunrise tim e - i) )

am ~--~+-~-~ In ----------- 2 2 Daylength

Bangladesh is tropical country duration of monsoon is longer than dry winter and hot

humid summer Hence in order to study chiller performance a typical hot day from

April has been considered The average maximum temperature in April is reported as

34degC at day time The average of average maximum insolation in one day for seven

years is calculated as 771 W1m 2 bull Though the maximum insolation is reported in the1-

~ month of May but due to the rainy season it is not consistent The simulated and the~~

measured insolation data are attached in Figure 22 for a typical hot day in April The

measured and simulated data are in good agreement The set of differential equations

have been solved numerically The simulation was run for three consecutive warm

days to investigate the solar adsorption system ability to maintain thermal comfort

during heat waves All the operating conditions are available in Table 22 The system

comes to its steady state from the 3rd day All the results are given for day 3 The

investigation is done by increasing the number of collectors keeping the standard

cycle tim~ 550 to get optimum performance for cooling In addition different cycle

time with various collector number have also been considered in intension to

calculate optimum collector number for the considered chiller

Later effect of the operating conditions has been studied for optimum projected area

with optimum cycle time for maximum cooling capacity

50

~

i

241 Adsorption Unit Performances for Different Number of

CollectorsFor this study the chosen half cycle time is kept as 550s while different no of

collectors are considered The pre-heating and pre-cooling times are kept equal and

worth around 30s depending on the daytime as Miyazaki et al [2009] The

thermodynamic performances of the adsorption unit are reported in Figure 23 (a) (b)

and (c) for different number of collectors The cooling capacity of the adsorbent bed

averaged on one cycle is reported as increasing monotonically with the increase in

the number of the collector The cooling capacity is 1116 kW at peak hours when 22

collectors are in use

The coefficient of performance averaged in one cycle (COP cycle) is illustrated in

Figure 23 (b) which indicate that better performance is possible with the increase in

the number of collectors But there is no significant change in the performance at the

peak hours between 110 h to 150 h due to the change of the collector number A

similar behavior is visible for COPsc Moreover increase in the collector number even

decreases the COPsc (solar COP in a cycle) at the peak hours However at the

beginning and at the end of the day when there is less heat input through the collector

better COP cycle is noticeable for higher number of collectors Therefore it is

assumed that the COP cycle can be improved with lesser number of collectors if

cycle time is adjusted At the peak hours COP cycle is 045 whereas the maximum

COP cycle is achieved as 047 for 22 collectors at the sunset time At the peak hours

maximum COPsc is 027 (Figure 23 (c))

51

I

161412

bullbullbullbullbullS 10~U 8u~ 6

4

2

o

--14 collector--18 collectorso~to 22 collectors

bull bullbull -16 collectors=t -- 20 collectors

I

T 8 9 -10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

Figure 23 Performance ofthe chiller for different number of collectors (a)

Cooling capacity for different number of collectors

52

06

05

Gl 04]~ 03Ou 02

01

o

-14collectors ----16collectors 18coliectors- lt= 20collectors bullbullbullbullbullbull 22collectors

7 8 9 10 11 12 13 14 15 16 17 18 19

DayTIme (Hours)

(b) Coefficient of performance in a cycle for different number of collectors

03

025

02uIII0 0150u

01

005--14 collectors ----16 collectors

20 collectors

I _~_L L__

i

8 9 10 11 12 13 14 15Day Time (Hours)

16 17 18 19

(c) COPsc for different number of collectors

Figure 23 Performance of the chiller for different number of collectors

53

I

-

242 Adsorption Unit Performances for Different Cycle Time

During the above discussion it is understood that the cooling capacity and the COP

cycle increases w~en the collector number increases But the COP cycle does not

show any significant change when the collector number is increased from 14 to 22

during the peak hours of the day However the chiller can produce 1116 kW cooling

with 22 collectors Nevertheless there remains an optimum projected area (gross

collector area) based on the design and the operating conditions of the chiller Thus

for this study the chosen half cycle time is kept diverse while 182022 and 24 no of

collectors have been studied The pre-heating and pre-cooling times are kept equal

and worth around 30s depending on the daytime It is observed that with less number

of collectors it need longer cycle time to increase bed temperature as well as the

cooling capacity Besides there remain optimum cycle time for maximum cooling

capacity for a fixed projected area (Saha et ai [1995b] and Chua et ai [1999]) And

also for a very long cycle time the collector temperature rises beyond 100degC which is

not only inappropriate for the considered operating conditions but also hampers the

system performance Hence when the cycle time is increased beyond 800s that is

1000s while 22 collectors are in a panel the collector temperature is 100degC which is

not preferable for the present case as the heat transfer fluid in this assumption is

water Consequently in order to explore for optimum collector number 24 collectors

have been considered with cycle time 600s With 24 collectors cycle time 800s causes

a similar situation for the collector outlet As a result for 24 collectors optimum cycle

time is 600s The performance of the chiller with different collector numbers with

their optimum cycle time is produced in Figure 24 (a) (b) and (c) The cooling

capacity is maximum 1228 kW with collector number 24 But with collector number

22 it is 1199 kW There is no significant change in the cooling capacity when the

collector number differs from 22 to 24 (Figure 24 (araquo For 24 collectors and optimum

cycle time 600s maximum cooling capacity is 1228 kW The percentage increase in

cooling capacity is 2 where as the percentage increase in projected area from 22 to

24 is 9 Therefore increase in the projected area is not noteworthy Hence finally

22 collectors with optimum cycle time 800s is considered as an standard choice to run

the solar heat driven adsorption cooling system for the climatic condition of Dhaka

54

II

The COP cycle increases while the cycle time increases The increase of COP at

afternoon happens due to the inertia of collector materials (Figure 24 (b)) At

afternoon there is less heat input but there is relative higher cooling production due to

the inertia of materials of collector Therefore there is slow increase of COP

However it starts declining suddenly when the insolation is too low to heat up the

heat transfer fluid A sudden rise of cycle COP is observed at late afternoon This

happens due to the excessive long cycle time comparing with low insolation at

afternoon Due to the long cycle time at afternoon there were some cooling

production at the beginning of that cycle but there is a very less heat input in whole

cycle time If variation in cycle time is considered during different time of the whole

day then this behavior willnot be observed for solar COP in a cycle (COPsc) This

study will be conducted in the later section Almost same observation was found as

for the cycle COP At the peak hours the COP cycle is 05 and the COPsc is 03

Temperature evolutions of the collector outlet and the adsorbent bed are described in

Figure 24 (a) and (b) COP solarnet gets maximum value with longer cycle time

(1200s) and is equal to 029 (Figure 24 (d)) It is also observed that COP solarnet

increases with longer cycle time and less projected area Which indicate that cycle

time and the capacity of the chiller is responsible for COP solarnet instead of

projected area When 22 collectors are in use the collector outlet temperature is 95degC

with optimum cycle time 800s hence the bed temperature is 87degC

Cooling capacity is not the only parameter to study the system performance

Comfortable cooling effect to the end user is dependent on evaporator outlet

temperature Figure 26 illustrates evaporator outlet temperature for collector numbers

22 and 24 It can be noted that for 22 collectors with its optimum cycle time 800s

evaporator outlet temperature is lower than that of with 24 collectors with its optimum

cycle time Though the maximum temperature drop is observed for cycle time 1000s

this choice is discarded since with 1000s cycle time collector temperature is 100dege

Therefore with 22 collectors the choice of 800s cycle time is appropriate Thus the

chilled water outlet is 719degC which is enough to produce comfort to the end user

(Figure 25 (b)) Nevertheless it can be observed that higher bed temperature (Figure

24 (a)) results in lower temperature evaporator outlet (Figure 25 (a))

55

(a) Cooling capacity of adsorption unit for different collectors amp theiroptimum cycle time

19

6 i-n bull ~

1715

- - 18 collectors 1200s- 20 collectors 1000sbullbullbullbullbullbullbull 22 collectors 1000s

- = 18 collectors 1200s= 20 collectors 1000sbullbullbullbullbullbullbull 22 collectors 1000s

13Day Time (Hours)

119

bullbullbullbullbullbullbull 18 collectors 1000sbullbullbullbullbullbullbull 20 collectors 800s- 22 collectors 800s- - - - 24 collectors 600s

Day TIme (Hours)

8 9 10 11 12 13 14 15 16 17 -18 19

~bullbullbullbullbullbullbull 18 collectors 1000sbullbullbullbullbullbullbull 20 collectors 800s- 22 collectors SODs---- 24 collectors 600s

18

16

14

12

~ 10lII

Uu 8ctu

6

4

2

0

7

12

j 1~~ lt~

1 08 QI) U gtu 06

Q

0u04

02

0

7

(b) Coefficient of performance ina cycle of adsorption unit for differentcollectors amp their optimum cycle time

Figure 24 Solar adsorption cooling for different collectors amp their optimumcycle time

56

191715

ClCD CI 018 collector 1200s=== 20 collectors 1000sbullbullbullbullbullbullbull 22 collectors 1000s

13

DayTime (Hours)

10 11 12 13 14 15 16 17 18 19

9

--r bull ~ --_- ---~~-~-~--~~~~- ~ 1~

~ ~

18 collectors 12005 - 20 collectors 10005 bullbullbullbullbullbullbull 22 collectors 10005 ~

bullbull

-----_ _ --~ -----OI ---- bullbullbullbullbullbullbull 18 collectors 1000s

17 20 collectors 800s~ - 22 collectors 800s

---- 24 collector 600s

8

bullbullbullbullbull 18 collectors 10005bullbullbullbullbullbull 20collectors 8005- 22 collectors 8005

---~ 24 collectors 6005

7

a

03

04

01

u0 028

035

03

bullbull 02541c~ 02III0III 0150-0u 01

005

0

7

(c) Solar coefficient of performance in a cycle of adsorption unit for differentcollectors amp their optimum cycle time

DayTime (Hours)

(d) COP solarnet for different collectors amp their optimum cycle time

57

- collectoroutlet bullbullbullbull bullbullbull bed 1

12 13

Daynme (Hours)

(a) 24 collectors cycle time 600s

--collectoroutlet bullbullbullbullbullbullbull bed1 bed2

f f

~

~ 0 bull 0 Q

bull g -- ~

~

bull bull I bull

12 13

Day Time (Hours)

(b) 22 collectors cycle time 800s

Figure 25 Adsorbed temperature of the collector outlet andadsorbent bed

58

~gt =

1312

po 11-10

9

8

deg7

6

-22 collectors800s-24 collectors600s

- 22collectors1000s

11191195 12 1205 121 1215 122 1225 123 1235

Day Time (Hours)

Figure 26 Temperature histories of the evaporator outlet for different collectornumber and cycle timOeat peak hours

59

li

i ~

The temperature history of collector outlet and bed for cycle time 800s is presented

in Figure 25 (b) at the peak hours The driving temperature level for the silica gel-

water pair is around 80degC (Saba et al [1995b]) Bed temperature reaches 87degC when

cycle time 800s has been considered at the steady state Besides according to the

previous discussion longer cycle during the first part of the day and a shorter cycle

time at afternoon may provide better performance Hence several choices of the cycle

time are considered Figure 27 (a) (b) and (c) depict the temperature profile of

collector outlet and adsorptiondesorption b~d To achieve the required temperature

level (i) first uniform cycle time 800s then (ii) a variable cycle time such as starting

with 800s working till 140h of the day and then gradually decreasing with a rate of

10 seconds per cycle is considered and also (iii) another variable cycle starting with

550s working till 140h of the day and then gradually decreasing with a rate of 10

seconds per cycle is considered These choices of different cycles are discussed in

table 23 With both uniform and non-uniform cycle time 800s the collector outlet is

95degC while the desorber reaches to 87degC And with non-uniform cycle time starting

from 550s the collector outlet is 93degC and desorber bed is 85degC

Clearly there remain an optimum cycle time for maximum cooling capacity (Sana et

al [1995b] and Chua et al [1999]) the optimum cycle time for collector number 22

in April is 800s which is discussed in the earlier section It can be mentioned here

that the collector size can be reduced by taking longer cycle time for solar heat driven

adsorption cooling system (Alam et al [2013a]) However it may reduce cooling

capacity for taking excessive long cycle time Therefore it is essential to take both

driving source temperature as well as cooling capacity into consideration to select

optimum cycle time The comparative performances of all the three different choices

of the cycle time allocation are presented in Figure 28 (a) (b) and (c) Since for the

first part of the day that is from sunrise till 140h on behalf of both case (i) and (ii)

cycle time 800s is identical therefore CACC for these cases are similar during this

time period As designed for the second part of the day with longer cycle the chi~ler

takes few more minutes to c01-tinueworking compared to the shorter cycle However

in favor of case (iii) with shorter cycle to start with the chiller starts working late

60

compared to the first two cases and also stops working earlier (Figure 28 (a))

Although for all the three cases the maximum cooling capacity around 119 kW

which is achievable taking 22 collectors can be obtained

Conversely increase in the cycle time increases the COP values of the system (Saha

et al [1995b] and Chua et al [1999]) The maximum COP cycle 065 and COPsc 0316

is achievable by the proposed system when uniform 800s cycle time is considered at

late afternoon (Figure 28 (b) and (c)) At afternoon there is less heat input but there

is relative higher cooling production This happens due to the excessive long cycle

time comparing with low insolation at afternoon Due to the long cycle time at

afternoon there were some cooling production at the beginning of that cycle but there

is a very less heat input in whole cycle time When shorter cycle time is taken this

behavior was not observed for solar COP Almost same observation was found as for

the cycle COP The overall maximum COP cycle is 06and COPsc is 031 whilst case

(ii) is considered Since the optimum cycle time is 800s for collector number 22

CACC decreases when cycle time is less than 800s However the unsteady behavior

of the COP values at late afternoon can be corrected by taking shorter cycle time at

the sunset hours

Table 23 Design of cycle time

Case Starting Duration of Rate of Duration of Rate of

cycle Increase Increase decrease decrease

(i) 800s

(ii) 800s 140 - 185 h 20 scycle

(iii) 550s 55 - 140 h 20 scycle 140 - 185 h 20 scycle

61

110100

P 90-~ 80J10 70~ 60~ 50I-

4030

=collectoroutlet -bed 1 --bed2

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day TIme (Hours)

(a) 22 collectors with uniform cycle 800s-I

=collectoroutlet =--bed 1 ==bed 2~

110 100 ~

U 900- 80(1)gt0-jbull 70IIIbull(1)Q 60E(1) SO

4030

5 7 9 11 13 15Day Time (Hours)

17 19

(b) 22 collectors with non uniform cycle starting from 800s decreasing from

140h

Figure 27 Temperature history of different heat exchangers for 22collectors for different choices of cycle time

62

(c) 22 collectors nonuniformcycle starting from 55Osincreasing till 140h then

decreasing gt I11i

1917151311

DayTime (Hours)

97

=collectoroutlet ==-bed 1 --=-==bed2110

~ 100d1

f(

U 900-lt1l 80l+ 70(ll lt1lQ 60E 50

4030

5

Il

1917

uniform cycle 800s

9

c==starting with 550s increasing till14h thendecreasing

-starting with 800sdecreasing after 14

11 13 15

Day Time (Hours)

(a) Cyclic average cooling capacity

()fJ

~~ 13

121110

9~ 8 7

U 6u-laquo 5u4321 -0

7

Figure 28 Performance of solar adsorption cooling for 22 collectors withdifferent choices of cycle time

63

1

08

41 06ugtua0 04u

02

o

=uniform cycle800s-starting with 800sdecreasingafter 14h-starting with 550 increasingtill14h then decreasing

7 8 9 10 11 12 13 14 15 16 i7 18 19

Day Time (Hours)

(b) Coefficient of Performance in a cycle

=uniform cycle800s-starting with 800sdecreasingafter 14h-starting with 550sincreasingtil114h then decreasing

05

04

u 03VIa

0u 02

01

0

7 9 11 13

__ I

15 17 19Day Time (Hours)

(c) Coefficient of Performance of solar in a cycle

Figure 28 Performance of solar adsorption cooling for 22 collectors with

different choices of cycle time

64

~

(J

1ltlt

1lt ~

lt)lt

The chilled water outlet t~mperature histories at peak hours for different design of

cycle time have been depicted in Figure 29 (a) The fluctuation of the chilled water is

71 to 113degC at the pick hours when uniform 800s and non-uniform 800s cycle is

considered while it is 74 to 111degC for the case of non-uniform cycl~ 550s The

evaporator outlet at the late afternoon is also depicted in Figure 29 (b) In air

conditioning system CACC and COP are not the only measurement of performances

If those values are higher but there is relatively higher temperature chilled water

outlet then the systemmay not provide comfortable temperature to the end user With

uniform cycle time 800s chilled water outlet shows lower temperature than the other

cases for both at peak hours and at late afternoon Although the difference in the

chilled water temperature between the different cases of cycle time is negligible

Hence reviewing the performance and the chilled outlet non-uniform cycle time

starting with 800s till 140h and then decreasing till sunset at the rate of lOscycle

(case (ii)) could be a better choice to get maximum cooling capacity with a better

performance The outputs of different design of the cycle time are displayed in Table

24Table 24 performance of different desig~ of cycle time

Cycle Time (case) Collector Desorber Chilled CACC COPcycle COPscoutlet (OC) water (kW)caC) outlet

(OC)(i) Uniform 95 87 71 119 065 0315

800s(ii) Non- 95 87 71 119 057 0314

uniform800s

(iii)Non- 93 85 74 118 056 0311uniform550s

65

12115

11

U 105a-~ 101i 95~ 9E~ 85

8757

1195

-starting from 800sdecreasingfrom 14h-starting with 5505incr sing till14h then decreasin-uniform ~ycle8005

12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

r Co

figure 29 Evapo~ator Qutlet for different choice of cycle time at peakhours

66

Next the effect of the chilled water flow has been studied Different amount of chilled

water supply to the evaporator is considered in view to increase the cooling capacity

Thus three different choices of chilled water flow rates are considered The

comparative performances of the chiller due to this change are illustrated in Figure

211 (a) (b) and (c) A choice of 1kgs 07kgs and O4kgs chilled water supply to the

evaporator is considered For a less amount of chilled water supply results in a less

amount of evaporation of refrigerant As a result there is comparatively less amount ofI

adsorption and desorption Hence less cooling capacity is visible A similar behavior

is observed as for the cycle COP and COPsc In addition for too low supply of chilled

water and for an exceptionally longer cycle time there is an abnormal high value for

COP cycle at late afternoon On the other hand increase in the volume of the chilled

water flow from 07kgs to 10 kgs does not increase the volume of evaporation of the

refrigerant Hence the volumetric flow of chilled water at the rate of 07 kgs could be

considered as optimum amount of flow for the base run condition

A change is also observed in the temperature profile of the collector outlet and the

adsorption desorption beds due to the change in the volumetric flow of chilled water

Temperature of collector outlet and desorption bed decreases as the volumetric flow

of chilled water increases Increase in the chilled water flow results in increasing

evaporation consequently adsorption increases so does desorption Thus the cooling

capacity increases Hence more heat is utilized inside the desorption bed as a

consequence temperature of hot water outflow from desorber decreases For this

reason the temperature of collector outlet is lower compared to that of the case of

lower volumetric flow of chilled water The teflperature histories of the collector

outlet beds and evaporator outlets for different volumetric flow of chilled water are

presented in Figure 210 (a) (b) and 312 It has been observed that rate of volumetric

flow of chilled water (Fe) is inversely proportional to the temperature of collector

outlet (THOIout) and is directly proportional to evaporator outlet (TChiUouI) and cooling

capacity (CACC) which is supported by equations (211) and (2 12)Since COP cycle

is dependent on cycle time therefore for a considered cycle time if the chilled water

flow decreases temperature difference between chilledwater in and chilled water out

67

II

=collectoroutlet -bed 1 =bed 2120110

U 100o- 90 bullbullJ 80tu~ 70~ 60

~ 504030

5 7 9 11 13 15 17 19Day TIme (Hours)

(a) chilled water flow 03 kgls

fr

Ii ~

110

100 =collectoroutlet =bed1 -~~bed 2

- 90u0-C1l 80bullJ+J 70robullC1lQ 60EC1l 50I-

40

30

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

(b) chilled water flow 1 kgls

Figure 210 Temperature history different heat exchangers with 22 collectorscycle time 800s for

68

Day Time (Hours)

-__-~--~-

(a) CACC

-chilled flow03kgs=-chilled flow07kgs-chilled flow1kgs

__ ~_L_~_~_

9 10 11 12 13 14 15 16 17 18 19

chilledflow03 kgs =chilledflow 07kgs -chilled flow1kgs1

09

08

07

~ 06gtrr 058 04

03

02

01 -

o

13121110- 9

S 8 7-u 6uot 5u 4

3210

7 8

7 8 9 10 11 1213 14 15 16 17 18 19

Day rfme (Hours)

(b) COP cycle

Figure 211 Performance of solar adsorption cooling for 22 collectors cycletime 800s with different chilled water flow

69

19171513

Day Time (Hours)

(c) COPse

119

-chilled flow03kgs -chilled flow07kgs -chilled flow1kgs

04

035

03

025uQ 020v

015

01

005

0

7

151413

U 12~ 11

ltIJi 1010 9bull~ 8E 7 6

543

bullbullbullbullbullbullbull chilled water flow 1 kgs- chilled water flow 07 kgs

~ - chilled water flow 03 kgs bull 1o~o 000000000

00000deg(1

bull__ J 1 bull ~_J

i195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

Figure 212 Evaporator outlet for different amount of chilled water flow

70

increases at the same time temperature difference between collector in and collector

outlet increases

25 SummaryCooling capacity increases with the increase of the number of collectors Maximum

COP cycle is observed for 22 collectors an~ it is around 047 In order to improve the

system performance one can cOnsider longer cycle time However since there remains

optimum cycle time for maximum cooling capacity Saha et al [1995b] and Chua et

al [1999] the maximum cooling capacity is achieved for 800s cycle time and it is

119 kW when 22 collectors are in use The change in the cycle time does not have

much effect on the cycle COP at the beginning of the day but increases at the end of

the day A similar trend is observed for COPsc The optimum COPsc is 03 at the

peak hours

It is seen that collector temperature reaches to 952degC thus the bed temperature is

875degC with optimum projected area and cycle time The evaporator temperature

decreases to 71 degC which is enough to provide comfortable room temperature for an

en~ user Based on the above study it can be concluded that for the climatic condition

of Dhaka 22 collectors with 800s cycle time could be a better choice to run a solar

heat driven cooling system

The effects of some operating conditions have been mathematically investigated For

the climatic conditions of Dhaka for the month of April 22 collectors are considered

with different design of cycle time The optimum cycle time for collector number 22

is 800s If longer cycle time in the morning and in the afternoon and a comparatively

shorter cycle time at midday is considered the chiller can produce maximum cooling

with optimum COP Furthermore amount of chilled water is also a parameter for

cooling capacity Hence the effect of different volumetric flow of chilled water is

investigated With the optimum cycle time and 1kgs chilled water supply maximum

cooling capacity is 123 kW But cooling capacity is not the only measure to describe

system performance It the evaporator outlet temperature is lower than the other

options of the flow rate it will be more comfortable to the end user The minimum

71

~

c

bull~

~r f

~

evaporator outlet is 71degC for chilled water flow 07 kgso Hence chilled water flow

07 kgs is the best choice for the chiller The cooling capacity and also temperature of

chilled water outlet are proportional to the amount of chilled water supply to the

evaporator But temperature of collector outlet is inversely proportional to amount of

chilled water supply to the evaporator

The foremost drawback of the Solar heat driven adsorption cooling and heating

syste~ is its requirement of huge area and cost for the installation of the collector

panel and the cooling unit It is essential to study the consequence of the operating

conditions in need of reducing both installation cost and installation area Bangladesh

is a tropical country it observes mainly three seasons namely hot humid season

monsoon and dry winter Hence it is important to study the optimum performance of

the chiller round the year In Chapter 3 the study is conducted for some months of

different seasons of the year

72

CHAPTER 3

Yearly Analysis of the Solar Adsorption Cooling for the

Climatic Condition of Dhaka

31 Introduction

For the climatic condition of Dhaka it is pragmatic to install 22 collectors to gain

driving heat with optimum cycle time 800s in order to run the solar heat driven

cooling and heating system where silica gel- water pair is considered as the

adsorbentadsorbate pair In the previous chapter it was discussed that for a typical

day in the month of April the available solar insolation can raise the bed temperature

to 85degC at 12h with the base run condition given inTable 22 But the solar insolation

data and the temperature varies with different seasons of tile year Therefore it is

indispensable to study the prospect of the solar heat driven cooling unit for the

climatic condition of Dhaka round the year The feasibility of installation of the solar

heat driven environment friendly cooling system depends on the accurate choice of

the number of collectors and the operating conditions

32 Result and DiscussionIn Chapter 2 it was observed that based on the available solar insolation ill the month

of April 22 collectors each of area 2415m2 has been taken into consideration Since

available solar insolation differs with different seasons of the year a standard number

of collectors should be chosen to be installed In the present chapter the program is

allowed to run with 22 collectors and optimum cycle time 800s for several months

during hot summer season and dry winter season First the driving temperature level

which is reported as around 80degC for silica-gel water pair (Saha et al [1995b] and

Chua et al [1999] is checked then the performances has been checked For the present

case 22 collectors is the best option for which the performances do not affect too

much and driving heat source temperature level can be controlled by adjusting the

cycle time Figure 31 presents a comparison between simulated and measured data

73

900

800 I-NE 700bullS 600-c 5000PIV 400 bullbull0IIIC 300bullbull ~sjmulated dataIV 2000 bull 27032004 RERC III

100 A 28032005 RERCa

5 7 9 11 13 15 17 19Day Time (Hoursl

III11I

Figure 31 Solar insolation data for several months of the year (a) March

I I

19171513119

900800

E700 ~~ ~ ~

c 600 EJ ~

1~~ ~~ c 300 I d ~ ~

12 j bull =Simulated data 0 0 o 200 A 1 [] III I A 16042008 RERC

100 ~ [II 06042009 RERC bull Gl~ 0 A ~o - I

5 7

Day Time (Hours)

Figure 31 Solar insolation data for several months of the year (b) April

74- _- - _~----~~------

800700-NS 600

~- 500c0- 400to-0 300IIIC

- 200nI0V) 100

a ~~ 5 7

II

15 17 19

lIII

Figure 31 Solar insolation data for several months of the year (c) Ju~e

simulated data[J 25082003 RERCbull 27082006 RERC

600

~ 500Ebullbullbull$- 400c0 300ro-CIIIc 200-roa 100III

0

5 7 9 11 13 15 17 19

Day Time (Hours)

Figure 31 Solar insolation data for several months of the year (d) August

75

Figure 31 Solar insolation data for several months of the year (e) October

600

500-NE--= 400A-t

0~ 300 A nl0ent

200 bullnl A bull0VI =sjmulate~ata100

A bull 06102006 RERCamp

0 0710 007

5 7 9 11 13 15 17 19Day Time (Hours)

600[J

1500 ~

~ 400 )- V g P bull fl~ 300 _ If ~Of ~III i bull 0c 200 - IJ Q

~ I if simulated data a 100 1

1

- l 0 3i122E04RERC bull bullf G bull 08122006 RERC Do Lbull_L____i__ L J bullbull L__ -L1-B- __

5 9 11 13 15 17 19Day Time (Hours)

Figure 31 Solar insolation data for several months of the year (t) December

76

of insolation for few months that is of March April June August October and

December It is seen that the simulated model for the insolation shows good

agreement with measured data for March April and December The deviation seen in

the simulated and measured data for June August and October is due to cloud

coverage since monsoon has already started from the end of May The simulation of

the insolation is done according to a sine function (equation (215))The climatic data

for the proposed months have been illustrated in table 31

First the driving source temperature needs to be adjusted and then the performance

can be analyzed The driving heat that is produced to the chiller comes from the

collector outlet The heat absorbed by the collector material depends both on the

available insolation and the ambient temperature since in the beginning of the day

collector input and the cooling load is the water in ambient temperature

Consequently for different seasons available insolation and maximum minimum

temper~ture varies According to Figure 31 the available solar insolation in the

month of March and April are moderate and is approximately 700-800 Wm2 which

gradually increases but during the later months due to monsoon measured average

insolation is less than that of April However it starts decreasing from Septemoer and

in the month of December it is approximately 500 Wm2

Based on the analysis of Chapter 2 a standard of 22 CPC collectors has been chosen to

be installed in order to produce maximum cooling with the proposed chiller with the

base run conditions The climatic data was taken for the month of April Figure 32 (a)

illustrates the temperature histories of the collector outlet and bed temperature for ~he

month of March It is seen that the bed temperatures are within the range of the -

temperature of driving temperature that is around 80degC It could be also observed

that the half cycle time (heating or cooling) 800s is required for March which is

similar as for April However with the change of the climatic datathere is change in

the system performance The Figure 32 (b) shows that for the same number of

collectors and cycle time the bed temperature reaches to 95degC Hence with cycle time

800s the bed temperature is at the desirable level for the rest of the months (Figure 32

(c)-(f)) While the insolation is incr~asing during the next month August but due to

77

toe rainy season it is not consistent and the average insolation data appears to be less

than that of the month of April However this study has been conducted considering

optimum projected area and cycle time considered in the previous chapter for the

typIcal hot day of the month of April Thus the highest collector temperature is

observed to be95degC in April and the lowest temperature is 65degC in December

Table 31 Climatic data for several months

Month Average of average Maximum Minimum

maximum temperature temperature

insolation day- degC degC

HVm2(Average on 7

years)

March 712 300 188

April 771 340 240

June 568 314 258

August 546 325 266

October 536 312 250

December 501 259 164

Figure 33 shows the performance of the chiller for different months It can be seen

that cooling capacities varies for different months It is also seen that cyclic ayerage

cooling capacity (CACC) of April is higher than that of other months This is due to

the higher solar insolation in April The cooling capacity in December is minimum

and it is 66 kW Thus with the proposed system for the climatic condition of Dhaka

the maximum cooling capacity is 119 kW during April with 22 collectors And the

minimum cooling capacity during December is 66 kW It is also observed that there

is a very little variation in the values of COP cycle for different months at the peak

hours But there is little variation at late afternoon The COP cycle is steady However

for all cases COP cycle increases steadilyup at afternoon The maximum 0316 COP

78

-__-------------------------__-_-

l

sc is achievable with the proposed system whereas the average COP cycle at the peak

hours is 05 for the climatic condition of Dhaka

In air conditioning system CACC and COP are not the only measurement of

performances If those values are higher but there is relatively higher temperature

chilled water outlet then the system may not provide comfortable temperature to the

end user From this context the chilled water outlet temperatures for different months

are presented in Figure 34 It is noticeable that for higher temperature hot water

supply to the desorber results in lower temperature evaporator outlet For the month of

December with 22 collectors cycle time 800s bed temperature reaches 65degC which

results in O4degCevaporator outlet On theother hand in April bed temperature is 95degC

and hence the evaporator outlet is 73degC It is well ~own that less the fluctuation of

chilled water temperature better the performance of the system However the chilled

water outlet temperature can be controlled by adjusting the flow rate of chilled water

which is discussed in the previous chapter

79

~

--coliectoroutlet bullbullbullbullbullbullbull bed1

115 12Day Time (Hours)

125

bed 2

13

i (a) March

bed 2

~bull I

o

-~

-- collector outlet bullbullbullbullbullbullbull bed 1

85

~[35 LL

115

105 -

G 95o-

1J

(b) April

Figure 32 Temperature profile of the heat exchangers for different monthswith 22 collectors cycle time 800s

80

-collectoroutlet bullbullbullbullbullbullbullbed1 bed2

10090-u 800bull

OJl 70J+Ill 60GIQ

EGI 50I-

40

30

bull ~- 11 115 12

Day Time (Hours)

i ~

--J~ -

125 13 I I

I

(c) June

1312512Day Time (Hours)

(d) August

115

_____ ~I _ bull i bull -- __

--collector outlet bullbullbullbullbullbullbull bed1 bed2

10090 --u 800-~

lo 70s+IVlo 60~Q

E 50~1-

4030

11

Figure 32 Temperature profile of the heat exchangers for different months with22 collectors cycle time 800s

81

--collector outlet bullbullbullbullbullbullbull bed1 bed210090-u 800-QJ- 70J

10- 60QJa-S 50QJl-

40

3011 115 12

Day Time (Hours)

(e) October

I

-J ii

125

J13

(f) December

125 13

82

_-----------------------------------

Figure 33 Comparative Performances of the chiller for different months (a)CACC

83

bullbullbull -Junebullbullbullbullbullbullbull Decem ber

--April--October

Day Time (Hours)

10 11 12 13 14 15 16 17 18 19

bullbull

bullbulltbullbullbullo__ 1-_1 _I __ L_ bull J _I _ bullbull _L __

9

bullbullbullbull 11 Marchbullbullbull -August

87

16151413121110987654321a

-S0-UUctu

DayTime (Hours)

191817161514

---April----Augustbullbullbullbullbullbullbull December

131210 11

(b) COPcycle

9

bullbullbullbullbullbullbull March--~-June---October

1

08QI 06Ugt-uQ

0 04u

02

07 8

-J __L- __--L- __ _____ --

Marchampgt=June

=-October

---April===August000 bullbull 0 December

17 18 191614 151310 11 1298

0605

04tv

lVIQ 030u

02

01

0

7

Day Time (Hours)

(c) COPsc

Figure 33 Comparative Performances ofthe chiller for different months

84

85

(b) April

1

Day Time (Hours)

7 l-_---__ ~__ ~ __ ~ __ ~__ ~_~__

1195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

(a) March

12

a- II-evaporator outlet

0-C1I~ 10lbullnl~C1I 9cEC1I 8bull

1194 1199 1204 1209 1214 1219 1224 1229 1234 1239

12115

a- i1e 105C1I3 10~ 95~X 9E 85~ 8

757

Figure 34 Chilled water outlet temperature for different month and cycle time800s

Day Time (Hours)

(c) June

-evaporator outlet

1199 1204 1209 1214 1219 1224 1229 1234 1239

13

125

12115

uo-ltIIbull~ 11bullltIIc 105E

~ 1095

9

1194

-evaporator outlet

13513

G 125o~ 12bullE 11510

~ 11E 105 -

10

959 1- I

1195 12 1205 121 1215 122 1225 123 1235 124

DayTime (Hours)

(d) August

86

r

135- evaporator outlet

P 125-

951205 121 1215 122 1225 123 1235 124 1245 125 1255

Day Time (Hours)

(e) October

14-evaporator outlet

G 13~Qj~J 12III ~QjQ

EQj 11I-

10

1184 1189

___ L __ J__ ~_~ __ J __ -L

1194 1199 1204 1209 1214 1219 1224 1229

Day Time (Hours)

(1) December

87

_----- --------------------------------~-_---

33 Summary

The objective of the chapter is to select an appropriate number of collectors to be

installed in order to make the most of the utilization of solar heat driven adsorption

cooling system which is run by silica gel-water pair under the operating conditions

given in table 22 round the whole year It can be concluded that 22 collectors could

be an appropriate choice for the months of summer and autumn season While for the

winter season it is not enough to produce the standard amount of cooling such as 9

kW In order to increase the cooling capacity we need to increase either collector

number or cyCle time Although too much long cycle time may affect the system

performance Also it is noticeable that the COP values are not stable at late afternoon

due to the longer cycle time and lower heat input therefore shorter cycle should be

considered for late afternoon

In the next chapter in view to improve the performance of the proposed chiller a heat

storage namely an insulated tank holding water is added with the system and the

performance of the chiller will be studied

88

---__----------------------------_ -__ _

tt~r~~~~

~

i ~ t

+ bull

1

CHAPTER 4

Implementation of Heat Storage with Solar Adsorption

Cooling Enhancement of System Performance

41 Introduction

According to Chapter 2 in the month of April22 collectors with optimum cycle time

800s are sufficient to run the solar cooling unit However it had been concluded in

Chapter 3 that the optimum cycle time and performance varies with various seasons

of the year To achieve better performance and to increase system efficiency we need

to critically investigate the operating conditions

The number of collectors had been decided based on the study discuss~d in Chapter 2

and Chapter 3 A case study had been conducted to examine the performance of solar

heat driven adsorption cooling unit based on the climatic condition of Dhaka The

program was allowed to run with different amount of supply of chiiled water to the

evaporator and taking variable cycle time at different time period during the whole

day in Chapter 3 The rest of the operating conditions are same as the previously

discussed two chapters and in Table 22 However according to all these studies it is

concluded that solar heat driven cooling system can provide required cooling to cool

down a standard size of 100m2 room But it is effective only during the day time

while solar insolation is available It is necessary to consider an alternate backup to

keep the chiller active at least for few more hours when solar insolation is not

available Nowadays there are a number of sorption heat pumps for solar coohng

available in the global market (Jakob [2013]) These units are run by different choices

of adsorbentadsorbate pairs Although the market price of these units are very high

and the driving temperature varies between 70deg- 90degC Bangladesh is a d~veloping

country in the present study silica gel-water pair has been considered as

adsorbentadsorbate pair not only for their large scale availability and low price but

also their driving temperature is Soo-80degC

89

___________ _ bull ~ bull 4lt

~ or

In this chapter in anticipation to increase working hour and also the performance of

the solar heat driven adsorption cooling system a storage tank is added with the

outdoor unit This storage tank considered to beinsulated will hold hot water which

when needed will be utilized to run the chiller at times when solar insolation is absent

or is not enough to supply heat A number of investigations are discussed in this

section (i) Two different designs have been considered for the connection between

the collector and desorption bed with the storage tank The performance of both

designs and their comparison has been discussed (ii) Different choices of cycle times

have been considered to study the performance of the solar adsorption cooling system

supported by reserve tank

In the present study a series of solar panel is connected with conventional single stage

two-bed basic adsorption cycle as it is mentioned in Chapter 2 A storage tank

holding water is connected with the solar panel and alternately to the two adsorption

beds Two different designs have been considered to attach the reserve tank to the

solar adsorption chiller Schematic of adsorption solar cooling system with storage

tank according to the first design is given in Figure 41 The desorberadsorber heat

exchangers (SE2 SEl Figure 41) are alternately connected to the solar panel and

condenser during the pre-heating and desorptioncondensation processes and to the

cooling tower and evaporator during the pre-cooling and adsorptionevaporation

processes respectively The heat transfer fluid (water) is heated in the solar thermal

collector and transported to the desorber Desorber gains heat and the outflow of this

hot water from the desorber then collected in the storage tank Storage tank supplies

water to the collector from it lower level where its temperature is comparatively

cooler than the upper water level This water supply gains heat in the collector arid

complete the cycle An artistic view of desorptioncondensation mode of SE2 which

is filled up by the sorption material SE (silica gel) is presented in Figure 42 The

working principle of the present system is same as the working principle discussed in

Chapter 2

90

However according to the second design the collector supplies heat through the heat

transfer fluid (water) to the reserve tarue Reserve tank then supplies water to the

desorber from its upper level which is comparatively hot than the lower level water

Desorber gains heat and outflow of the desorber is supplied tq the collector again The

schematic of the second design is illustrated in Figure 43 The rest of the working

principal is same as design 1 The hot water supply chain during both design 1 and 2

is discussed in Table 41 The operating conditions are followed as Ttable 22

As discussed in Chapter 2 that considering variable cycle time during different day

time enhances the system performance four different choices of allocation of cycle

time have also been considered Firstly uniform cycle of 1400s secondly variable

cycle time starting from 800s and different choices have also been considered One of

the choice is increasing cycle with a rate of 20scycle starting from 800s till the end of

the working hour of the system Another choice is increasing of the cycle time at the

rate of20scycle till 140h and then decreasing for the rest of the time at the same rate

And lastly increasing and decreasing the cycle time at the rate of 20scycle starting

from 800s Increasing cycle time till sunset and then decreasing These four choices

are listed in Table 42 The specification of the storage tank is given in Table 43

Table 41 Design of the solar adsorption cooling sy~tem with storage tank

j bull

1

Designl

Design 2

Collector-gt Desorber-gt Storage tank-gt Collector

Collector-gt Storage tank-gt Desorber-gt Collector

Table 42 Choices of the cycle time

Choice Uniform Nonuniform Starting Rate of Increasing Decreasingcycle cycle cycle change till till

time

1 1 - 1400s - -End of the

2 - 1 800s 20scycle working -hour

End of the3 - 1 800s 20scvcle 140h workin hour

End of the4 - 1 800s 20scycle 185h workin hour

91

V5VIO

SE2

V8

Evaporator

[ __ dere~~~d~I ~ I

1_ - - - -- - - - L - - - - - - -

I ~~-~~-~~=~~-~ II ( Condenser I)

III V4

III

IIIIIII1IIIf

- - - - - - - -1_-_1__-_-_-__-_-_-_Dcooling

loadO

V2

VI

V3

tt

J

i

Figure 41 Schematic diagram of solar adsorption cooling run by storage tank

design 1

bull

12

1

v1

HollVaer ollilel

if Cooling load

CondQnCQf

S IGlcqe tank

bullbull Pw ~IL E~apolatof-=~=~~==D- 4 -4--

design 1

92

I]I]

~ V4III

IfI]I]

I

IVlO

-Evaporator

_ _W _ _ _ __ __r - - -__C_

Condenser

IIIIIII

lXt=-It2 I

I ----- -r------J - 1 r P- -r

==~=====_---figti Cnn~irDgloaJl1

IVbull ~

I

i

f t

if~Iii~~

~ t~ ~

design 2

93

_I

(41)

Table 43 Design of reserve tank

Symbol Description Value

LHW Dimension of the tank 13 mWrv Volume of the tank 133 m3

Wwt Weight of water in reserve tank W tvxl000-10 kgVtoss Reserve tank heat transfer loss coefficient 05 WmLKASrt Reserve tank outer surface area 6x11lml

Wtm Reserve tank metal weight AwtxO005x2700kg

The energy balance equations of the adsorption desorption beds condenser and

evaporator are same as equations 2 i to 26 Each collector has nine pipes water

enters through the first pipe and the outlet of the first pipe enters into the next pipe

thus the outlet of the ninth pipe of each collector combines together and enters into

the desorber Hence the temperature of the heat transfer fluid in each pipe is

calculated separately for all the collectors Th~ energy qalance of each collector can

be expressed asdT -

W ~=rA +mj Cj(T -T )+(l-r)u A (ram-r )CfJ1 dt 1 Cr1 cr crlm CrIout asAr crl

I

1

T =T +(T -T)EXP(UcpA Ifnj Cj)crlout crl crlln crl Cpl cr

where i=1 9 r is either 1 or 0 depending on daytime or nighttime

The energy balanc~ for te reserve tank can be expressed as

-ffw C +w C L =m C (r -T )+U AS(T -T)dt l~tm tm wt wJL wt w w bed out wt loss rI am wi

(42)

(43)

wher~ T =T Jcrlout crz+ In T == T and T = T

9 b d 1 bedoul wlincr oul e m (44)

And

Tcr 1in = Twt bull

in case of design 1

94

(45)

Although for design 2 the energy balanpe for the reserve tank can be expressed as

-ffw c + W C r = m C (T - T )+ U AS (T - T ~ (46)dt ~ tm tm wt w wt w w crOfll wt Iloss rl am wI J

The pressure and concentration in each bed is calculated as it is in Chapter 2 and by

equation (27) The performances are calculated by equations (28) to (210) The

COPsolarnet is calculated as

(48)

(47)

T =T Tbd =Ttcr 9 out wi in e In w

TbedoUI = Tcrin

fhiler stop lime bull

COP = kunsellme mchillCchl(Thln - ThllOUl)dtsola net tlltstop time

nA Idtunrlsettme cr

First the driving source temperature for design 1 has been checked for different

collector numb~r and cycle time The driving temperature of the adsorption cooling

system with silica gel - water pair is around 80degC Following the discussion of

Chapter 2 and Chapter 3 for the climatic condition of Dhaka Bangladesh 22

collectors each of area 2415 m2 with cycle time 800s is optimum to raise sufficient

bed temperature to run the silica gel-water adsorption cooling system with direct

coupling of solar thermal collector Howev~r the present system needs to first heat up

the water of the reserve tank and then the collector is able to provide the system

enough temperature to run the cooling unit Therefore it is observed that it needs more

collectors to heat up the bed than that of adsorption cooling system with direct solar

coupling Hence 20 22 24 26 28 and 30 no of collectors have been considered for

the present case to investigate the optimum system performance

where T = T bull 1 crlout cr+ m

and

bull

~

The temperature histories of collector outlet bed and reserve tank for different

number of collectors and cycle times to begin with have been illustrated in Figure 44

(a) (b) (c) and (d) It needs at least 22 collectors with cycle time 1400s to obtain

required ampunt of driving temperature It can be also seen that the lesser number of

collectors the lower the driving heat source temperature Increasing cycle time does

95

- __--------__-----__-----------------

not show any significant increase in bed temperature However less number of

collectors may be used if the size of the reserve tank is less than that of the present

case Or else it is also observed that the driving temperature may rise with less

number of collectors along with higher cycle time however it may affect the system

performance It can also be noted that the bed temperature fluctuate in the beginning

of the 1st day It happens due to the initial concentration At the beginning both beds

are assumed saturated with water vapor at ambient temperature therefore both beds

desorb vapor in the beginning However after few cycles the system reaches its

cyclic steady conditions Therefore performances of the system after few cycles do

not have any effect on initial conditions

In order to come to the steady state the system is allowed to run for few consecutive

days With 1400s cycle time the system comes to its steady state fro~ the second day

The chiller works till 218 h while the temperature difference between the heat so~ce

(heat input) and heat sink (ambient temperature) is 25degC The collector adsorption

desorption beds and all other units of the chiller exchange heat with the outer

environment during night time and looses temperature and come to the ambient

temperature in the next morning The reserve tank is insulated hence the tank water

temperature is 45degC at the beginning of the second day At 55h the valve between the

reserye tank and the collector is reopened Hot water from the reserve tank travels

through the collector and the bed looses temperature returns to the tank Thus when

all the heat exchangers gain the driving temperature the chiller starts working at 86 h

in the morning since it does not need to heat up the tank water this time

The collector temperature reaches to 7745degC while the bed temperature is 771degC

when cycle time is 1400s at the steady state with 22 collectors While the collector

temperature is almost 8945degC and hence bed temperature is 8922degC with cycle time

1400s and increasing collector number to 30 It is also observed that the bed

temperature and the cooling capacity does not show any significant increase due to

the increase of cycle time Rather for avery long cycle time though there is a very

little increase in the collector outlet temperature there exist a negative effect on the

96

-collectoroutlet=bed 1 -bed 2 tank~

i~

85

75-u0 65-lt1Jbulllbullbullbull 55rolt1Jae 45lt1Jt-

35

255 7 9 11 13 15 17 19 21 23

Day Time (Hours)(a) 20 collectors cycle time 1400s

23

21

~j

19171513

I Jl I I

1197

lt===Dcollectoroutlet 7=--=00 bed 1 -bed 2 tank

---L-~ ____~_~ __ ~ I __J_ __ ~ __-

9085r 801

u 750 70-lt1J 65bulll 60bullbullbullro 55bulllt1J 50C-E 45lt1JI- 40

353025

5

Day Time (Hoursl

Figure 44 Temperature histories of collector outlet bed and reserve tank fordifferent number of collectors and cycle time on the first day design 1

97

--__----------------------------

(c) 22 collectors cycle time 1800s

7 9 11 13 15 17 19 21 23 25Day Time (Hours)

tank-COllector autlet908580

G 750 70-OJ 65bulls 60bull(I 55bullOJQ 50E 45OJl- 40

353025

5

=collectoroutlet ---bed1 -bed 2 tank

lJ~~(J~ lOS~~

1 ~ 100~- 95~

~ 90r u 85

0 80-~ 75 70Jbullbullbull 65Illbull 60~Q 55E 50~ 45l-

40353025

5 7 9 11 13 15 17 19 21

I

23

Day Time (Hours)

(d) 30 collectors cycle time 1400s

Figure 44 Temperature histories of collector outlet bed and reserve tank

for different number of collectors and cycle time on the first day design 1

98

cooling capacity The temperature histories of the c911ector bed and the tank for three

consecutive days f~r botn collector number 22 and 30 with cycle time 1400s have

been presented in Figure 45

At the steady state in the beginning of the day the instability of the bed temperature is

absent This time temperature of the tank water is higher than the ambient temperature

and is supplied to the collector It increases the temperature of the collector and the

desorber The ~utlet of the desorber returns to the tank The temperature of the outlet

of the desorber is lower than that of the tank water For some time in the morning

when enough insolation is not available the tank water looses temperature This

behavior is visible in Figure 46

At the steady state with 22 collectors the chiller starts working one hour earlier than

the 1st day and produces maximum 81 kW cooling at 156h and the duration of the

working hour on one day of the chiller is around 135 hours when cycle time is 1400s

CACC increases monotonically with the increase of collector number And with the

optimum collector number 30 and optimum cycle time 1400s maximum CACC is 93

kW at 156 h it takes 8 more collectors in order to increase 12 kW cooling capacity

Which implies that for 15 increase in cooling capacity it asks for 36 increase in

the projeCted area The cyclic average cooling capacity CACC and the performance

of the chiller are presented in Figure 47 (a) (b) and (c) The maximum COP cycle

reaches after sunset and it is 06 while the COPsolarnet is maximum 026 at the end

of the working hour of the chiller At the sunset hours there is no heat input but still

the chiller -is working therefore shows a very high solar COP for one cycle

Maximum cooling capacity is noticed for optimum cycle time 800s while maximum

COP occurs for longer cycle time A comparative figure for CACC is produced in

Figure 48 (a) for chiller with direct solar coupling and with storage tank design 1

with their optimum projected area and cycle time respectively It is observed in

Chapter 2 that the optimum projected area with direct solar coupling is 22 projected

areas and cycle time is 800s where as it is 30 projected area and 1400s for chiller with

storage tank design 1 With direct solar coupling maximum CACC is 119 kW

99

--------- _ -- -__-

=collectoroutlet =bed 1 =bed 2 =tank

80-u 700-lt11~ 60J+-(U

50lt11aE 40lt11I-

30

5

DayTIme (Hours)

=collec[oroutlet ~bed 1 ==bed 2 == tank

Figure 45 Temperature histories of different heat transfer units for three

consecutive days for design 1

100

25

23

21

-

21

1911 13 15 17Day Time (Hours)

11 13 15 17 19

Da~Time (Hours)

9

7

~collectoroutlet =bed 1 ~bed 2 tank

-collectoroutlet === bed 1 ~bed 2 ~al1k

90858075-u 700-Q) 65-s 60+ro 55-Q)

Q 50EGJ 45bullbullbull 40

353025

5

~fj~

~

95lt

1 90t 85

80u 750- 70lt1J 65J+ 60((

lt1J 55Q

E 50lt1J 45~

40353025

5

Figure 46 Temperature histories of the heat transfer units at steady state withdifferent collector and cycle time design 1

101

-collector outlet =bed 1 -bed 2 p -~tal1k

~

105100

9590

85uo 80-4J 75J 701n 65~ 60e 55Q) 50 r 45 r ~

- ~05 ~~ru~ I I I I 11 I i I I~I i J I I I I I I I I JO J bull bull

J 25 __----bull _~-- L I _ __ _~__- Jbull__ -__ _J__

5 7 9 11 11) 15 17 19 21 23

- lt

Day Time Hours)

(c) 30 collect9rs cycle time 1400s

102

However with storage tank design 1 maximum CACC is studied as 932 kW

COPsolarnet in case of direct solar coupling is higher than that with storage tank

(Figure 48 (b)) But if smaller dimension of the storage tank is considered it may

offer better values

In the above discussion it has also been established that for the solar adsorption

cooling system supported by heat storage (design 1) 22 collectors with 1400s cycle

time can gain sufficient heat to run the chiller But 30 collectors can be considered in

order to achieve maximum duration for cooling production As for the design 2 the

temperature histories of the collector outlet beds and reserve tank have been

illustrated in Figure 49

Both 22 and 30 collectors with cycle time 1400s have been studied for few

consecutive days It is noticeable that in case of design 1 the collector temperature is

8945degC and the bed temperature is 8922degC (Figure 45) Wh~le for the same

operating conditions in case of design 2 the collector temperature is 9238degC and the

bed temperature is around 8874degC at the steady state (Figure 410) Which indicate

that according to design 1 the chiller is capable to utilize maximum heat absorbed by

solar thermal collector On the other hand according to design 2 the collector

temperature rises higher but the bed temperature is less than that of design 1

Although Figure 47 and Figure 411 illustrate that 1400s is the optimum cycle time

to get maximum cooling capacity for both designs 1 and 2 And COP values increases

with increasing cycle time However smaller cycle time performs better in the

beginning of the day where as a comparative longer cycle time enhances the system

working hour Therefore variable cycle time need to be investigated in order to obtain

a better performance from the system Yet again design 1 is 20 minutes advance than

design 2 to start the chiller but the overall working hour is same for both of the design

Figure 412 Furthermore maximum CACC value is 93 kW and 928 kW for design

1 and design 2 respectively Comparative performances of design 1 and 2 are

103

-

(

10

9

8

7

- 6Samp- 5uulaquou 4

3

2

1

0

8

~--- bull~ - ct- -+ - - ~ 11 ~

0 ~~ t ~~ ~

~ ~~ ~f

il l 1

rJ bullbullbullbullbullbullbullbullbull 20 collectors 1400s -----22 collectors 1400s

- 24 collectors 1400s ~ 26 collectors 14005 ~

----- 26 collectors 1600s ==----- 28 collectors 14005

- 30 collectors 1400s_---_---_-- __ ---_----- ~_~ __ ~ __ l___ _______ ___ __

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

(a) cyclic average cooling capacity

Figure 47 Performance of so~ar adsorption cooling system with storage tankdesign 1

104

_-----------------------____ --------

Figure 47 Performance of solar adsorption cooling system with storage tank design 1

23211913 15 17Day TIme (Hours)

(b) COPcycle

11

bull 20 collectors 1400s ----- 22 collectors 1400s-24collectors 1400s - 26 collectors 1400s- 28 collectors 1400s - 30 collectors 1400s----- 26 collectors 16005

9

080706

~ 05ugtu 04a0u 03

0201a

7

~

20 collectors 1400s ---~-22collectors 1400s24 collectors 1400s 26 collectors 1400s

===gt 28 colectors 1400s --- 30 collectors 1400s 000f --- -- 26 collectors 1600s bullbullbullbullbull

~

o ---1--_ 1- -_---l l-_ I ---- bullbullbullbullbull -__- -- bull--_- bull

005

03

~ 02c

025

bull~ 015aou 01

8 10 12 14 16 18Day Time(Hours)

20 24

(c) COP soiarnet

Figure 47 Performance of solar adsorption cooling system with storage tankdesign 1

105

232119171513

30 collectors cycle lime 14005 with tJlik22 collectors cycle time 8005 direct coupling

I I I I I -1- __I I I I I

11

Day TIme (Hours)

(a) Comparative CACC

9

D~ 0bullbullbullbull 0 bull CIllOe o

co- e bull

~ 22 collectors cycle time 800sirect COUPIi~~bullbullbull bullbullbullbullbullbull 22 collectors cycle time 1400s ith tank bullbullbullbullbull

bullbullbull __ 30 collectors cycle time 1400s w h tank

CIClK)ta ~

I

II

OJ

o

7

025

005

1312

1110

9

3 8 7~ 65 - 5

4321o

)

~ 015ltII0

8 01

bullbullbullltu 02c

7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24

DayTime (Hours)

(b) Comparative COPsolarnet

Figure 48 with optimum projected area and cycle time for direct solar couplingand storage tank design 1

106

~

-collector outlet -bed 1 bed2 -tank

ltflLIA IIl lj l

l ~ ~ bull j 1

J l f l I ~-

Vt 111lt111141deg( Lllllllllllll~] Llllllllhll~t l bullbullbull~ 1~1 ~~ J bullbullbull

-- gt1 I I -1-_ I I I I I I 1 I

I sl day 2nd day 3rd day5 8 1114 17 2a 23 26 29 32 3S 3g 41 44 47 50 53 56 59 62 65 68 71

95

85

-u 750-C1l

65s+(0 55C1lcE

45C1l

bullbullbullbull

35

25

l1iibullbullbullbullbull

~

tIt[~I bull

~I J II

J~tI

~

Day Time Hours)

Figure 49 Temperature histories of different heat transfer units for three corisecuttve days with 30 collectors cycle time 1400s for desigp 2

107

Finally different choices of cycle time have been investigated It has been established

earlier that 1400s is the optimum cycle time for maximum cooling capacity It can be

noticed that at the steady state the system starts working early if smaller cycle 800s

increasing till 140h and decreasing (choice 3) is considered On the other hand

working hour is extended for almost one hour for choice 1 (Figure 413) There is no

change in the cooling capacity for choices 2 and 4 For both of these cho1ces

maximum cooling capacity is 107 kW A similar behavior is observed for COP cycle

and COP solarnet

The cooling effect to the end user dep~nds on the evaporator outlet The evaporator

outlet temperature at the peak hours of the steady state that is 140h to 170h of the

third day is 75deg to 124degC (Figure 415) The lowest temperature of the evaporator

outlet is observed for cycle time 1400s of design 1 According to design 1 the reserve

tank is positioned before the collector During day time collector temperature rises

very quickly hence the temperature of the desorber can be raised within a short time

and the system becomes robust On the other hand change in the choice of the cycle

time shows that with 1400s evaporator outlet is lower than the other choices Due to

the position of the tank the efficiency of the collector has been calculated It is seen

that for design 1 overall collector efficiency is 068 at the steady state However the

efficiency gradually decryases after 150 h The efficiency of the collector 1]sc is

calculated according to the manufacturers data same as Clausse et al [2008] thatis

(41 Q)

(49)

T = THWin + THWOUIHW 2

-where ~JW is the heat transfer fluid mean temperature ie

and J is the solar insolation On the other hand there exists fluctuation in the collector

efficiency for design 2 (Figure 417(b)) The reason behind this behavior can be

explained with Figure 416

108

i

~

-collectoroutlet =~~=bed1-bed 2

23

21

ta 11k

19

I 1 J

1715131197

10595

- 85u0-ltIJ 75loos+ 65robullltIJa 55EltIJ 45

3525

5

Day Time (Hours)

Figure 410 Temperature histories of the heat transfer units at steady state with different collector ~nd cycle time design 2

109

I

109

8

7

i 6II- 5uui3 4

3

2

1

0

8 9 10 11 12 13 14 15 16 _ 17 18 19 20 21 22 23 24

Day TIme (Ihours)

Ii

08

07

06

~ 05ugt-u 04

Q

0u 03

02

01

O- 8

I~-_-__20 cillectors 1400s 24 collectors 1400s I)

26collector 1400s ---22 collectors 1400s ----30collectors 1400s ==28 collectors 1400s I

1 bull

(b) COP cycle

23

Figure 411 The adsorption chiller for different number of collectors anddifferent cycle time at steady state design 2

110

20 collectors 1400s ---24 collectors 1400s26 collectors 1400s ----30collectors 1400s22 collectors 1400s --=28collectors 140

10 12 -14 16 18 20 22 24

bull Day Time (Hours)

(c) COPsolarnet

_Figure 411 The adsorption chiller for different number of collectorsanddifferent cycle time at steady state design 2

24222Q181614

design 1 lt=lt=lt=0 design 2

121QDay TiIne (Hours)

11Figure 412 The adsorption chiller for different number of collectors and

different cycletime at steady state design 1 amp 2

111

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

10908

Q) 07tl 06e 05~0 04U 03

02010

8

~==-design 1 ---- design 2bullbullbull

IIIIIIIII

Day Time (Homs)

(b) COP cycle

03025

005

8 10 12 14 16 18

- -

20 22 24

Day Tillie (Hours)

(c) COPsolarnet

Figure 412 The adsorption chillerfor different number of collectorsanddifferent cycle time at steady state design 1 amp 2

112

gti

r-i~

121110

98

i 7II- 6uu~ 5u

4~ 3

21

0

8

1400suniform-800s nonuniform increasing-800s nonuniform increaing till14h th~n decreasing-800s nonuniform increasingtill sunsetthen decreasin

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

2422

1-

10

-uniform 1400s=nonuniform increasingfrom 800s

nonuniform increasingfrom 800stil114h then decreasing-nonuniform increasingfrom 800s till sunsetthen decreasi

1

09

08

07

06

tugt- 05u0-0u 04

03

02

01

a8

(b) COP cycle

Figure 413 The solar adsorption cooling chiller for different choices of cycletime-at steady state design 2

113

2422201816141210

-uniform 1400s=nonuniform increasingfrom 80~s-nonuniform increasingfrom 800still14h t-nonuniform increasingfrom 800still s

8

02

005

o

025

bull~ 015tiloVIao 01u

Day Time (Hours)

(c) COPsolarnet

-t +

Figure 413 The solar adsorption cooling chiller for different choices of cycletime at steady state design 2

bullbullbullbullbullbullbullcollectoroutlet ==bed 1 -bed 2 tank10095908580-u 750- 70lt1Jbull

J 65+-til 60bulllt1Ja 55Elt1J 50bull 45

40353025

5 7 9 11 13 15 17 1921 23

Day Time (Hours)

Figure 414 Temperature history of different heat exchangers for 30 collectorswith increasing cycle starting from 800s

114

13-design =de~ign2

1482 1492 1502 1512 1522 1532 1542 1552 1562i

8

12

Day Time (Hours)

(a) Different design and cycle time

14

~nonuniform increasing from 800snonuniform increasing froln 800s til114h thendecreasing

=~= nonuniform increasing from 800s till sunset then decreasing

12 _ =uniform 1400s ~~

I ~- i~l ~

( -P amp- d 4-- ~r ~ ~ 4~

) V~ P~~r - 9 ~ ~ I f ~lt7 1 -

~ (=~

[

13

u0-lt1l 11~bullIIIlt1l 100

Elt1lI-

9

8

7

1365 1369 1373 1377 1381 1385 1389 1393 1397 1401 1405 1409

DayTime (Hours)

(b) Design 2 and different choices of cycle time

Figure 4~15Evaporator outlet

II115

~l

~~

~

I 95( 90lO 85~ 80-u 750- GJ 70( ~J 65t + ~ ror 60 GJ~ Q 55r E GJ 50 I- 45 40

3530

~design 2 -design 1

r _

5 7 9 11 13 15 17 19 21 23

Day Time (Hours)

Figure 416 Collectoroutlet design lan~ design 2 with 30 collectors and cycletime 1400s

I

~

~ ~ 116

---L__ _______ ___

~f 7 gt

ff

I I~

fi

07

06

05gtu 04c~u 03QJ

02

01

a

-collectorefficiency

5 6 7 8 9 10 11 12 13 14 15 16 17 18Day Time (Hours)

(a) Storage tank design 1

- collector efficiency

6 7 8 9 iO11 12 13 14 15 16 17 18 19Day Time (Hoursl

(b) storage tank design 2

Figure 417 Collector effici~ncy at steady state

117

~I

H

I

Cooling production with optimum collector area andoptimum cycle time

Figure 418 Cooling production by system with direct solar coupling 22-collectorscycle time 800s and with storage tank ~esign 1 amp 2 collector number 30

cycle time ~400s

Figure 419 Heat used if cooling production by the system with direct solarcoupling 22 collectors cycle time 800s and with storage tank design 1 amp 2

collector number 30 cycle time 1400s

118

With storage tank chiller need to use less heat in to produce cooling compared with

the chiller with direct solar coupling Figure 418 (a) (b) and (c) represent the bar

diagrams of energy used and produced for different cases It is observed that with

optimum collector number 22 and cycle time 800s for direct solar coupling total

cooling production is 2649036 kJ utilizing 9980169 kJ heat that is 026 cooling

Whereas the chiller produces 274174 kJ cooling with 5382294 kJ heat that is 05

cooling with optimum collector number 30 and cycle time 1400s with storage tank

The rest of the heat that is collected through the projected area are utilized to heat up

tank water which can perform for other purposes I

45 SummaryIn the present chapter a storage tanltis added with the solar adsorption cooling system

in anticipation to enhance both the working hour and the system performance Two

different designs have been considered Maximum cooling capacity 93 kW is

achievable with design 1 System working hour is enhanced after sunset with design

2 In case of both of the designs optimum cycle time is 1400s with 30 collectors

Moreover longer cycle time extends system working hours and the COP values for

both of the cases Hence variable cycle time at different time interval of the day has

been investigated with design 2 -

Considering shorter cycle in the mormng when insolation IS very low and a

comparatively longer cycle at the end of the day improves the system performance

both in view of the cooling capacity and in extension of the wrking hour after sunset

On the other hand implementation of smaller cycle time and an increasing cycle till

sunset maximize cooling capacity

However the overall collector e~ficiency is 068 for both of the designs although

uniform efficiency is observed for design 1 while it oscillates for design 2 Since the

collector outlet temperature for design 1 shows a uniform increase during day time

and decrease at afternoon as a result there is uniform value in collector efficiency Onthe other hand there exist fluctuation in the collector outlet temperature hence there

exist no uniformity in efficiency ofthe collector

The cyclic average cooling capacity 1199 kW is maximum for the chiller with direct

solar coupling The performance of the chiller with storage tank could be improved if

119

I~

i

I-~j~

smaller dimension of the storage tank or advanced adsorption chiller can be

considered It is observed that with optimum collector number 22 and cycle time 800s

for direct solar coupling chiller can produce 026 cooling where as it is 050(0 with

optimum collector number 30 and cycle time 1400s with storage tank design 1

120

L fj

iI ~

J

~

CHAPTER 5

Hot Water Supply During Winter Season Utilization of Solar

Thermal Collectors

51 IntroductionThe duration of Winter season is two months in Bangladesh According to the

geographical position of Dhaka minimum temperature of this region during winter is

around 11 to 16degC except for few irregular sudden cold waves when the temperaturedrop

is seldom less than 10degC In Chapter 2 investigation is done for an optimum projected

area and an optimum cycle time suitable for the typical hot summer period to utilize

climatic data of Dhaka for maximum cooling production It was observed that 22

collectors with optimum cycle time 800s can produce maximum cooling for the climatic

condition of Dhaka with direct solar coupling

It is discussed in Chapter 3 that the cyclic average cooling capacity (CACC) for

December for optimum projected area with optimum cycle time is 66 kw with direct

solar coupling During winter it is not necessary to run the chiller since room cooling is

not needed at this time of year But again the modern architectural buildings are designed

in such a way so that the temperature of the room can be controlled Also there is no

ventilat~on in this type of buildings Thu~ some cooling production is needed for

comfortable working environment Furthermore beyond room cooling the chiller could

be utilized for use of household hot water supply to u~ilize in cooking bathing and other

house hold affairs This will save primary energy used in cooking such as useof natural

~ gas or other primary fuelsI

According to State of Colorado estimate typical need of water [2014] a minimum well

yield of 4 to 10 gallons per minute is recommended for househol~ That includes shower

and bath faucet toilet and cloth washing Hence an average of 8 gallons of water per

~

I___L121

j

minute can be considered to be consumed for household in each_day during peak demand

in Dhaka

52 System Description and Mathematical EquationsBased on the discussion of Chapter 4 itis comprehensible that 30 collectors each of area

2415 m2 along with an insulated reserve tank (holding water) of volume 133m3 need to

be installed for expected performance On the other hand it needs 22 collectors to run the

chiller only during day time with direct solar coupling In December since cooling is not

required the valve between collector and bed and reserve tank and bed is closed The

collector panel is connected with reserve tank directly Tank supplies hot water for

household use and also to the collector The amount of outflow of tank water for

household is filled up with same amount of inflow of water of ambient temperature

during day time Tank size is same as the tank considered in Chapter 4 Weight of water

in reserve tank is half of that of the weight considered in Chapter 4 Schematic of the tank

and collector water flow chain is presented in Figure 51

In order to store hot water heated inside the collector and to reserve it in the reserve tank

a closed hot water fill is considered without any outflow for household The schematic of

the closed hot water fill is given in Figure 52

Water supply from the collector to reserve tank and from reserve tank to collector is

considered to be 1 kgs While the outflow of the reserve tank for household and inflow

to reserve tank of water of ambient temperature is equal and it is 05 kgso Exploiting a

lumped parameter model the energy balance equation for collector are

dTcr ( )WcrM i -- = 7]Acr J + mf cre ~ank - Tcr i out

dt l UCPiAcp]

TCriout = Tcri + (rtank - TcrJexp- rnIcre I

122

(5 1 )

(52)

SolarI

Tlterloal Co8ector

(

Figure51 Schematic diagram of hot water chain -between collector tank and

household use

Figure 5~2Schematic diagram of closed h~t water ~hain between collecto~ and tank

123

I _~

~Obil - Q

ii ~l~ ITllerlnal c~onector l~

~ ~T ------[lt----------~

ll I~V4

___-L

l

~

And energy balance equation of the reserve tank is

~Wt Ct +W tC ~ t=m C (T t -T t)+UtorsAS(Tam -Tw)-mwCw(Twt-Tam) dt m m w w w w w crou w (53)

Also for the second case there is no drain of water from the reserve tank for household

and therefore no fill in the tank the energy balance equation isc

(54)

53 Result and DiscussionIn December with 22 projected area and cycle time 800s collector temperature rises till

bull I 70degC at the steady state (3rd day) with direct solar coupling The temperature history of

the collector outlet and beds are illustrated in Figure 53 For 30 projected area and cycle

time 1400s when the storage tank is added (with design 2 described in Chapter 4)

collector temperature as well as the tank temperature rises gradually in each consecutive

day Since the tank is insulated there is a negligible amount of heat loss of tank water

during the night time Since in winter room cooling is not applicable the valve between

collector and bed and tank and bed is closed The c91lector panel is connected with tank

directly Tank supplies hotwater fOfhousehold use and also to the collector The amount

of outflow of tank water for household is 05 kgs and is made up with same amount of1

inflow of water of ambient temperature during day time Tank size is same as the tank

considered in Chapter 4 Weight of water in reserve tank is half of that of the weight

considered in Chapter 4 (Table 43) The temperature history of tank water and ambient

temperature is illustrated in Figure 54 In this case hot water flow from collector to tank

and from tank to collector is 1 kgso In this case 22 collectors are connected with the

reserve tank In this system tank temperature rises to 345deg~

On the other hand with storage tank 30 projected area is optimum Hence there remain 8

more collectors Hence another tank of same size can be altided with the remaining 8

collectors ~ollector supply hot water at the rate of 1 kgs to the tank and tanksupplies

124

-P~_ __ l J

--colectoroutlet bullbullbullbullbullbullbull beurod1 c=~-==bed2

~~ ~

I ~i~

At steady state Oecember 22 collectors cycle time 800speak hours direct solar coupling

- -- ~ r

~-i

Figure 53 Temperature history of collector outlet and bed for direct solar coupling

125

125 13

= Tankwater -ambienttemperature

36

33

-u 300-QlbullJto 27bullQlCLE 24Qlt-

21

186 8 ~o 12 14

DayTime (Hours)16 18

Figure 54 Temperature history of reserve tank when 22 collectors supply hot water

to tank tank supply hot water for household and supply water fill up the tank

Figure 55 Temperature history of reserve tank when 8 coll~ctors s~pply hot water

-to tank no supply of hot water for household

Ibull

9 12

Day Time (Hoursl-

15 18

11bull

126

water to the collector No outflow from the tank is considered for household during day

time The temperature history of tank and ambient temperature in this case is illustrated

in Figure 55 The temperature of tank water at the end of the day is 4rC This water can

be used for household need after sunset

54 SummaryIn order to utilize solar heat even after sunset one needs to install 30 collectors along

with a storage tank of size 133m3bull Whereas it needs 22 collectors with optimum cycle

time to get maximum cooling during a typical hot day in April Thus in December with

22 collectors hot water supply of 345degC can be supplied for house hold use during day

time And at the same time with the remaining 8 collectors hot water of 4rc can be

t saved in another reserve tank of same dimension to be used after sunset for household

1 need

if1 In the next chapter conclusion and future work of the thesis is discussed for the climatic

j) condition of Dhaka as well as Bangladeshi~1

i

127

f

q

IjHlIIIiIIij~I

CHAPTER 6

An analytical investigation was carried out to explore the prospect of implementation

of solar heat driven adsorption cooling system for the perspective of a tropical region

Dhaka Bangladesh (Latitude 2373deg N Longitude 90AOdeg E) The measured solar

insolation data collected by Renewable Energy Research Centre (RERC) University

of Dhaka has been utilized in the simulation The maximum and minimum

temperatures throughout the year and the sunrise and sunset time have been supplied

by Bangladesh Meteorological Department The concept of waste heat driven

conventional two bed basic adsorption chiller has been considered where silica gel-

water pair was chosen to be the adsorbent-adsorbate pair The climatic condition of

different global region differs widely and hence the system performance varies Since

the selected city Dhaka is a tropical region an alternative to the waste heat solar

insolation is considered to be the source of driving heat of the proposed chiller As for

the driving heat solar insolation is availed free of cost and silica gel is available low

cost and environment friendly the contribution of this system would be popular for a

developing country like Bangladesh if the installation cost can be brought to its

optimum level Based on the climatic and solar data of Dhaka the performance of a

two bed conventional basic adsorption chiller has been studied for three cases (i)

With direct solar coupling (ii) a heat storage tank is added with the system and (iii)

during winter season as hot water supplier It should be noted that the cooling

capacity increases with the increase of projected area whereas the COP values

increases with the increase of cycle time The performance can be increased by

-increasing cycle time with a smaller projected area But there exists optimum cycle

time for a particular projected area to get maximum cooling capacity Furthermore as

cooling capacity is dependent on the chiller configurations there also exists optimum

projected area Study has ~een conducted for direct solar coupling to figure out

optimum projected area to get maximum cooling for the proposed chiller with the

considered base run conditions It was observed that

bull optimum projected area is found 22 solar thermal collectors with each having

an area 24l5m2 and optimum cycle tiple is 800s128

~

bull

Maximum cooling capacity is found to be 119 kW

COP cycle is 047 at the peak hours where maximum COP cycle is 065 which

occured at the end of the day

Maximum COP sc is found as 031

Change in the cycle time is found not to have much effect on the performanee

of the chiller

Collector temperature has been raised to 952degC and bed temperature to

875degC

Evaporator outlet temperature is found to be 71degc

Optimum chilled water supply to the evaporator is 07 kgs

Chiller performs from 80 h in the morning till 180 h in the evening That is

overall 10 hours during day time at steady state

Overall cooling production in one working day is 2649036 MJ

On the other hand fot a moderate projected area too long cycle time may raise

collector temperature beyond lOOdegCwhich is not desirable for the heat transfer fluid

(water) considered in the present chiller In an intension to enhance the system

performance different choices of non uniform cycle time and chilled water flow rate

has also been studied It was seen that a comparatively longer cycle time should be

considered at the beginning and at the end of the day to prolong the system working

hour Also for the chilled water flow it is seen that for the base run conditions 1kgs

chilled water flow to the evapo~ator gives maximum cooling capacity but considering

the evaporator outlet temperature 07 kgs flow rate is better option for the

comfortable cooling for end user The available insolation varies in different seasons

throughout the year In this regard comparative performance for the months of March

April June August October and December had been studied It is observed that

better performance is achieved for themonths of March and April During this period

of the year which is the beginning of the hot summer monsoon is yet to start

Therefore sky is apparently clear than the heavy cloud coverage during monsoon

129

IIjf

starting from May till October On the other hand December is the beginning of

winter season and therefore though the sky is clear other climatic conditions such as

maximum minimum temperature and sumise sunset time affect the chiller

performance

Since solar insolation is not available at night and during day time amount of

insolation varies with time such as maximum insolation is collected between IIGh to

120h At the sumise and sunset hours the insolation is very low chiller can work only

for day time and a very small period of time If the heat can be stored and used when

sun insolation is not available work~ng hour of the chiller could be enhanced In

anticipation of the enhancement of the chiller working hour an insulated storage tank

had been joined in the system in two ways In this system since a huge amount of

water reserved in the storage tank need to be heated first in order to run the chiller the

chiller starts functioning late than the system with direct solar coupling Also it needs

a longer cycle time to heat up water in the -collector Therefore optimum projectedr

area for this case is more than that of direct solar coupling~ It is observed that with

design 1 the chiller starts functioning earlier than design 2 on the other hand with

design 2 the chiller functions late after sunset For both of the cases maximum cooling

capacity is around 93 kW The maximum cooling effect is available for a longer time

with heat storage than the system with direct solar coupling The cooling capacity and

overall cooling load could be enhanced if (a) suitable operating conditions can be

adopted and (b) an advanced system such as heat recovery system mass recovery

system or multiple stage system is implemented However with the present

considerations it can be concluded that

bull With storage tank of volume 2197 m3 containing 2177 liters of water

optimum collector number is found 30 and optimum cycle time 1400s

bull Maximum CACC is found to be 93 kW with optimum cycle time

bull Cycle time is found to be ah important parameter

bull Maximum CACC 107 kW occurs for shorter cycle during 130-150 h

130

bull Working hour enhances for longer cycle time

bull

Evaporator outlet temperature is minimum for optimum cycle time 1400s at

peak hours

Minimum temperature of evaporator outlet is found to be 75degC

I

bull Overall cooling production is found 274174 MJ with design 1 and it is

2616234MJ with design 2

During winter III Dhaka mInImUm temperature vanes between 11 to 16degC and

maximum temperature is 24degC Therefore during this time of the year room cooling

or heating is not needed But hot water supply is in demand for household use It

includes demand in cooking bathing and dishwashing Obtainable hot water supply

by utilizing solar thermal collectors installed for room cooling purpose in summer

has been discussed With a reserve tank of volume 2197m3 which contains 10885

liters of water

bull

With 22 collectors a continuous water supply of temperature 345degC at a rate

of 05 kgs could be assured at the peak hours for household use

With remaining 8 collectors water of temperature 47degC could be stored for

house hold use during night time

d

Future WorkBased on the above discussion it is understandable that for the implementation of the

application of solar heat driven cooling system for the climatic condition of Dhaka as

well as Bangladesh the following studies are necessary

bull The optimum tank dimension for maximum performance

bull Heat recovery system with solar coupling

bull Mass recovery system with solar coupling

bull Implement multistage andor multiple bed for improvement of the

performance

131

bull A comparative study of hybrid system such as solar adsorption cooling with

(a) electricity driven vapor compression chiller (b) natural gas driven vapor

compression chiller

bull Study on economic perspective of the system comparing with that of existing

system

132

~

d

References

Akahira A Alam K C A Hamamoto Y Akisawa A Kashiwagi T (2004)Mass recovery four-bed adsorption refrigeration cycle with energy cascadingApplied Thermal Engineering Vol 25 pp 1764-1778

Akahira A Alam K C A Hamamoto Y Akisawa A and Kashiwagi T (2005)Experimental investigation of mass recovery adsorption refrigeration cycleInternational journal of refrigeration Vol 28 pp 565-572

Alam K C A Saha B B Kang Y T Akisawa A Kashiwagi T (2000a) Heatexchanger design effect on the system performance of silica gel - water adsorptionsystem Int J Heat and Mass Transfer Vol 43 (24) pp 4419-4431

Alam K C A Saha B B Akisawa A Kashiwagi T (2000b) A novelparametric analysis of a conventional silica-gel water adsorption chiller JSRAETransaction VoL 17 (3) pp 323-332

Alam K C A Saha B B Akisawa A Kashiwagi T (2001) Optimization of asolar driven adsorption refrigeration system Energy conversion and managementVol 42 (6) pp 741-753

Alam K C A Akahira A Hamamoto Y Akisawa A Kashiwagi T Saha B BKoyama S Ng K C and Chua H T (2003) Multi beds multi-stage adsorptionrefrigeration cycle-reducing driving heat source temperature JSRAE TransactionVol 20 (3) pp 413-420

Alam K C A Saha B B Akisawa A and Kashiwagi T (2004) Influence ofdesign and operating conditions on the system performances of a two-stage adsorptionchiller Chemical Engineering Communications Vol 191 (7) pp 981-997

Alam K C A Rouf R A Khan M A H (2009a) Solar adsorption coolin~based on solar data of Dhaka Part 1- effect of collector size presented at 16t

Mathematics Conference Dhaka 17-19 December

Alam K C A Rouf R A Khan M A H (2009b) Solar adsorption coolin~based on solar data of Dhaka Part II- effect of cycle time presented at 16t

Alam K C A Saha B B Akisawa A (2013a) Adsorption cooling systemdriven by solar collector A case study for Tokyo solar data AppJied ThermalEngineering Vol 50 (2) pp 1603-1609

Alam K C A Rouf R A SahaB B Khan M A H Meunier F (2013b)Adsorption solar cooling - driven by heat storage collected from CPC panelProceedings of Inilovati ve Materials for Processes in Energy Systems IMPRES20 13pp397-402Chen J and Schouten A (1998) Optimum performance characteristics of anirreversible absorption refrigeration cyole Energy Conversion and Management Vol39 pp 999-1005Chua H T Ng K c Malek A Kashiwagi T Akisawa A Saha B B (1999)Modeling the performance of two-bed silica gel-water adsQrption chillers Int JRefrig Vol 22 pp 194-204

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Clausse M Alam K C A Meunier F (2008) Residential air conditioning andheating by means of enhanced solar collectors coupled to an adsorption systemSolar Energy Vol 82 (10) pp 885-892Critoph R E (1998) Forced convection adsorption cycles Appl Thermal EngVol 18 pp799~807Douss N Meunier F (1988) Effect of operating temperatures on the coefficient ofperformance of active carbon-methanol systems J Heat Recovery Syst CHP 8(5)pp 383-392Electricity sector in Bangladesh Wikipedia the free encyclopedia (viewed on5

April 2014)Farid S (2b09) Performance evaluation of a two-stage adsorption chilleremploying re-heat scheme with different mass ratios Mphil thesis DepartmentMathematics Bangladesh University of Engineering and TechnologyGuilleminot J 1 Meunier F (1981) Etude experimental dune glaciere solaire

utilisant Iecycle zeolithe-13X-eau Rev Gen Therm Fr 239 pp 825-834

Greatest Engineering Achiev~ments-lO Air Conditioning and Refrigeration

httpwwwmaencsuedueischencoursesmae415docsgreatestEngineering

Achievementspdf(viewed on 4 April 2014)

Heat pump and refrigeration cycle Wikipedia the free encyclopedia (viewed on 5ApriI2014a)History of Refrig~ration IIT Kharagpurhttpwwwacademiaedu4892513EEIlT Kharagpur India 2008 40 LESSONS ON REFRIGERATION AND AIR CONDITIONING FROM lIT KHARAGPUR USEFUL TRAINING MATERIAL FOR MECHANICAL ENGINEERING STUDENTS -

(viewedon 6 March 2014)Images of absorption refrigeration cycle httpwwwustudyinincde3197 (viewed on5 April 2014)Jakob D (2013) Sorption heat pumps for solar cooling applications ProceedingsofInnovative Materials for Processes ih Energy Systems IMPRES2013 pp 378-382Kashiwagi T Akisawa A yoshida S Alam K C A Hamamoto Y (2002) Heatdriven sorption refrigerating and air conditioning cycle in Japan Proceedings ofInternational sorption heat pump conference September 24-27 Shanghai Cqina pp

J 50-62

Khan M Z 1 Alam K C A Saha B B Akisawa A Kashiwagi T (2007)Study on a re-heat two-stage adsorption chiller - The influence of thermalcapacitance ratio overall thermal conductance ratio and adsorbent maSs on systemperformance Applied Thermal Engineering Vol 27 pp 1677-1685Li M and Wang R Z (2002) A study of the effects of collector and environmentparameters on the performance of a solar powered solid adsorp~ion refrigeratorRenewable Energy Vol 27 pp 369-382

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Meunier F (1986) Theoretical performance of solid adsorbent cascading cyclesusin~ zeolite-water and active carbon- methanol pairs four c~se studies Heatrecovery CHP system Vol 6 (6) pp 491-498Miyazaki T Akisawa A Saha B B EI-Sharkawy L L Chakraborty A (2009)A new cycle time allocation for enhancing the performance of two-bed adsorptionchillers International Journal of Refrigeration Vol 32 pp~846-853Pons M Guilleminot 1 J (1986) Design of an experimental solar powered solidadsorption ice maker Journal of Solar Energy Engineering Vol 108 pp 332-337

Pons M Poyelle F (1999) Adsorptive machines with advanced cycles for heatpumping or cooling applications International Journal of Refrigeration Vol 22(1)pp27-37Principle of adsorption cycles for refrigeration or heat pumpinghttpwwwgooglecombdimagesq=principle+of+Adsorption+cycles+for+refrigeration+or+heaHpumping (viewed on 5 ApriI2014f)Rothmeyer M Maier-Luxhuber P Alefeld G (1983) Design and performance ofzeolite-water heat pumps Proceedings of IIR-XVIth International congress ofRefrigeration Paris pp 701-706Rouf R A Alam K C A Khan M A H Ashrafee T (2011) Prospect of solarcooling based on the climatic condition of Dhaka Proceedings of 9th InternationalConference on Mechanical Engineering RE-14Rouf R A Alam K C A Khan M AH (2013) Effect of operating conditionson the performance of adsorption solar cooling run by solar collectors ProcediaEngineering Vol 56 pp607-612Sakoda A Suzuki M (1986) Simultaneous transport of heat and adsorbate inclosed type adsorPtion cooling system utilizing solar heat J of Solar EnergyEngineering Vol 108 pp 239-245Saha B B Boelman E c Kashiwagi T (1995a) Computer simulation of asilica gel-water adsorption refrigeration cycle - the influence of operating conditionson cooling output and COP ASHREA Trans Res Vol 101 (2) pp 348-357Saha B B Boelman E C Kashiwagi T (1995b) Computational analysis of anadvanced adsorption refrigeration cycle Energy Vol 20 (10) pp 983-994Saha B B Alam KC A Akisawa A Kashiwagi T Ng K C Chua H T(2000) Two stage non-regenerative silica gel-water adsorption refrigeration cycleProceedings of ASME Advanced Energy System Division Orland pp 65~78Shelton S V Wepfer 1 W Miles D J (1990) Ramp wave analysis of thesolidvapor heat pump ASME Journal of Energy Resources Technology Vol 112pp 69-78 _Sokolov M Harshgal D (1993) Optimal coupling and feasibility of a solarpowered year-round ejector air conditioner Solar Energy Vol 50 pp 507-512

State of Colorado estimate typical need of waterlegmtgovconlentcommitteesInterim2007 _2008water-policystaffmemos typicalneedpdf (viewed on 14May 2014)Tchernev D I Emerson D T (1988) High -efficiency regenerative zeolite heatpump ASHRAE Trans Vol 94 (2) (2) pp 2024-2032

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Vargas J V c Sokolov M and Bejan A (1996) Thermodynamic optimization ofsolar-driven refrigerators J of Solar Energy Engineering Vol 118 pp 130-136

Wang R Z (2001) Performance improvement of adsorption cooling by heat(indmass recovery operation International Journal of Refrigeration Vol 24 pp 602-611

Yong L Sumathy K (2004) Modeling and simulation of a solar powered two bedadsorption air conditioping system Energy Conversion and Management Vol 45pp2761-2775

Zhang G WangD C Han Y P Sun W (2011) Simulation of operatingcharacteristics of the silica gel-water adsorption chiller powered by solar energySolar Energy Vol 85 (7)pp 1469-1478

136

Journal

Alam K C A Rouf R A Saha B B Khan M A H Meunier F Autonomousadsorption cooling - driven by heat storage collected from solar heat Heat TransferEngineering (In Press 2014)

Rouf R A Alam K C A Khan M A H Ashrafee T Anwer M (2013a) Solaradsorption cooling a case study on the climatic condition of Dhaka AcademyPublishers Journal of Computers Vol 8 (5) pp 1101-1108

Rouf R A Alam K C A Khan M A H Saha B B El-Sharkawy I IPerformance analysis of solar adsorption cooling system - effect of position of heatstorage tan~ Applications and Applied Mathematics an International Journal (AAM)(under r~view)Rouf R A Alam K C A Khan M A H Saha B B Meunier F Significance ofheat storage in the performance of solar adsorption cooling system (underpreparation)

Alam K C A Rouf R A SahaB B Khan M A H Meunier F (2013)Adsorption solar cooling - driven by heat storage collected from CPC panelProceedings of Innovative Materials for Processes in Energy Systems IMPRES2013pp397-402Rouf R A Alam K C A Khan M A H Ashrafee T (2011) Prospect of solarcooling based on the climatic condition of Dhaka Proceedings of 9th InternationalConference on Mechanical Engineering 2011 ICME11-RE-014

RoufR A AlamK C A Khan M A H (2013b) Effect of operating conditionson the performance of adsorption solar cooling run by solar collectors ProcediaEngineering Vol 56 pp 607-612~Rouf R A Alam K C A Khan M A H Saha B B Meunier F Alim M AKabir K M A (2014) Advancement of solar adsorption cooling by means of heatstorage Proceedings of 10th International Conference on Mechanical EngineeringICME2013

- i Conference Proceedings (Full length articles)

~

Conference Presentations (Abstract boo~)

Alam K C A Rouf R A Khan M A H (2009) Solar adsorption cooling basedon solar data of Dhaka Part I- effect of collector size presented at 16th MathematicsConference Dhaka 17-19 December

137

_------- _- _ --_ _ __ _---------------------

IIi

-

Alam K C A Rouf R A Khan M A H (2009) Solar adsorption cooling basedon solar data of Dhaka Part II- effect of cycle time 16th Mathematics ConferenceDhaka 17-19 DecemberRouf R A Alam K C A Khan M A H Ashrafee T and Khan A F M K(2011) Mathematical Analysis of Adsorption Solar Cooling in the perspective ofDhaka Climatic Conditions 17th Mathematics Conference of BangladeshMathematical society Dhaka 22-24 December

138

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00000019
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00000032
00000033
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00000038
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Page 2: Full Thesis - Bangladesh University of Engineering and ...

wi

This thesis entitled Analytical Investigation for the Solar Heat Driven Coolingand Heating System for the Climatic Condition of Dhaka submitted by RifatAra Rouf Roll nOP0409094001P Registration no 0403447 Session April-2009 hasbeen accepted as satisfactory in partial fulfillment of the requirement for the degree ofDoctor of Philosophy in Mathematics on 12th July 2014

Board of Examiners

1

2

-~tY

Dr Md Abdul Hakim KhanProfessorDepartment of MathematicsBUET Dhaka-lOOO(Supervisor)

At~Dr K C Amanul AlamAssociate ProfessorDepartment of Electronics and Communication EngineeringEast-West University Dhaka-1212(Co-Supervisor)

Chairman

Member

3 _HeadDepartment of MathematicsBUET Dhaka-lOOO

4D~ProfessorDepartment of MathematicsBUET Dhaka-1 000

11

Member (Ex-Officio)

Member

~ I 7bull _

-

Member

c bull

)n-~~7bull~_(_~-_v_) _

)

Member (External)

iii

--- __ ----~-----_ _

DEDICATION

tV

~A~Rifat Ara Rouf

12th July 2014

v

___ ctr --- ---- _ -

-__~_- - ----_-_ _-

Acknowledgement

VI

~---__- -----__ __

and advice

understanding

Vll

_ _--_--- -

Abstract

heating purposes

VIp

CONTENTS

Board of Examiners

Acknowledgements

Abstract

Nomenclature-

List of Tables

List of Figures

ii

v

vi

viii

xiii

xiv

xv

CHAPTERl (

124 Time Line

Cycle

IX

1

2

3

5

6

7

8

10

11

13

14

17

Refrigeration Cycle

CHAPTER 2

23 Formulation

231 Solar System

Cycle Time

25 Summary

x

18

26

27

353537

3738

39

4041

45

4750

51

54

6071

r ~-I

I j

------

CHAPTER 3

Dhaka

31 Introduction

33 Summary

CHAPTER 4

System Performance

41 Introduction

45 Summary

CHAPTERS

54 Summary

CHAPTER 6

Xl

73

88

89

899094

95

119

121

122

124

127

128

-

Future work

References

Xli

131

133137

r

Nomenclature

A Area (m2)

XliI

------------- __--------~ -_- --- _- _ -

I

r~-I

i

List of Tables

-

XIV

94

I

List of Figures

II

Figure 11

Figure 12

Figure 13

Figure 14

Figure 15

Figure 16

Figure 17

Figure 18

[2009]

cooling system

[2009]

xv

15

16

19

20

21

22

23

24

25

28

[2005])

April

optimum cycle time

XVI

Figure 24

Figure 25

(

cycle 800s

57

58

59

62

Figure 27

Figure 28

Figure 29

140h

then decreasing

cooling capacity

XVII

62

63

64

66

rttI

-

Figure210

Figure 710

Figure 211

Figure 212

Figure 31

hours

cycle -

(a) March

(b) April

(c) June

(d) August

68

69

70

74

75

Figure 31

bullbullbull

(e) October

(t) December

March

XVIII

76

80

months (a)CACC

months (c) COPse

XIX

gt

time 1400s

xx

~I

design 1

for design 2

cycle

COPsolarnet

XXI

104

105

106

107

109

110

III

111

Figure 412

Figure 413

Figure 414

Figure 415

Figure 4J5

COP cycle

COPsolarnet

cooling capacity

time

Figure 416

Figure 417

Figure 418

design 1

design 2

XXII

116

117

118

b

Figure 419

Figure 51

Figure 52

Figure 53

Figure 54

Figure 55

1400s

collector and tank

solar coupling

household

XXIII

CHAPTER

Introduction

11 Introduction

cycle begins again

I

2

--

f

3

e

4

I

i1

Japan

conditioning

cooking

residences

perishable goods

Kettering of GM

distribution

5

Superior Arizona

surface phenomenon

the adsorbate

6

t

--l

7

isotherm etc

8

f

9

(v) Low viscosity

water etc

10

-

io-(

11

I~

f

IIII[

f

I

i

1

12

I

t f

I

i

~~

13

lt A ~ -

of the liquid

cycles lie around 3

14

f

CompressorQpor

~vaporator

Expansion

Condenser

Uquid + porValve

15

-Isobars

( ~

t

~

1

~-

-I--

1 _

1-

f

----4-isobar

1gt1 Y Liquid

--_ 1 Vapor

High Pr

i NH3 Vapour

VapQufc ~

~~n~~t~

Q T j1gt~

1 1~ ~-~- ~ -

Strong Absorb~r -

NHJ solution

16

(Figurel3)

17

18

-~

LoP

II

I

~~

~

-lIT

-

AdsomedI

vapour

Ie

-~oCondensel

heat pumping [2014J

19

~

--

~

LnP

-lff

Q-

ht Qcs~---II

IIIII

bullbullII_~- -

20--_bullbull_--------_- -- _ --_-

-~ -

-

LnP

~

COtliBS + ltii

tlqmssumtttibn -lIT

heat pumping [2014]

21

LnP

-lIT

QcsTcs ===

IIIIIIIIIII_---

heat pumping [2014]

22

I ~ _

I -

i ~i

Ci Pc- bull Wo- InP

bull

PE

I)-

T-o

23

vm

Condenser

SE2

V8

EvaporatorV2 i

II i

r-------

VIrt

i =

Cooling load

system

24

deg IIIIII V4

vs

r -~---~- deg

VI IIi

~

i (IIi= Ii~Ii~ 0

~

V2 V8

Evaporator

adsorbero

SEl

25

installed

process)

26

~

27

8x+amp

lnP

~ ~

a2e a1 a1

bullbull1--T

28

29

)~ 737t tlOr~ lir ~ ~ t 4~24l

bull~f

1~8 234

~

]f~ 123~

o10 20 30 40 50 60 70 80

40

bullbullu30 L

4JI-

2~I-~p

fi20 -

1-ec~gt01)

10 bullbullCd3Cd

r

0

30

et)c~- (JJ-~deg0o~u

5

~

Heatrejected

VIO

Condenser

V8----

Evaporator

r------- J~~ ~_~ IIIIII V4

VI

V2

~

i=1

I

31

---_-bull_----_ - --

32

--_ bull__-----~----------__-__ __ _- -

jiJ

~iAff~l

CONO

(b) ModcB

CONOl

CONOI

(a) ModeA

33

denoted as mode D

mode A

34--_bull_ bull_-----------------__- _

Sumanthy [2004]

35

36

Figure 112

mathematically

ice making purpose

37

~

f ~

lower heat source

38

CHAPTER 2

ofDhaka

39

-~--_ ---_ _ _

40

I

41

-_ __-__-----__----__ __ ~

V4btgt~c- ()- ~0

VIO 00U-

5

VI

- ~~

bull t~

42

(23)

by

transfer fluid

(24)

43

(27)

(26)

(25)

loops

ToUl

state q

(29)

calculated by

Ps(T) = 13332 e [183-3820 1(1-461)] (21 0)

44

(213)

(212)

endojcyclelime

endofcycletime

cycle

number of collector

ao -15587 bo -65314

aj 015915 bl 072452E-Ol

a2 -050612E-03 b2 -023951 E-03

a3 053290E-06 b3 025493E-06

231 Solar System

45

expressed as

where

(214)

(215)

(2 f6)

46

(217)

47

900800

f1E 700

~ 600c2 500+(U-o 400IIIs - 300_(U

0 200til

100o

bull

[l 06042009 RERC [JI

5 7 9 11 13 17 19

Day Time (Hoursl

April

48

49

(218)

am ~--~+-~-~ In ----------- 2 2 Daylength

50

~

i

51

I

161412

4

2

o

I

T 8 9 -10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

52

06

05

Gl 04]~ 03Ou 02

01

o

7 8 9 10 11 12 13 14 15 16 17 18 19

DayTIme (Hours)

03

025

02uIII0 0150u

01

20 collectors

I _~_L L__

i

8 9 10 11 12 13 14 15Day Time (Hours)

16 17 18 19

53

I

-

54

II

55

19

6 i-n bull ~

1715

13Day Time (Hours)

119

Day TIme (Hours)

8 9 10 11 12 13 14 15 16 17 -18 19

18

16

14

12

~ 10lII

Uu 8ctu

6

4

2

0

7

12

j 1~~ lt~

1 08 QI) U gtu 06

Q

0u04

02

0

7

56

191715

13

DayTime (Hours)

10 11 12 13 14 15 16 17 18 19

9

--r bull ~ --_- ---~~-~-~--~~~~- ~ 1~

~ ~

bullbull

8

7

a

03

04

01

u0 028

035

03

005

0

7

DayTime (Hours)

57

12 13

Daynme (Hours)

f f

~

~ 0 bull 0 Q

bull g -- ~

~

bull bull I bull

12 13

Day Time (Hours)

58

~gt =

1312

po 11-10

9

8

deg7

6

- 22collectors1000s

11191195 12 1205 121 1215 122 1225 123 1235

Day Time (Hours)

59

li

i ~

60

the sunset hours

(i) 800s

(ii) 800s 140 - 185 h 20 scycle

61

110100

P 90-~ 80J10 70~ 60~ 50I-

4030

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day TIme (Hours)

110 100 ~

4030

17 19

140h

62

decreasing gt I11i

1917151311

DayTime (Hours)

97

~ 100d1

f(

U 900-lt1l 80l+ 70(ll lt1lQ 60E 50

4030

5

Il

1917

uniform cycle 800s

9

11 13 15

Day Time (Hours)

()fJ

~~ 13

121110

9~ 8 7

7

63

1

08

41 06ugtua0 04u

02

o

7 8 9 10 11 12 13 14 15 16 i7 18 19

Day Time (Hours)

05

04

u 03VIa

0u 02

01

0

7 9 11 13

__ I

64

~

(J

1ltlt

1lt ~

lt)lt

(OC)(i) Uniform 95 87 71 119 065 0315

800s(ii) Non- 95 87 71 119 057 0314

uniform800s

(iii)Non- 93 85 74 118 056 0311uniform550s

65

12115

11

U 105a-~ 101i 95~ 9E~ 85

8757

1195

12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

r Co

66

67

II

U 100o- 90 bullbullJ 80tu~ 70~ 60

~ 504030

5 7 9 11 13 15 17 19Day TIme (Hours)

fr

Ii ~

110

40

30

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

68

Day Time (Hours)

-__-~--~-

(a) CACC

__ ~_L_~_~_

9 10 11 12 13 14 15 16 17 18 19

09

08

07

~ 06gtrr 058 04

03

02

01 -

o

13121110- 9

S 8 7-u 6uot 5u 4

3210

7 8

7 8 9 10 11 1213 14 15 16 17 18 19

Day rfme (Hours)

(b) COP cycle

69

19171513

Day Time (Hours)

(c) COPse

119

04

035

03

025uQ 020v

015

01

005

0

7

151413

U 12~ 11

543

00000deg(1

bull__ J 1 bull ~_J

i195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

70

outlet increases

peak hours

71

~

c

bull~

~r f

~

72

CHAPTER 3

31 Introduction

73

900

100 A 28032005 RERCa

5 7 9 11 13 15 17 19Day Time (Hoursl

III11I

I I

19171513119

900800

E700 ~~ ~ ~

c 600 EJ ~

1~~ ~~ c 300 I d ~ ~

5 7

Day Time (Hours)

74- _- - _~----~~------

800700-NS 600

~- 500c0- 400to-0 300IIIC

- 200nI0V) 100

a ~~ 5 7

II

15 17 19

lIII

600

0

5 7 9 11 13 15 17 19

Day Time (Hours)

75

600

500-NE--= 400A-t

0~ 300 A nl0ent

0 0710 007

5 7 9 11 13 15 17 19Day Time (Hours)

600[J

1500 ~

1

5 9 11 13 15 17 19Day Time (Hours)

76

77

HVm2(Average on 7

years)

March 712 300 188

April 771 340 240

June 568 314 258

August 546 325 266

October 536 312 250

78

-__-------------------------__-_-

l

79

~

125

bed 2

13

i (a) March

bed 2

~bull I

o

-~

85

~[35 LL

115

105 -

G 95o-

1J

(b) April

80

10090-u 800bull

OJl 70J+Ill 60GIQ

EGI 50I-

40

30

bull ~- 11 115 12

Day Time (Hours)

i ~

--J~ -

125 13 I I

I

(c) June

(d) August

115

_____ ~I _ bull i bull -- __

10090 --u 800-~

lo 70s+IVlo 60~Q

E 50~1-

4030

11

81

10- 60QJa-S 50QJl-

40

3011 115 12

Day Time (Hours)

(e) October

I

-J ii

125

J13

(f) December

125 13

82

_-----------------------------------

83

--April--October

Day Time (Hours)

10 11 12 13 14 15 16 17 18 19

bullbull

9

87

16151413121110987654321a

-S0-UUctu

DayTime (Hours)

191817161514

131210 11

(b) COPcycle

9

1

08QI 06Ugt-uQ

0 04u

02

07 8

-J __L- __--L- __ _____ --

Marchampgt=June

=-October

17 18 191614 151310 11 1298

0605

04tv

lVIQ 030u

02

01

0

7

Day Time (Hours)

(c) COPsc

84

85

(b) April

1

Day Time (Hours)

7 l-_---__ ~__ ~ __ ~ __ ~__ ~_~__

1195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

(a) March

12

1194 1199 1204 1209 1214 1219 1224 1229 1234 1239

12115

a- i1e 105C1I3 10~ 95~X 9E 85~ 8

757

Day Time (Hours)

(c) June

-evaporator outlet

1199 1204 1209 1214 1219 1224 1229 1234 1239

13

125

12115

~ 1095

9

1194

-evaporator outlet

13513

G 125o~ 12bullE 11510

~ 11E 105 -

10

959 1- I

1195 12 1205 121 1215 122 1225 123 1235 124

DayTime (Hours)

(d) August

86

r

P 125-

951205 121 1215 122 1225 123 1235 124 1245 125 1255

Day Time (Hours)

(e) October

EQj 11I-

10

1184 1189

___ L __ J__ ~_~ __ J __ -L

1194 1199 1204 1209 1214 1219 1224 1229

Day Time (Hours)

(1) December

87

_----- --------------------------------~-_---

33 Summary

88

---__----------------------------_ -__ _

tt~r~~~~

~

i ~ t

+ bull

1

CHAPTER 4

41 Introduction

89

___________ _ bull ~ bull 4lt

~ or

Chapter 2

90

j bull

1

Designl

Design 2

time

1 1 - 1400s - -End of the

91

V5VIO

SE2

V8

Evaporator

[ __ dere~~~d~I ~ I

1_ - - - -- - - - L - - - - - - -

I ~~-~~-~~=~~-~ II ( Condenser I)

III V4

III

IIIIIII1IIIf

- - - - - - - -1_-_1__-_-_-__-_-_-_Dcooling

loadO

V2

VI

V3

tt

J

i

design 1

bull

12

1

v1

HollVaer ollilel

if Cooling load

CondQnCQf

S IGlcqe tank

design 1

92

I]I]

~ V4III

IfI]I]

I

IVlO

-Evaporator

_ _W _ _ _ __ __r - - -__C_

Condenser

IIIIIII

lXt=-It2 I

I ----- -r------J - 1 r P- -r

IVbull ~

I

i

f t

if~Iii~~

~ t~ ~

design 2

93

_I

(41)

be expressed asdT -

I

1

(42)

(43)

And

Tcr 1in = Twt bull

in case of design 1

94

(45)

(48)

(47)

TbedoUI = Tcrin

nA Idtunrlsettme cr

and

bull

~

95

- __--------__-----__-----------------

96

i~

85

35

255 7 9 11 13 15 17 19 21 23

23

21

~j

19171513

I Jl I I

1197

---L-~ ____~_~ __ ~ I __J_ __ ~ __-

9085r 801

353025

5

Day Time (Hoursl

97

--__----------------------------

7 9 11 13 15 17 19 21 23 25Day Time (Hours)

353025

5

lJ~~(J~ lOS~~

1 ~ 100~- 95~

~ 90r u 85

40353025

5 7 9 11 13 15 17 19 21

I

23

Day Time (Hours)

98

99

--------- _ -- -__-

80-u 700-lt11~ 60J+-(U

50lt11aE 40lt11I-

30

5

DayTIme (Hours)

100

25

23

21

-

21

11 13 15 17 19

Da~Time (Hours)

9

7

90858075-u 700-Q) 65-s 60+ro 55-Q)

353025

5

~fj~

~

95lt

1 90t 85

80u 750- 70lt1J 65J+ 60((

lt1J 55Q

E 50lt1J 45~

40353025

5

101

~

105100

9590

85uo 80-4J 75J 701n 65~ 60e 55Q) 50 r 45 r ~

J 25 __----bull _~-- L I _ __ _~__- Jbull__ -__ _J__

5 7 9 11 11) 15 17 19 21 23

- lt

Day Time Hours)

102

offer better values

103

-

(

10

9

8

7

3

2

1

0

8

~--- bull~ - ct- -+ - - ~ 11 ~

0 ~~ t ~~ ~

~ ~~ ~f

il l 1

- 30 collectors 1400s_---_---_-- __ ---_----- ~_~ __ ~ __ l___ _______ ___ __

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

104

_-----------------------____ --------

(b) COPcycle

11

9

080706

~ 05ugtu 04a0u 03

0201a

7

~

005

03

~ 02c

025

bull~ 015aou 01

8 10 12 14 16 18Day Time(Hours)

20 24

(c) COP soiarnet

105

232119171513

11

Day TIme (Hours)

9

co- e bull

CIClK)ta ~

I

II

OJ

o

7

025

005

1312

1110

9

3 8 7~ 65 - 5

4321o

)

~ 015ltII0

8 01

bullbullbullltu 02c

7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24

DayTime (Hours)

106

~

ltflLIA IIl lj l

l ~ ~ bull j 1

J l f l I ~-

-- gt1 I I -1-_ I I I I I I 1 I

95

85

-u 750-C1l

65s+(0 55C1lcE

45C1l

bullbullbullbull

35

25

~

tIt[~I bull

~I J II

J~tI

~

Day Time Hours)

107

and COP solarnet

(41 Q)

(49)

108

i

~

23

21

ta 11k

19

I 1 J

1715131197

10595

3525

5

Day Time (Hours)

109

I

109

8

7

i 6II- 5uui3 4

3

2

1

0

8 9 10 11 12 13 14 15 16 _ 17 18 19 20 21 22 23 24

Day TIme (Ihours)

Ii

08

07

06

~ 05ugt-u 04

Q

0u 03

02

01

O- 8

1 bull

(b) COP cycle

23

110

10 12 -14 16 18 20 22 24

(c) COPsolarnet

24222Q181614

111

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

10908

Q) 07tl 06e 05~0 04U 03

02010

8

IIIIIIIII

Day Time (Homs)

(b) COP cycle

03025

005

8 10 12 14 16 18

- -

20 22 24

Day Tillie (Hours)

(c) COPsolarnet

112

gti

r-i~

121110

98

i 7II- 6uu~ 5u

4~ 3

21

0

8

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

2422

1-

10

1

09

08

07

06

tugt- 05u0-0u 04

03

02

01

a8

(b) COP cycle

113

2422201816141210

8

02

005

o

025

Day Time (Hours)

(c) COPsolarnet

-t +

40353025

5 7 9 11 13 15 17 1921 23

Day Time (Hours)

114

13-design =de~ign2

1482 1492 1502 1512 1522 1532 1542 1552 1562i

8

12

Day Time (Hours)

14

12 _ =uniform 1400s ~~

I ~- i~l ~

( -P amp- d 4-- ~r ~ ~ 4~

) V~ P~~r - 9 ~ ~ I f ~lt7 1 -

~ (=~

[

13

Elt1lI-

9

8

7

1365 1369 1373 1377 1381 1385 1389 1393 1397 1401 1405 1409

DayTime (Hours)

II115

~l

~~

~

3530

~design 2 -design 1

r _

5 7 9 11 13 15 17 19 21 23

Day Time (Hours)

I

~

~ ~ 116

---L__ _______ ___

~f 7 gt

ff

I I~

fi

07

06

05gtu 04c~u 03QJ

02

01

a

5 6 7 8 9 10 11 12 13 14 15 16 17 18Day Time (Hours)

117

~I

H

I

cycle time ~400s

118

119

I~

i

I-~j~

120

L fj

iI ~

J

~

CHAPTER 5

Thermal Collectors

~

I___L121

j

in Dhaka

dt l UCPiAcp]

122

(5 1 )

(52)

SolarI

Tlterloal Co8ector

(

household use

123

I _~

~Obil - Q

~ ~T ------[lt----------~

ll I~V4

___-L

l

~

(54)

124

-P~_ __ l J

~~ ~

I ~i~

- -- ~ r

~-i

125

125 13

36

33

21

186 8 ~o 12 14

Ibull

9 12

Day Time (Hoursl-

15 18

11bull

126

1 need

i

127

f

q

IjHlIIIiIIij~I

CHAPTER 6

~

bull

of the chiller

875degC

129

IIjf

performance

130

bull

peak hours

I

liters of water

bull

d

performance

131

compression chiller

system

132

~

d

References

133

II

d

J 50-62

134

J

135

J

136

Journal

~

137

_------- _- _ --_ _ __ _---------------------

IIi

-

138

00000001
00000002
00000003
00000004
00000005
00000006
00000007
00000008
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00000161

Page 3: Full Thesis - Bangladesh University of Engineering and ...

Member

~ I 7bull _

-

Member

c bull

)n-~~7bull~_(_~-_v_) _

)

Member (External)

iii

--- __ ----~-----_ _

DEDICATION

tV

~A~Rifat Ara Rouf

12th July 2014

v

___ ctr --- ---- _ -

-__~_- - ----_-_ _-

Acknowledgement

VI

~---__- -----__ __

and advice

understanding

Vll

_ _--_--- -

Abstract

heating purposes

VIp

CONTENTS

Board of Examiners

Acknowledgements

Abstract

Nomenclature-

List of Tables

List of Figures

ii

v

vi

viii

xiii

xiv

xv

CHAPTERl (

124 Time Line

Cycle

IX

1

2

3

5

6

7

8

10

11

13

14

17

Refrigeration Cycle

CHAPTER 2

23 Formulation

231 Solar System

Cycle Time

25 Summary

x

18

26

27

353537

3738

39

4041

45

4750

51

54

6071

r ~-I

I j

------

CHAPTER 3

Dhaka

31 Introduction

33 Summary

CHAPTER 4

System Performance

41 Introduction

45 Summary

CHAPTERS

54 Summary

CHAPTER 6

Xl

73

88

89

899094

95

119

121

122

124

127

128

-

Future work

References

Xli

131

133137

r

Nomenclature

A Area (m2)

XliI

------------- __--------~ -_- --- _- _ -

I

r~-I

i

List of Tables

-

XIV

94

I

List of Figures

II

Figure 11

Figure 12

Figure 13

Figure 14

Figure 15

Figure 16

Figure 17

Figure 18

[2009]

cooling system

[2009]

xv

15

16

19

20

21

22

23

24

25

28

[2005])

April

optimum cycle time

XVI

Figure 24

Figure 25

(

cycle 800s

57

58

59

62

Figure 27

Figure 28

Figure 29

140h

then decreasing

cooling capacity

XVII

62

63

64

66

rttI

-

Figure210

Figure 710

Figure 211

Figure 212

Figure 31

hours

cycle -

(a) March

(b) April

(c) June

(d) August

68

69

70

74

75

Figure 31

bullbullbull

(e) October

(t) December

March

XVIII

76

80

months (a)CACC

months (c) COPse

XIX

gt

time 1400s

xx

~I

design 1

for design 2

cycle

COPsolarnet

XXI

104

105

106

107

109

110

III

111

Figure 412

Figure 413

Figure 414

Figure 415

Figure 4J5

COP cycle

COPsolarnet

cooling capacity

time

Figure 416

Figure 417

Figure 418

design 1

design 2

XXII

116

117

118

b

Figure 419

Figure 51

Figure 52

Figure 53

Figure 54

Figure 55

1400s

collector and tank

solar coupling

household

XXIII

CHAPTER

Introduction

11 Introduction

cycle begins again

I

2

--

f

3

e

4

I

i1

Japan

conditioning

cooking

residences

perishable goods

Kettering of GM

distribution

5

Superior Arizona

surface phenomenon

the adsorbate

6

t

--l

7

isotherm etc

8

f

9

(v) Low viscosity

water etc

10

-

io-(

11

I~

f

IIII[

f

I

i

1

12

I

t f

I

i

~~

13

lt A ~ -

of the liquid

cycles lie around 3

14

f

CompressorQpor

~vaporator

Expansion

Condenser

Uquid + porValve

15

-Isobars

( ~

t

~

1

~-

-I--

1 _

1-

f

----4-isobar

1gt1 Y Liquid

--_ 1 Vapor

High Pr

i NH3 Vapour

VapQufc ~

~~n~~t~

Q T j1gt~

1 1~ ~-~- ~ -

Strong Absorb~r -

NHJ solution

16

(Figurel3)

17

18

-~

LoP

II

I

~~

~

-lIT

-

AdsomedI

vapour

Ie

-~oCondensel

heat pumping [2014J

19

~

--

~

LnP

-lff

Q-

ht Qcs~---II

IIIII

bullbullII_~- -

20--_bullbull_--------_- -- _ --_-

-~ -

-

LnP

~

COtliBS + ltii

tlqmssumtttibn -lIT

heat pumping [2014]

21

LnP

-lIT

QcsTcs ===

IIIIIIIIIII_---

heat pumping [2014]

22

I ~ _

I -

i ~i

Ci Pc- bull Wo- InP

bull

PE

I)-

T-o

23

vm

Condenser

SE2

V8

EvaporatorV2 i

II i

r-------

VIrt

i =

Cooling load

system

24

deg IIIIII V4

vs

r -~---~- deg

VI IIi

~

i (IIi= Ii~Ii~ 0

~

V2 V8

Evaporator

adsorbero

SEl

25

installed

process)

26

~

27

8x+amp

lnP

~ ~

a2e a1 a1

bullbull1--T

28

29

)~ 737t tlOr~ lir ~ ~ t 4~24l

bull~f

1~8 234

~

]f~ 123~

o10 20 30 40 50 60 70 80

40

bullbullu30 L

4JI-

2~I-~p

fi20 -

1-ec~gt01)

10 bullbullCd3Cd

r

0

30

et)c~- (JJ-~deg0o~u

5

~

Heatrejected

VIO

Condenser

V8----

Evaporator

r------- J~~ ~_~ IIIIII V4

VI

V2

~

i=1

I

31

---_-bull_----_ - --

32

--_ bull__-----~----------__-__ __ _- -

jiJ

~iAff~l

CONO

(b) ModcB

CONOl

CONOI

(a) ModeA

33

denoted as mode D

mode A

34--_bull_ bull_-----------------__- _

Sumanthy [2004]

35

36

Figure 112

mathematically

ice making purpose

37

~

f ~

lower heat source

38

CHAPTER 2

ofDhaka

39

-~--_ ---_ _ _

40

I

41

-_ __-__-----__----__ __ ~

V4btgt~c- ()- ~0

VIO 00U-

5

VI

- ~~

bull t~

42

(23)

by

transfer fluid

(24)

43

(27)

(26)

(25)

loops

ToUl

state q

(29)

calculated by

Ps(T) = 13332 e [183-3820 1(1-461)] (21 0)

44

(213)

(212)

endojcyclelime

endofcycletime

cycle

number of collector

ao -15587 bo -65314

aj 015915 bl 072452E-Ol

a2 -050612E-03 b2 -023951 E-03

a3 053290E-06 b3 025493E-06

231 Solar System

45

expressed as

where

(214)

(215)

(2 f6)

46

(217)

47

900800

f1E 700

~ 600c2 500+(U-o 400IIIs - 300_(U

0 200til

100o

bull

[l 06042009 RERC [JI

5 7 9 11 13 17 19

Day Time (Hoursl

April

48

49

(218)

am ~--~+-~-~ In ----------- 2 2 Daylength

50

~

i

51

I

161412

4

2

o

I

T 8 9 -10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

52

06

05

Gl 04]~ 03Ou 02

01

o

7 8 9 10 11 12 13 14 15 16 17 18 19

DayTIme (Hours)

03

025

02uIII0 0150u

01

20 collectors

I _~_L L__

i

8 9 10 11 12 13 14 15Day Time (Hours)

16 17 18 19

53

I

-

54

II

55

19

6 i-n bull ~

1715

13Day Time (Hours)

119

Day TIme (Hours)

8 9 10 11 12 13 14 15 16 17 -18 19

18

16

14

12

~ 10lII

Uu 8ctu

6

4

2

0

7

12

j 1~~ lt~

1 08 QI) U gtu 06

Q

0u04

02

0

7

56

191715

13

DayTime (Hours)

10 11 12 13 14 15 16 17 18 19

9

--r bull ~ --_- ---~~-~-~--~~~~- ~ 1~

~ ~

bullbull

8

7

a

03

04

01

u0 028

035

03

005

0

7

DayTime (Hours)

57

12 13

Daynme (Hours)

f f

~

~ 0 bull 0 Q

bull g -- ~

~

bull bull I bull

12 13

Day Time (Hours)

58

~gt =

1312

po 11-10

9

8

deg7

6

- 22collectors1000s

11191195 12 1205 121 1215 122 1225 123 1235

Day Time (Hours)

59

li

i ~

60

the sunset hours

(i) 800s

(ii) 800s 140 - 185 h 20 scycle

61

110100

P 90-~ 80J10 70~ 60~ 50I-

4030

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day TIme (Hours)

110 100 ~

4030

17 19

140h

62

decreasing gt I11i

1917151311

DayTime (Hours)

97

~ 100d1

f(

U 900-lt1l 80l+ 70(ll lt1lQ 60E 50

4030

5

Il

1917

uniform cycle 800s

9

11 13 15

Day Time (Hours)

()fJ

~~ 13

121110

9~ 8 7

7

63

1

08

41 06ugtua0 04u

02

o

7 8 9 10 11 12 13 14 15 16 i7 18 19

Day Time (Hours)

05

04

u 03VIa

0u 02

01

0

7 9 11 13

__ I

64

~

(J

1ltlt

1lt ~

lt)lt

(OC)(i) Uniform 95 87 71 119 065 0315

800s(ii) Non- 95 87 71 119 057 0314

uniform800s

(iii)Non- 93 85 74 118 056 0311uniform550s

65

12115

11

U 105a-~ 101i 95~ 9E~ 85

8757

1195

12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

r Co

66

67

II

U 100o- 90 bullbullJ 80tu~ 70~ 60

~ 504030

5 7 9 11 13 15 17 19Day TIme (Hours)

fr

Ii ~

110

40

30

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

68

Day Time (Hours)

-__-~--~-

(a) CACC

__ ~_L_~_~_

9 10 11 12 13 14 15 16 17 18 19

09

08

07

~ 06gtrr 058 04

03

02

01 -

o

13121110- 9

S 8 7-u 6uot 5u 4

3210

7 8

7 8 9 10 11 1213 14 15 16 17 18 19

Day rfme (Hours)

(b) COP cycle

69

19171513

Day Time (Hours)

(c) COPse

119

04

035

03

025uQ 020v

015

01

005

0

7

151413

U 12~ 11

543

00000deg(1

bull__ J 1 bull ~_J

i195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

70

outlet increases

peak hours

71

~

c

bull~

~r f

~

72

CHAPTER 3

31 Introduction

73

900

100 A 28032005 RERCa

5 7 9 11 13 15 17 19Day Time (Hoursl

III11I

I I

19171513119

900800

E700 ~~ ~ ~

c 600 EJ ~

1~~ ~~ c 300 I d ~ ~

5 7

Day Time (Hours)

74- _- - _~----~~------

800700-NS 600

~- 500c0- 400to-0 300IIIC

- 200nI0V) 100

a ~~ 5 7

II

15 17 19

lIII

600

0

5 7 9 11 13 15 17 19

Day Time (Hours)

75

600

500-NE--= 400A-t

0~ 300 A nl0ent

0 0710 007

5 7 9 11 13 15 17 19Day Time (Hours)

600[J

1500 ~

1

5 9 11 13 15 17 19Day Time (Hours)

76

77

HVm2(Average on 7

years)

March 712 300 188

April 771 340 240

June 568 314 258

August 546 325 266

October 536 312 250

78

-__-------------------------__-_-

l

79

~

125

bed 2

13

i (a) March

bed 2

~bull I

o

-~

85

~[35 LL

115

105 -

G 95o-

1J

(b) April

80

10090-u 800bull

OJl 70J+Ill 60GIQ

EGI 50I-

40

30

bull ~- 11 115 12

Day Time (Hours)

i ~

--J~ -

125 13 I I

I

(c) June

(d) August

115

_____ ~I _ bull i bull -- __

10090 --u 800-~

lo 70s+IVlo 60~Q

E 50~1-

4030

11

81

10- 60QJa-S 50QJl-

40

3011 115 12

Day Time (Hours)

(e) October

I

-J ii

125

J13

(f) December

125 13

82

_-----------------------------------

83

--April--October

Day Time (Hours)

10 11 12 13 14 15 16 17 18 19

bullbull

9

87

16151413121110987654321a

-S0-UUctu

DayTime (Hours)

191817161514

131210 11

(b) COPcycle

9

1

08QI 06Ugt-uQ

0 04u

02

07 8

-J __L- __--L- __ _____ --

Marchampgt=June

=-October

17 18 191614 151310 11 1298

0605

04tv

lVIQ 030u

02

01

0

7

Day Time (Hours)

(c) COPsc

84

85

(b) April

1

Day Time (Hours)

7 l-_---__ ~__ ~ __ ~ __ ~__ ~_~__

1195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

(a) March

12

1194 1199 1204 1209 1214 1219 1224 1229 1234 1239

12115

a- i1e 105C1I3 10~ 95~X 9E 85~ 8

757

Day Time (Hours)

(c) June

-evaporator outlet

1199 1204 1209 1214 1219 1224 1229 1234 1239

13

125

12115

~ 1095

9

1194

-evaporator outlet

13513

G 125o~ 12bullE 11510

~ 11E 105 -

10

959 1- I

1195 12 1205 121 1215 122 1225 123 1235 124

DayTime (Hours)

(d) August

86

r

P 125-

951205 121 1215 122 1225 123 1235 124 1245 125 1255

Day Time (Hours)

(e) October

EQj 11I-

10

1184 1189

___ L __ J__ ~_~ __ J __ -L

1194 1199 1204 1209 1214 1219 1224 1229

Day Time (Hours)

(1) December

87

_----- --------------------------------~-_---

33 Summary

88

---__----------------------------_ -__ _

tt~r~~~~

~

i ~ t

+ bull

1

CHAPTER 4

41 Introduction

89

___________ _ bull ~ bull 4lt

~ or

Chapter 2

90

j bull

1

Designl

Design 2

time

1 1 - 1400s - -End of the

91

V5VIO

SE2

V8

Evaporator

[ __ dere~~~d~I ~ I

1_ - - - -- - - - L - - - - - - -

I ~~-~~-~~=~~-~ II ( Condenser I)

III V4

III

IIIIIII1IIIf

- - - - - - - -1_-_1__-_-_-__-_-_-_Dcooling

loadO

V2

VI

V3

tt

J

i

design 1

bull

12

1

v1

HollVaer ollilel

if Cooling load

CondQnCQf

S IGlcqe tank

design 1

92

I]I]

~ V4III

IfI]I]

I

IVlO

-Evaporator

_ _W _ _ _ __ __r - - -__C_

Condenser

IIIIIII

lXt=-It2 I

I ----- -r------J - 1 r P- -r

IVbull ~

I

i

f t

if~Iii~~

~ t~ ~

design 2

93

_I

(41)

be expressed asdT -

I

1

(42)

(43)

And

Tcr 1in = Twt bull

in case of design 1

94

(45)

(48)

(47)

TbedoUI = Tcrin

nA Idtunrlsettme cr

and

bull

~

95

- __--------__-----__-----------------

96

i~

85

35

255 7 9 11 13 15 17 19 21 23

23

21

~j

19171513

I Jl I I

1197

---L-~ ____~_~ __ ~ I __J_ __ ~ __-

9085r 801

353025

5

Day Time (Hoursl

97

--__----------------------------

7 9 11 13 15 17 19 21 23 25Day Time (Hours)

353025

5

lJ~~(J~ lOS~~

1 ~ 100~- 95~

~ 90r u 85

40353025

5 7 9 11 13 15 17 19 21

I

23

Day Time (Hours)

98

99

--------- _ -- -__-

80-u 700-lt11~ 60J+-(U

50lt11aE 40lt11I-

30

5

DayTIme (Hours)

100

25

23

21

-

21

11 13 15 17 19

Da~Time (Hours)

9

7

90858075-u 700-Q) 65-s 60+ro 55-Q)

353025

5

~fj~

~

95lt

1 90t 85

80u 750- 70lt1J 65J+ 60((

lt1J 55Q

E 50lt1J 45~

40353025

5

101

~

105100

9590

85uo 80-4J 75J 701n 65~ 60e 55Q) 50 r 45 r ~

J 25 __----bull _~-- L I _ __ _~__- Jbull__ -__ _J__

5 7 9 11 11) 15 17 19 21 23

- lt

Day Time Hours)

102

offer better values

103

-

(

10

9

8

7

3

2

1

0

8

~--- bull~ - ct- -+ - - ~ 11 ~

0 ~~ t ~~ ~

~ ~~ ~f

il l 1

- 30 collectors 1400s_---_---_-- __ ---_----- ~_~ __ ~ __ l___ _______ ___ __

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

104

_-----------------------____ --------

(b) COPcycle

11

9

080706

~ 05ugtu 04a0u 03

0201a

7

~

005

03

~ 02c

025

bull~ 015aou 01

8 10 12 14 16 18Day Time(Hours)

20 24

(c) COP soiarnet

105

232119171513

11

Day TIme (Hours)

9

co- e bull

CIClK)ta ~

I

II

OJ

o

7

025

005

1312

1110

9

3 8 7~ 65 - 5

4321o

)

~ 015ltII0

8 01

bullbullbullltu 02c

7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24

DayTime (Hours)

106

~

ltflLIA IIl lj l

l ~ ~ bull j 1

J l f l I ~-

-- gt1 I I -1-_ I I I I I I 1 I

95

85

-u 750-C1l

65s+(0 55C1lcE

45C1l

bullbullbullbull

35

25

~

tIt[~I bull

~I J II

J~tI

~

Day Time Hours)

107

and COP solarnet

(41 Q)

(49)

108

i

~

23

21

ta 11k

19

I 1 J

1715131197

10595

3525

5

Day Time (Hours)

109

I

109

8

7

i 6II- 5uui3 4

3

2

1

0

8 9 10 11 12 13 14 15 16 _ 17 18 19 20 21 22 23 24

Day TIme (Ihours)

Ii

08

07

06

~ 05ugt-u 04

Q

0u 03

02

01

O- 8

1 bull

(b) COP cycle

23

110

10 12 -14 16 18 20 22 24

(c) COPsolarnet

24222Q181614

111

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

10908

Q) 07tl 06e 05~0 04U 03

02010

8

IIIIIIIII

Day Time (Homs)

(b) COP cycle

03025

005

8 10 12 14 16 18

- -

20 22 24

Day Tillie (Hours)

(c) COPsolarnet

112

gti

r-i~

121110

98

i 7II- 6uu~ 5u

4~ 3

21

0

8

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

2422

1-

10

1

09

08

07

06

tugt- 05u0-0u 04

03

02

01

a8

(b) COP cycle

113

2422201816141210

8

02

005

o

025

Day Time (Hours)

(c) COPsolarnet

-t +

40353025

5 7 9 11 13 15 17 1921 23

Day Time (Hours)

114

13-design =de~ign2

1482 1492 1502 1512 1522 1532 1542 1552 1562i

8

12

Day Time (Hours)

14

12 _ =uniform 1400s ~~

I ~- i~l ~

( -P amp- d 4-- ~r ~ ~ 4~

) V~ P~~r - 9 ~ ~ I f ~lt7 1 -

~ (=~

[

13

Elt1lI-

9

8

7

1365 1369 1373 1377 1381 1385 1389 1393 1397 1401 1405 1409

DayTime (Hours)

II115

~l

~~

~

3530

~design 2 -design 1

r _

5 7 9 11 13 15 17 19 21 23

Day Time (Hours)

I

~

~ ~ 116

---L__ _______ ___

~f 7 gt

ff

I I~

fi

07

06

05gtu 04c~u 03QJ

02

01

a

5 6 7 8 9 10 11 12 13 14 15 16 17 18Day Time (Hours)

117

~I

H

I

cycle time ~400s

118

119

I~

i

I-~j~

120

L fj

iI ~

J

~

CHAPTER 5

Thermal Collectors

~

I___L121

j

in Dhaka

dt l UCPiAcp]

122

(5 1 )

(52)

SolarI

Tlterloal Co8ector

(

household use

123

I _~

~Obil - Q

~ ~T ------[lt----------~

ll I~V4

___-L

l

~

(54)

124

-P~_ __ l J

~~ ~

I ~i~

- -- ~ r

~-i

125

125 13

36

33

21

186 8 ~o 12 14

Ibull

9 12

Day Time (Hoursl-

15 18

11bull

126

1 need

i

127

f

q

IjHlIIIiIIij~I

CHAPTER 6

~

bull

of the chiller

875degC

129

IIjf

performance

130

bull

peak hours

I

liters of water

bull

d

performance

131

compression chiller

system

132

~

d

References

133

II

d

J 50-62

134

J

135

J

136

Journal

~

137

_------- _- _ --_ _ __ _---------------------

IIi

-

138

00000001
00000002
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00000004
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00000006
00000007
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00000161

Page 4: Full Thesis - Bangladesh University of Engineering and ...

--- __ ----~-----_ _

DEDICATION

tV

~A~Rifat Ara Rouf

12th July 2014

v

___ ctr --- ---- _ -

-__~_- - ----_-_ _-

Acknowledgement

VI

~---__- -----__ __

and advice

understanding

Vll

_ _--_--- -

Abstract

heating purposes

VIp

CONTENTS

Board of Examiners

Acknowledgements

Abstract

Nomenclature-

List of Tables

List of Figures

ii

v

vi

viii

xiii

xiv

xv

CHAPTERl (

124 Time Line

Cycle

IX

1

2

3

5

6

7

8

10

11

13

14

17

Refrigeration Cycle

CHAPTER 2

23 Formulation

231 Solar System

Cycle Time

25 Summary

x

18

26

27

353537

3738

39

4041

45

4750

51

54

6071

r ~-I

I j

------

CHAPTER 3

Dhaka

31 Introduction

33 Summary

CHAPTER 4

System Performance

41 Introduction

45 Summary

CHAPTERS

54 Summary

CHAPTER 6

Xl

73

88

89

899094

95

119

121

122

124

127

128

-

Future work

References

Xli

131

133137

r

Nomenclature

A Area (m2)

XliI

------------- __--------~ -_- --- _- _ -

I

r~-I

i

List of Tables

-

XIV

94

I

List of Figures

II

Figure 11

Figure 12

Figure 13

Figure 14

Figure 15

Figure 16

Figure 17

Figure 18

[2009]

cooling system

[2009]

xv

15

16

19

20

21

22

23

24

25

28

[2005])

April

optimum cycle time

XVI

Figure 24

Figure 25

(

cycle 800s

57

58

59

62

Figure 27

Figure 28

Figure 29

140h

then decreasing

cooling capacity

XVII

62

63

64

66

rttI

-

Figure210

Figure 710

Figure 211

Figure 212

Figure 31

hours

cycle -

(a) March

(b) April

(c) June

(d) August

68

69

70

74

75

Figure 31

bullbullbull

(e) October

(t) December

March

XVIII

76

80

months (a)CACC

months (c) COPse

XIX

gt

time 1400s

xx

~I

design 1

for design 2

cycle

COPsolarnet

XXI

104

105

106

107

109

110

III

111

Figure 412

Figure 413

Figure 414

Figure 415

Figure 4J5

COP cycle

COPsolarnet

cooling capacity

time

Figure 416

Figure 417

Figure 418

design 1

design 2

XXII

116

117

118

b

Figure 419

Figure 51

Figure 52

Figure 53

Figure 54

Figure 55

1400s

collector and tank

solar coupling

household

XXIII

CHAPTER

Introduction

11 Introduction

cycle begins again

I

2

--

f

3

e

4

I

i1

Japan

conditioning

cooking

residences

perishable goods

Kettering of GM

distribution

5

Superior Arizona

surface phenomenon

the adsorbate

6

t

--l

7

isotherm etc

8

f

9

(v) Low viscosity

water etc

10

-

io-(

11

I~

f

IIII[

f

I

i

1

12

I

t f

I

i

~~

13

lt A ~ -

of the liquid

cycles lie around 3

14

f

CompressorQpor

~vaporator

Expansion

Condenser

Uquid + porValve

15

-Isobars

( ~

t

~

1

~-

-I--

1 _

1-

f

----4-isobar

1gt1 Y Liquid

--_ 1 Vapor

High Pr

i NH3 Vapour

VapQufc ~

~~n~~t~

Q T j1gt~

1 1~ ~-~- ~ -

Strong Absorb~r -

NHJ solution

16

(Figurel3)

17

18

-~

LoP

II

I

~~

~

-lIT

-

AdsomedI

vapour

Ie

-~oCondensel

heat pumping [2014J

19

~

--

~

LnP

-lff

Q-

ht Qcs~---II

IIIII

bullbullII_~- -

20--_bullbull_--------_- -- _ --_-

-~ -

-

LnP

~

COtliBS + ltii

tlqmssumtttibn -lIT

heat pumping [2014]

21

LnP

-lIT

QcsTcs ===

IIIIIIIIIII_---

heat pumping [2014]

22

I ~ _

I -

i ~i

Ci Pc- bull Wo- InP

bull

PE

I)-

T-o

23

vm

Condenser

SE2

V8

EvaporatorV2 i

II i

r-------

VIrt

i =

Cooling load

system

24

deg IIIIII V4

vs

r -~---~- deg

VI IIi

~

i (IIi= Ii~Ii~ 0

~

V2 V8

Evaporator

adsorbero

SEl

25

installed

process)

26

~

27

8x+amp

lnP

~ ~

a2e a1 a1

bullbull1--T

28

29

)~ 737t tlOr~ lir ~ ~ t 4~24l

bull~f

1~8 234

~

]f~ 123~

o10 20 30 40 50 60 70 80

40

bullbullu30 L

4JI-

2~I-~p

fi20 -

1-ec~gt01)

10 bullbullCd3Cd

r

0

30

et)c~- (JJ-~deg0o~u

5

~

Heatrejected

VIO

Condenser

V8----

Evaporator

r------- J~~ ~_~ IIIIII V4

VI

V2

~

i=1

I

31

---_-bull_----_ - --

32

--_ bull__-----~----------__-__ __ _- -

jiJ

~iAff~l

CONO

(b) ModcB

CONOl

CONOI

(a) ModeA

33

denoted as mode D

mode A

34--_bull_ bull_-----------------__- _

Sumanthy [2004]

35

36

Figure 112

mathematically

ice making purpose

37

~

f ~

lower heat source

38

CHAPTER 2

ofDhaka

39

-~--_ ---_ _ _

40

I

41

-_ __-__-----__----__ __ ~

V4btgt~c- ()- ~0

VIO 00U-

5

VI

- ~~

bull t~

42

(23)

by

transfer fluid

(24)

43

(27)

(26)

(25)

loops

ToUl

state q

(29)

calculated by

Ps(T) = 13332 e [183-3820 1(1-461)] (21 0)

44

(213)

(212)

endojcyclelime

endofcycletime

cycle

number of collector

ao -15587 bo -65314

aj 015915 bl 072452E-Ol

a2 -050612E-03 b2 -023951 E-03

a3 053290E-06 b3 025493E-06

231 Solar System

45

expressed as

where

(214)

(215)

(2 f6)

46

(217)

47

900800

f1E 700

~ 600c2 500+(U-o 400IIIs - 300_(U

0 200til

100o

bull

[l 06042009 RERC [JI

5 7 9 11 13 17 19

Day Time (Hoursl

April

48

49

(218)

am ~--~+-~-~ In ----------- 2 2 Daylength

50

~

i

51

I

161412

4

2

o

I

T 8 9 -10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

52

06

05

Gl 04]~ 03Ou 02

01

o

7 8 9 10 11 12 13 14 15 16 17 18 19

DayTIme (Hours)

03

025

02uIII0 0150u

01

20 collectors

I _~_L L__

i

8 9 10 11 12 13 14 15Day Time (Hours)

16 17 18 19

53

I

-

54

II

55

19

6 i-n bull ~

1715

13Day Time (Hours)

119

Day TIme (Hours)

8 9 10 11 12 13 14 15 16 17 -18 19

18

16

14

12

~ 10lII

Uu 8ctu

6

4

2

0

7

12

j 1~~ lt~

1 08 QI) U gtu 06

Q

0u04

02

0

7

56

191715

13

DayTime (Hours)

10 11 12 13 14 15 16 17 18 19

9

--r bull ~ --_- ---~~-~-~--~~~~- ~ 1~

~ ~

bullbull

8

7

a

03

04

01

u0 028

035

03

005

0

7

DayTime (Hours)

57

12 13

Daynme (Hours)

f f

~

~ 0 bull 0 Q

bull g -- ~

~

bull bull I bull

12 13

Day Time (Hours)

58

~gt =

1312

po 11-10

9

8

deg7

6

- 22collectors1000s

11191195 12 1205 121 1215 122 1225 123 1235

Day Time (Hours)

59

li

i ~

60

the sunset hours

(i) 800s

(ii) 800s 140 - 185 h 20 scycle

61

110100

P 90-~ 80J10 70~ 60~ 50I-

4030

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day TIme (Hours)

110 100 ~

4030

17 19

140h

62

decreasing gt I11i

1917151311

DayTime (Hours)

97

~ 100d1

f(

U 900-lt1l 80l+ 70(ll lt1lQ 60E 50

4030

5

Il

1917

uniform cycle 800s

9

11 13 15

Day Time (Hours)

()fJ

~~ 13

121110

9~ 8 7

7

63

1

08

41 06ugtua0 04u

02

o

7 8 9 10 11 12 13 14 15 16 i7 18 19

Day Time (Hours)

05

04

u 03VIa

0u 02

01

0

7 9 11 13

__ I

64

~

(J

1ltlt

1lt ~

lt)lt

(OC)(i) Uniform 95 87 71 119 065 0315

800s(ii) Non- 95 87 71 119 057 0314

uniform800s

(iii)Non- 93 85 74 118 056 0311uniform550s

65

12115

11

U 105a-~ 101i 95~ 9E~ 85

8757

1195

12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

r Co

66

67

II

U 100o- 90 bullbullJ 80tu~ 70~ 60

~ 504030

5 7 9 11 13 15 17 19Day TIme (Hours)

fr

Ii ~

110

40

30

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

68

Day Time (Hours)

-__-~--~-

(a) CACC

__ ~_L_~_~_

9 10 11 12 13 14 15 16 17 18 19

09

08

07

~ 06gtrr 058 04

03

02

01 -

o

13121110- 9

S 8 7-u 6uot 5u 4

3210

7 8

7 8 9 10 11 1213 14 15 16 17 18 19

Day rfme (Hours)

(b) COP cycle

69

19171513

Day Time (Hours)

(c) COPse

119

04

035

03

025uQ 020v

015

01

005

0

7

151413

U 12~ 11

543

00000deg(1

bull__ J 1 bull ~_J

i195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

70

outlet increases

peak hours

71

~

c

bull~

~r f

~

72

CHAPTER 3

31 Introduction

73

900

100 A 28032005 RERCa

5 7 9 11 13 15 17 19Day Time (Hoursl

III11I

I I

19171513119

900800

E700 ~~ ~ ~

c 600 EJ ~

1~~ ~~ c 300 I d ~ ~

5 7

Day Time (Hours)

74- _- - _~----~~------

800700-NS 600

~- 500c0- 400to-0 300IIIC

- 200nI0V) 100

a ~~ 5 7

II

15 17 19

lIII

600

0

5 7 9 11 13 15 17 19

Day Time (Hours)

75

600

500-NE--= 400A-t

0~ 300 A nl0ent

0 0710 007

5 7 9 11 13 15 17 19Day Time (Hours)

600[J

1500 ~

1

5 9 11 13 15 17 19Day Time (Hours)

76

77

HVm2(Average on 7

years)

March 712 300 188

April 771 340 240

June 568 314 258

August 546 325 266

October 536 312 250

78

-__-------------------------__-_-

l

79

~

125

bed 2

13

i (a) March

bed 2

~bull I

o

-~

85

~[35 LL

115

105 -

G 95o-

1J

(b) April

80

10090-u 800bull

OJl 70J+Ill 60GIQ

EGI 50I-

40

30

bull ~- 11 115 12

Day Time (Hours)

i ~

--J~ -

125 13 I I

I

(c) June

(d) August

115

_____ ~I _ bull i bull -- __

10090 --u 800-~

lo 70s+IVlo 60~Q

E 50~1-

4030

11

81

10- 60QJa-S 50QJl-

40

3011 115 12

Day Time (Hours)

(e) October

I

-J ii

125

J13

(f) December

125 13

82

_-----------------------------------

83

--April--October

Day Time (Hours)

10 11 12 13 14 15 16 17 18 19

bullbull

9

87

16151413121110987654321a

-S0-UUctu

DayTime (Hours)

191817161514

131210 11

(b) COPcycle

9

1

08QI 06Ugt-uQ

0 04u

02

07 8

-J __L- __--L- __ _____ --

Marchampgt=June

=-October

17 18 191614 151310 11 1298

0605

04tv

lVIQ 030u

02

01

0

7

Day Time (Hours)

(c) COPsc

84

85

(b) April

1

Day Time (Hours)

7 l-_---__ ~__ ~ __ ~ __ ~__ ~_~__

1195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

(a) March

12

1194 1199 1204 1209 1214 1219 1224 1229 1234 1239

12115

a- i1e 105C1I3 10~ 95~X 9E 85~ 8

757

Day Time (Hours)

(c) June

-evaporator outlet

1199 1204 1209 1214 1219 1224 1229 1234 1239

13

125

12115

~ 1095

9

1194

-evaporator outlet

13513

G 125o~ 12bullE 11510

~ 11E 105 -

10

959 1- I

1195 12 1205 121 1215 122 1225 123 1235 124

DayTime (Hours)

(d) August

86

r

P 125-

951205 121 1215 122 1225 123 1235 124 1245 125 1255

Day Time (Hours)

(e) October

EQj 11I-

10

1184 1189

___ L __ J__ ~_~ __ J __ -L

1194 1199 1204 1209 1214 1219 1224 1229

Day Time (Hours)

(1) December

87

_----- --------------------------------~-_---

33 Summary

88

---__----------------------------_ -__ _

tt~r~~~~

~

i ~ t

+ bull

1

CHAPTER 4

41 Introduction

89

___________ _ bull ~ bull 4lt

~ or

Chapter 2

90

j bull

1

Designl

Design 2

time

1 1 - 1400s - -End of the

91

V5VIO

SE2

V8

Evaporator

[ __ dere~~~d~I ~ I

1_ - - - -- - - - L - - - - - - -

I ~~-~~-~~=~~-~ II ( Condenser I)

III V4

III

IIIIIII1IIIf

- - - - - - - -1_-_1__-_-_-__-_-_-_Dcooling

loadO

V2

VI

V3

tt

J

i

design 1

bull

12

1

v1

HollVaer ollilel

if Cooling load

CondQnCQf

S IGlcqe tank

design 1

92

I]I]

~ V4III

IfI]I]

I

IVlO

-Evaporator

_ _W _ _ _ __ __r - - -__C_

Condenser

IIIIIII

lXt=-It2 I

I ----- -r------J - 1 r P- -r

IVbull ~

I

i

f t

if~Iii~~

~ t~ ~

design 2

93

_I

(41)

be expressed asdT -

I

1

(42)

(43)

And

Tcr 1in = Twt bull

in case of design 1

94

(45)

(48)

(47)

TbedoUI = Tcrin

nA Idtunrlsettme cr

and

bull

~

95

- __--------__-----__-----------------

96

i~

85

35

255 7 9 11 13 15 17 19 21 23

23

21

~j

19171513

I Jl I I

1197

---L-~ ____~_~ __ ~ I __J_ __ ~ __-

9085r 801

353025

5

Day Time (Hoursl

97

--__----------------------------

7 9 11 13 15 17 19 21 23 25Day Time (Hours)

353025

5

lJ~~(J~ lOS~~

1 ~ 100~- 95~

~ 90r u 85

40353025

5 7 9 11 13 15 17 19 21

I

23

Day Time (Hours)

98

99

--------- _ -- -__-

80-u 700-lt11~ 60J+-(U

50lt11aE 40lt11I-

30

5

DayTIme (Hours)

100

25

23

21

-

21

11 13 15 17 19

Da~Time (Hours)

9

7

90858075-u 700-Q) 65-s 60+ro 55-Q)

353025

5

~fj~

~

95lt

1 90t 85

80u 750- 70lt1J 65J+ 60((

lt1J 55Q

E 50lt1J 45~

40353025

5

101

~

105100

9590

85uo 80-4J 75J 701n 65~ 60e 55Q) 50 r 45 r ~

J 25 __----bull _~-- L I _ __ _~__- Jbull__ -__ _J__

5 7 9 11 11) 15 17 19 21 23

- lt

Day Time Hours)

102

offer better values

103

-

(

10

9

8

7

3

2

1

0

8

~--- bull~ - ct- -+ - - ~ 11 ~

0 ~~ t ~~ ~

~ ~~ ~f

il l 1

- 30 collectors 1400s_---_---_-- __ ---_----- ~_~ __ ~ __ l___ _______ ___ __

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

104

_-----------------------____ --------

(b) COPcycle

11

9

080706

~ 05ugtu 04a0u 03

0201a

7

~

005

03

~ 02c

025

bull~ 015aou 01

8 10 12 14 16 18Day Time(Hours)

20 24

(c) COP soiarnet

105

232119171513

11

Day TIme (Hours)

9

co- e bull

CIClK)ta ~

I

II

OJ

o

7

025

005

1312

1110

9

3 8 7~ 65 - 5

4321o

)

~ 015ltII0

8 01

bullbullbullltu 02c

7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24

DayTime (Hours)

106

~

ltflLIA IIl lj l

l ~ ~ bull j 1

J l f l I ~-

-- gt1 I I -1-_ I I I I I I 1 I

95

85

-u 750-C1l

65s+(0 55C1lcE

45C1l

bullbullbullbull

35

25

~

tIt[~I bull

~I J II

J~tI

~

Day Time Hours)

107

and COP solarnet

(41 Q)

(49)

108

i

~

23

21

ta 11k

19

I 1 J

1715131197

10595

3525

5

Day Time (Hours)

109

I

109

8

7

i 6II- 5uui3 4

3

2

1

0

8 9 10 11 12 13 14 15 16 _ 17 18 19 20 21 22 23 24

Day TIme (Ihours)

Ii

08

07

06

~ 05ugt-u 04

Q

0u 03

02

01

O- 8

1 bull

(b) COP cycle

23

110

10 12 -14 16 18 20 22 24

(c) COPsolarnet

24222Q181614

111

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

10908

Q) 07tl 06e 05~0 04U 03

02010

8

IIIIIIIII

Day Time (Homs)

(b) COP cycle

03025

005

8 10 12 14 16 18

- -

20 22 24

Day Tillie (Hours)

(c) COPsolarnet

112

gti

r-i~

121110

98

i 7II- 6uu~ 5u

4~ 3

21

0

8

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

2422

1-

10

1

09

08

07

06

tugt- 05u0-0u 04

03

02

01

a8

(b) COP cycle

113

2422201816141210

8

02

005

o

025

Day Time (Hours)

(c) COPsolarnet

-t +

40353025

5 7 9 11 13 15 17 1921 23

Day Time (Hours)

114

13-design =de~ign2

1482 1492 1502 1512 1522 1532 1542 1552 1562i

8

12

Day Time (Hours)

14

12 _ =uniform 1400s ~~

I ~- i~l ~

( -P amp- d 4-- ~r ~ ~ 4~

) V~ P~~r - 9 ~ ~ I f ~lt7 1 -

~ (=~

[

13

Elt1lI-

9

8

7

1365 1369 1373 1377 1381 1385 1389 1393 1397 1401 1405 1409

DayTime (Hours)

II115

~l

~~

~

3530

~design 2 -design 1

r _

5 7 9 11 13 15 17 19 21 23

Day Time (Hours)

I

~

~ ~ 116

---L__ _______ ___

~f 7 gt

ff

I I~

fi

07

06

05gtu 04c~u 03QJ

02

01

a

5 6 7 8 9 10 11 12 13 14 15 16 17 18Day Time (Hours)

117

~I

H

I

cycle time ~400s

118

119

I~

i

I-~j~

120

L fj

iI ~

J

~

CHAPTER 5

Thermal Collectors

~

I___L121

j

in Dhaka

dt l UCPiAcp]

122

(5 1 )

(52)

SolarI

Tlterloal Co8ector

(

household use

123

I _~

~Obil - Q

~ ~T ------[lt----------~

ll I~V4

___-L

l

~

(54)

124

-P~_ __ l J

~~ ~

I ~i~

- -- ~ r

~-i

125

125 13

36

33

21

186 8 ~o 12 14

Ibull

9 12

Day Time (Hoursl-

15 18

11bull

126

1 need

i

127

f

q

IjHlIIIiIIij~I

CHAPTER 6

~

bull

of the chiller

875degC

129

IIjf

performance

130

bull

peak hours

I

liters of water

bull

d

performance

131

compression chiller

system

132

~

d

References

133

II

d

J 50-62

134

J

135

J

136

Journal

~

137

_------- _- _ --_ _ __ _---------------------

IIi

-

138

00000001
00000002
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00000006
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00000161

Page 5: Full Thesis - Bangladesh University of Engineering and ...

~A~Rifat Ara Rouf

12th July 2014

v

___ ctr --- ---- _ -

-__~_- - ----_-_ _-

Acknowledgement

VI

~---__- -----__ __

and advice

understanding

Vll

_ _--_--- -

Abstract

heating purposes

VIp

CONTENTS

Board of Examiners

Acknowledgements

Abstract

Nomenclature-

List of Tables

List of Figures

ii

v

vi

viii

xiii

xiv

xv

CHAPTERl (

124 Time Line

Cycle

IX

1

2

3

5

6

7

8

10

11

13

14

17

Refrigeration Cycle

CHAPTER 2

23 Formulation

231 Solar System

Cycle Time

25 Summary

x

18

26

27

353537

3738

39

4041

45

4750

51

54

6071

r ~-I

I j

------

CHAPTER 3

Dhaka

31 Introduction

33 Summary

CHAPTER 4

System Performance

41 Introduction

45 Summary

CHAPTERS

54 Summary

CHAPTER 6

Xl

73

88

89

899094

95

119

121

122

124

127

128

-

Future work

References

Xli

131

133137

r

Nomenclature

A Area (m2)

XliI

------------- __--------~ -_- --- _- _ -

I

r~-I

i

List of Tables

-

XIV

94

I

List of Figures

II

Figure 11

Figure 12

Figure 13

Figure 14

Figure 15

Figure 16

Figure 17

Figure 18

[2009]

cooling system

[2009]

xv

15

16

19

20

21

22

23

24

25

28

[2005])

April

optimum cycle time

XVI

Figure 24

Figure 25

(

cycle 800s

57

58

59

62

Figure 27

Figure 28

Figure 29

140h

then decreasing

cooling capacity

XVII

62

63

64

66

rttI

-

Figure210

Figure 710

Figure 211

Figure 212

Figure 31

hours

cycle -

(a) March

(b) April

(c) June

(d) August

68

69

70

74

75

Figure 31

bullbullbull

(e) October

(t) December

March

XVIII

76

80

months (a)CACC

months (c) COPse

XIX

gt

time 1400s

xx

~I

design 1

for design 2

cycle

COPsolarnet

XXI

104

105

106

107

109

110

III

111

Figure 412

Figure 413

Figure 414

Figure 415

Figure 4J5

COP cycle

COPsolarnet

cooling capacity

time

Figure 416

Figure 417

Figure 418

design 1

design 2

XXII

116

117

118

b

Figure 419

Figure 51

Figure 52

Figure 53

Figure 54

Figure 55

1400s

collector and tank

solar coupling

household

XXIII

CHAPTER

Introduction

11 Introduction

cycle begins again

I

2

--

f

3

e

4

I

i1

Japan

conditioning

cooking

residences

perishable goods

Kettering of GM

distribution

5

Superior Arizona

surface phenomenon

the adsorbate

6

t

--l

7

isotherm etc

8

f

9

(v) Low viscosity

water etc

10

-

io-(

11

I~

f

IIII[

f

I

i

1

12

I

t f

I

i

~~

13

lt A ~ -

of the liquid

cycles lie around 3

14

f

CompressorQpor

~vaporator

Expansion

Condenser

Uquid + porValve

15

-Isobars

( ~

t

~

1

~-

-I--

1 _

1-

f

----4-isobar

1gt1 Y Liquid

--_ 1 Vapor

High Pr

i NH3 Vapour

VapQufc ~

~~n~~t~

Q T j1gt~

1 1~ ~-~- ~ -

Strong Absorb~r -

NHJ solution

16

(Figurel3)

17

18

-~

LoP

II

I

~~

~

-lIT

-

AdsomedI

vapour

Ie

-~oCondensel

heat pumping [2014J

19

~

--

~

LnP

-lff

Q-

ht Qcs~---II

IIIII

bullbullII_~- -

20--_bullbull_--------_- -- _ --_-

-~ -

-

LnP

~

COtliBS + ltii

tlqmssumtttibn -lIT

heat pumping [2014]

21

LnP

-lIT

QcsTcs ===

IIIIIIIIIII_---

heat pumping [2014]

22

I ~ _

I -

i ~i

Ci Pc- bull Wo- InP

bull

PE

I)-

T-o

23

vm

Condenser

SE2

V8

EvaporatorV2 i

II i

r-------

VIrt

i =

Cooling load

system

24

deg IIIIII V4

vs

r -~---~- deg

VI IIi

~

i (IIi= Ii~Ii~ 0

~

V2 V8

Evaporator

adsorbero

SEl

25

installed

process)

26

~

27

8x+amp

lnP

~ ~

a2e a1 a1

bullbull1--T

28

29

)~ 737t tlOr~ lir ~ ~ t 4~24l

bull~f

1~8 234

~

]f~ 123~

o10 20 30 40 50 60 70 80

40

bullbullu30 L

4JI-

2~I-~p

fi20 -

1-ec~gt01)

10 bullbullCd3Cd

r

0

30

et)c~- (JJ-~deg0o~u

5

~

Heatrejected

VIO

Condenser

V8----

Evaporator

r------- J~~ ~_~ IIIIII V4

VI

V2

~

i=1

I

31

---_-bull_----_ - --

32

--_ bull__-----~----------__-__ __ _- -

jiJ

~iAff~l

CONO

(b) ModcB

CONOl

CONOI

(a) ModeA

33

denoted as mode D

mode A

34--_bull_ bull_-----------------__- _

Sumanthy [2004]

35

36

Figure 112

mathematically

ice making purpose

37

~

f ~

lower heat source

38

CHAPTER 2

ofDhaka

39

-~--_ ---_ _ _

40

I

41

-_ __-__-----__----__ __ ~

V4btgt~c- ()- ~0

VIO 00U-

5

VI

- ~~

bull t~

42

(23)

by

transfer fluid

(24)

43

(27)

(26)

(25)

loops

ToUl

state q

(29)

calculated by

Ps(T) = 13332 e [183-3820 1(1-461)] (21 0)

44

(213)

(212)

endojcyclelime

endofcycletime

cycle

number of collector

ao -15587 bo -65314

aj 015915 bl 072452E-Ol

a2 -050612E-03 b2 -023951 E-03

a3 053290E-06 b3 025493E-06

231 Solar System

45

expressed as

where

(214)

(215)

(2 f6)

46

(217)

47

900800

f1E 700

~ 600c2 500+(U-o 400IIIs - 300_(U

0 200til

100o

bull

[l 06042009 RERC [JI

5 7 9 11 13 17 19

Day Time (Hoursl

April

48

49

(218)

am ~--~+-~-~ In ----------- 2 2 Daylength

50

~

i

51

I

161412

4

2

o

I

T 8 9 -10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

52

06

05

Gl 04]~ 03Ou 02

01

o

7 8 9 10 11 12 13 14 15 16 17 18 19

DayTIme (Hours)

03

025

02uIII0 0150u

01

20 collectors

I _~_L L__

i

8 9 10 11 12 13 14 15Day Time (Hours)

16 17 18 19

53

I

-

54

II

55

19

6 i-n bull ~

1715

13Day Time (Hours)

119

Day TIme (Hours)

8 9 10 11 12 13 14 15 16 17 -18 19

18

16

14

12

~ 10lII

Uu 8ctu

6

4

2

0

7

12

j 1~~ lt~

1 08 QI) U gtu 06

Q

0u04

02

0

7

56

191715

13

DayTime (Hours)

10 11 12 13 14 15 16 17 18 19

9

--r bull ~ --_- ---~~-~-~--~~~~- ~ 1~

~ ~

bullbull

8

7

a

03

04

01

u0 028

035

03

005

0

7

DayTime (Hours)

57

12 13

Daynme (Hours)

f f

~

~ 0 bull 0 Q

bull g -- ~

~

bull bull I bull

12 13

Day Time (Hours)

58

~gt =

1312

po 11-10

9

8

deg7

6

- 22collectors1000s

11191195 12 1205 121 1215 122 1225 123 1235

Day Time (Hours)

59

li

i ~

60

the sunset hours

(i) 800s

(ii) 800s 140 - 185 h 20 scycle

61

110100

P 90-~ 80J10 70~ 60~ 50I-

4030

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day TIme (Hours)

110 100 ~

4030

17 19

140h

62

decreasing gt I11i

1917151311

DayTime (Hours)

97

~ 100d1

f(

U 900-lt1l 80l+ 70(ll lt1lQ 60E 50

4030

5

Il

1917

uniform cycle 800s

9

11 13 15

Day Time (Hours)

()fJ

~~ 13

121110

9~ 8 7

7

63

1

08

41 06ugtua0 04u

02

o

7 8 9 10 11 12 13 14 15 16 i7 18 19

Day Time (Hours)

05

04

u 03VIa

0u 02

01

0

7 9 11 13

__ I

64

~

(J

1ltlt

1lt ~

lt)lt

(OC)(i) Uniform 95 87 71 119 065 0315

800s(ii) Non- 95 87 71 119 057 0314

uniform800s

(iii)Non- 93 85 74 118 056 0311uniform550s

65

12115

11

U 105a-~ 101i 95~ 9E~ 85

8757

1195

12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

r Co

66

67

II

U 100o- 90 bullbullJ 80tu~ 70~ 60

~ 504030

5 7 9 11 13 15 17 19Day TIme (Hours)

fr

Ii ~

110

40

30

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

68

Day Time (Hours)

-__-~--~-

(a) CACC

__ ~_L_~_~_

9 10 11 12 13 14 15 16 17 18 19

09

08

07

~ 06gtrr 058 04

03

02

01 -

o

13121110- 9

S 8 7-u 6uot 5u 4

3210

7 8

7 8 9 10 11 1213 14 15 16 17 18 19

Day rfme (Hours)

(b) COP cycle

69

19171513

Day Time (Hours)

(c) COPse

119

04

035

03

025uQ 020v

015

01

005

0

7

151413

U 12~ 11

543

00000deg(1

bull__ J 1 bull ~_J

i195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

70

outlet increases

peak hours

71

~

c

bull~

~r f

~

72

CHAPTER 3

31 Introduction

73

900

100 A 28032005 RERCa

5 7 9 11 13 15 17 19Day Time (Hoursl

III11I

I I

19171513119

900800

E700 ~~ ~ ~

c 600 EJ ~

1~~ ~~ c 300 I d ~ ~

5 7

Day Time (Hours)

74- _- - _~----~~------

800700-NS 600

~- 500c0- 400to-0 300IIIC

- 200nI0V) 100

a ~~ 5 7

II

15 17 19

lIII

600

0

5 7 9 11 13 15 17 19

Day Time (Hours)

75

600

500-NE--= 400A-t

0~ 300 A nl0ent

0 0710 007

5 7 9 11 13 15 17 19Day Time (Hours)

600[J

1500 ~

1

5 9 11 13 15 17 19Day Time (Hours)

76

77

HVm2(Average on 7

years)

March 712 300 188

April 771 340 240

June 568 314 258

August 546 325 266

October 536 312 250

78

-__-------------------------__-_-

l

79

~

125

bed 2

13

i (a) March

bed 2

~bull I

o

-~

85

~[35 LL

115

105 -

G 95o-

1J

(b) April

80

10090-u 800bull

OJl 70J+Ill 60GIQ

EGI 50I-

40

30

bull ~- 11 115 12

Day Time (Hours)

i ~

--J~ -

125 13 I I

I

(c) June

(d) August

115

_____ ~I _ bull i bull -- __

10090 --u 800-~

lo 70s+IVlo 60~Q

E 50~1-

4030

11

81

10- 60QJa-S 50QJl-

40

3011 115 12

Day Time (Hours)

(e) October

I

-J ii

125

J13

(f) December

125 13

82

_-----------------------------------

83

--April--October

Day Time (Hours)

10 11 12 13 14 15 16 17 18 19

bullbull

9

87

16151413121110987654321a

-S0-UUctu

DayTime (Hours)

191817161514

131210 11

(b) COPcycle

9

1

08QI 06Ugt-uQ

0 04u

02

07 8

-J __L- __--L- __ _____ --

Marchampgt=June

=-October

17 18 191614 151310 11 1298

0605

04tv

lVIQ 030u

02

01

0

7

Day Time (Hours)

(c) COPsc

84

85

(b) April

1

Day Time (Hours)

7 l-_---__ ~__ ~ __ ~ __ ~__ ~_~__

1195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

(a) March

12

1194 1199 1204 1209 1214 1219 1224 1229 1234 1239

12115

a- i1e 105C1I3 10~ 95~X 9E 85~ 8

757

Day Time (Hours)

(c) June

-evaporator outlet

1199 1204 1209 1214 1219 1224 1229 1234 1239

13

125

12115

~ 1095

9

1194

-evaporator outlet

13513

G 125o~ 12bullE 11510

~ 11E 105 -

10

959 1- I

1195 12 1205 121 1215 122 1225 123 1235 124

DayTime (Hours)

(d) August

86

r

P 125-

951205 121 1215 122 1225 123 1235 124 1245 125 1255

Day Time (Hours)

(e) October

EQj 11I-

10

1184 1189

___ L __ J__ ~_~ __ J __ -L

1194 1199 1204 1209 1214 1219 1224 1229

Day Time (Hours)

(1) December

87

_----- --------------------------------~-_---

33 Summary

88

---__----------------------------_ -__ _

tt~r~~~~

~

i ~ t

+ bull

1

CHAPTER 4

41 Introduction

89

___________ _ bull ~ bull 4lt

~ or

Chapter 2

90

j bull

1

Designl

Design 2

time

1 1 - 1400s - -End of the

91

V5VIO

SE2

V8

Evaporator

[ __ dere~~~d~I ~ I

1_ - - - -- - - - L - - - - - - -

I ~~-~~-~~=~~-~ II ( Condenser I)

III V4

III

IIIIIII1IIIf

- - - - - - - -1_-_1__-_-_-__-_-_-_Dcooling

loadO

V2

VI

V3

tt

J

i

design 1

bull

12

1

v1

HollVaer ollilel

if Cooling load

CondQnCQf

S IGlcqe tank

design 1

92

I]I]

~ V4III

IfI]I]

I

IVlO

-Evaporator

_ _W _ _ _ __ __r - - -__C_

Condenser

IIIIIII

lXt=-It2 I

I ----- -r------J - 1 r P- -r

IVbull ~

I

i

f t

if~Iii~~

~ t~ ~

design 2

93

_I

(41)

be expressed asdT -

I

1

(42)

(43)

And

Tcr 1in = Twt bull

in case of design 1

94

(45)

(48)

(47)

TbedoUI = Tcrin

nA Idtunrlsettme cr

and

bull

~

95

- __--------__-----__-----------------

96

i~

85

35

255 7 9 11 13 15 17 19 21 23

23

21

~j

19171513

I Jl I I

1197

---L-~ ____~_~ __ ~ I __J_ __ ~ __-

9085r 801

353025

5

Day Time (Hoursl

97

--__----------------------------

7 9 11 13 15 17 19 21 23 25Day Time (Hours)

353025

5

lJ~~(J~ lOS~~

1 ~ 100~- 95~

~ 90r u 85

40353025

5 7 9 11 13 15 17 19 21

I

23

Day Time (Hours)

98

99

--------- _ -- -__-

80-u 700-lt11~ 60J+-(U

50lt11aE 40lt11I-

30

5

DayTIme (Hours)

100

25

23

21

-

21

11 13 15 17 19

Da~Time (Hours)

9

7

90858075-u 700-Q) 65-s 60+ro 55-Q)

353025

5

~fj~

~

95lt

1 90t 85

80u 750- 70lt1J 65J+ 60((

lt1J 55Q

E 50lt1J 45~

40353025

5

101

~

105100

9590

85uo 80-4J 75J 701n 65~ 60e 55Q) 50 r 45 r ~

J 25 __----bull _~-- L I _ __ _~__- Jbull__ -__ _J__

5 7 9 11 11) 15 17 19 21 23

- lt

Day Time Hours)

102

offer better values

103

-

(

10

9

8

7

3

2

1

0

8

~--- bull~ - ct- -+ - - ~ 11 ~

0 ~~ t ~~ ~

~ ~~ ~f

il l 1

- 30 collectors 1400s_---_---_-- __ ---_----- ~_~ __ ~ __ l___ _______ ___ __

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

104

_-----------------------____ --------

(b) COPcycle

11

9

080706

~ 05ugtu 04a0u 03

0201a

7

~

005

03

~ 02c

025

bull~ 015aou 01

8 10 12 14 16 18Day Time(Hours)

20 24

(c) COP soiarnet

105

232119171513

11

Day TIme (Hours)

9

co- e bull

CIClK)ta ~

I

II

OJ

o

7

025

005

1312

1110

9

3 8 7~ 65 - 5

4321o

)

~ 015ltII0

8 01

bullbullbullltu 02c

7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24

DayTime (Hours)

106

~

ltflLIA IIl lj l

l ~ ~ bull j 1

J l f l I ~-

-- gt1 I I -1-_ I I I I I I 1 I

95

85

-u 750-C1l

65s+(0 55C1lcE

45C1l

bullbullbullbull

35

25

~

tIt[~I bull

~I J II

J~tI

~

Day Time Hours)

107

and COP solarnet

(41 Q)

(49)

108

i

~

23

21

ta 11k

19

I 1 J

1715131197

10595

3525

5

Day Time (Hours)

109

I

109

8

7

i 6II- 5uui3 4

3

2

1

0

8 9 10 11 12 13 14 15 16 _ 17 18 19 20 21 22 23 24

Day TIme (Ihours)

Ii

08

07

06

~ 05ugt-u 04

Q

0u 03

02

01

O- 8

1 bull

(b) COP cycle

23

110

10 12 -14 16 18 20 22 24

(c) COPsolarnet

24222Q181614

111

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

10908

Q) 07tl 06e 05~0 04U 03

02010

8

IIIIIIIII

Day Time (Homs)

(b) COP cycle

03025

005

8 10 12 14 16 18

- -

20 22 24

Day Tillie (Hours)

(c) COPsolarnet

112

gti

r-i~

121110

98

i 7II- 6uu~ 5u

4~ 3

21

0

8

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

2422

1-

10

1

09

08

07

06

tugt- 05u0-0u 04

03

02

01

a8

(b) COP cycle

113

2422201816141210

8

02

005

o

025

Day Time (Hours)

(c) COPsolarnet

-t +

40353025

5 7 9 11 13 15 17 1921 23

Day Time (Hours)

114

13-design =de~ign2

1482 1492 1502 1512 1522 1532 1542 1552 1562i

8

12

Day Time (Hours)

14

12 _ =uniform 1400s ~~

I ~- i~l ~

( -P amp- d 4-- ~r ~ ~ 4~

) V~ P~~r - 9 ~ ~ I f ~lt7 1 -

~ (=~

[

13

Elt1lI-

9

8

7

1365 1369 1373 1377 1381 1385 1389 1393 1397 1401 1405 1409

DayTime (Hours)

II115

~l

~~

~

3530

~design 2 -design 1

r _

5 7 9 11 13 15 17 19 21 23

Day Time (Hours)

I

~

~ ~ 116

---L__ _______ ___

~f 7 gt

ff

I I~

fi

07

06

05gtu 04c~u 03QJ

02

01

a

5 6 7 8 9 10 11 12 13 14 15 16 17 18Day Time (Hours)

117

~I

H

I

cycle time ~400s

118

119

I~

i

I-~j~

120

L fj

iI ~

J

~

CHAPTER 5

Thermal Collectors

~

I___L121

j

in Dhaka

dt l UCPiAcp]

122

(5 1 )

(52)

SolarI

Tlterloal Co8ector

(

household use

123

I _~

~Obil - Q

~ ~T ------[lt----------~

ll I~V4

___-L

l

~

(54)

124

-P~_ __ l J

~~ ~

I ~i~

- -- ~ r

~-i

125

125 13

36

33

21

186 8 ~o 12 14

Ibull

9 12

Day Time (Hoursl-

15 18

11bull

126

1 need

i

127

f

q

IjHlIIIiIIij~I

CHAPTER 6

~

bull

of the chiller

875degC

129

IIjf

performance

130

bull

peak hours

I

liters of water

bull

d

performance

131

compression chiller

system

132

~

d

References

133

II

d

J 50-62

134

J

135

J

136

Journal

~

137

_------- _- _ --_ _ __ _---------------------

IIi

-

138

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00000002
00000003
00000004
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00000006
00000007
00000008
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Page 6: Full Thesis - Bangladesh University of Engineering and ...

-__~_- - ----_-_ _-

Acknowledgement

VI

~---__- -----__ __

and advice

understanding

Vll

_ _--_--- -

Abstract

heating purposes

VIp

CONTENTS

Board of Examiners

Acknowledgements

Abstract

Nomenclature-

List of Tables

List of Figures

ii

v

vi

viii

xiii

xiv

xv

CHAPTERl (

124 Time Line

Cycle

IX

1

2

3

5

6

7

8

10

11

13

14

17

Refrigeration Cycle

CHAPTER 2

23 Formulation

231 Solar System

Cycle Time

25 Summary

x

18

26

27

353537

3738

39

4041

45

4750

51

54

6071

r ~-I

I j

------

CHAPTER 3

Dhaka

31 Introduction

33 Summary

CHAPTER 4

System Performance

41 Introduction

45 Summary

CHAPTERS

54 Summary

CHAPTER 6

Xl

73

88

89

899094

95

119

121

122

124

127

128

-

Future work

References

Xli

131

133137

r

Nomenclature

A Area (m2)

XliI

------------- __--------~ -_- --- _- _ -

I

r~-I

i

List of Tables

-

XIV

94

I

List of Figures

II

Figure 11

Figure 12

Figure 13

Figure 14

Figure 15

Figure 16

Figure 17

Figure 18

[2009]

cooling system

[2009]

xv

15

16

19

20

21

22

23

24

25

28

[2005])

April

optimum cycle time

XVI

Figure 24

Figure 25

(

cycle 800s

57

58

59

62

Figure 27

Figure 28

Figure 29

140h

then decreasing

cooling capacity

XVII

62

63

64

66

rttI

-

Figure210

Figure 710

Figure 211

Figure 212

Figure 31

hours

cycle -

(a) March

(b) April

(c) June

(d) August

68

69

70

74

75

Figure 31

bullbullbull

(e) October

(t) December

March

XVIII

76

80

months (a)CACC

months (c) COPse

XIX

gt

time 1400s

xx

~I

design 1

for design 2

cycle

COPsolarnet

XXI

104

105

106

107

109

110

III

111

Figure 412

Figure 413

Figure 414

Figure 415

Figure 4J5

COP cycle

COPsolarnet

cooling capacity

time

Figure 416

Figure 417

Figure 418

design 1

design 2

XXII

116

117

118

b

Figure 419

Figure 51

Figure 52

Figure 53

Figure 54

Figure 55

1400s

collector and tank

solar coupling

household

XXIII

CHAPTER

Introduction

11 Introduction

cycle begins again

I

2

--

f

3

e

4

I

i1

Japan

conditioning

cooking

residences

perishable goods

Kettering of GM

distribution

5

Superior Arizona

surface phenomenon

the adsorbate

6

t

--l

7

isotherm etc

8

f

9

(v) Low viscosity

water etc

10

-

io-(

11

I~

f

IIII[

f

I

i

1

12

I

t f

I

i

~~

13

lt A ~ -

of the liquid

cycles lie around 3

14

f

CompressorQpor

~vaporator

Expansion

Condenser

Uquid + porValve

15

-Isobars

( ~

t

~

1

~-

-I--

1 _

1-

f

----4-isobar

1gt1 Y Liquid

--_ 1 Vapor

High Pr

i NH3 Vapour

VapQufc ~

~~n~~t~

Q T j1gt~

1 1~ ~-~- ~ -

Strong Absorb~r -

NHJ solution

16

(Figurel3)

17

18

-~

LoP

II

I

~~

~

-lIT

-

AdsomedI

vapour

Ie

-~oCondensel

heat pumping [2014J

19

~

--

~

LnP

-lff

Q-

ht Qcs~---II

IIIII

bullbullII_~- -

20--_bullbull_--------_- -- _ --_-

-~ -

-

LnP

~

COtliBS + ltii

tlqmssumtttibn -lIT

heat pumping [2014]

21

LnP

-lIT

QcsTcs ===

IIIIIIIIIII_---

heat pumping [2014]

22

I ~ _

I -

i ~i

Ci Pc- bull Wo- InP

bull

PE

I)-

T-o

23

vm

Condenser

SE2

V8

EvaporatorV2 i

II i

r-------

VIrt

i =

Cooling load

system

24

deg IIIIII V4

vs

r -~---~- deg

VI IIi

~

i (IIi= Ii~Ii~ 0

~

V2 V8

Evaporator

adsorbero

SEl

25

installed

process)

26

~

27

8x+amp

lnP

~ ~

a2e a1 a1

bullbull1--T

28

29

)~ 737t tlOr~ lir ~ ~ t 4~24l

bull~f

1~8 234

~

]f~ 123~

o10 20 30 40 50 60 70 80

40

bullbullu30 L

4JI-

2~I-~p

fi20 -

1-ec~gt01)

10 bullbullCd3Cd

r

0

30

et)c~- (JJ-~deg0o~u

5

~

Heatrejected

VIO

Condenser

V8----

Evaporator

r------- J~~ ~_~ IIIIII V4

VI

V2

~

i=1

I

31

---_-bull_----_ - --

32

--_ bull__-----~----------__-__ __ _- -

jiJ

~iAff~l

CONO

(b) ModcB

CONOl

CONOI

(a) ModeA

33

denoted as mode D

mode A

34--_bull_ bull_-----------------__- _

Sumanthy [2004]

35

36

Figure 112

mathematically

ice making purpose

37

~

f ~

lower heat source

38

CHAPTER 2

ofDhaka

39

-~--_ ---_ _ _

40

I

41

-_ __-__-----__----__ __ ~

V4btgt~c- ()- ~0

VIO 00U-

5

VI

- ~~

bull t~

42

(23)

by

transfer fluid

(24)

43

(27)

(26)

(25)

loops

ToUl

state q

(29)

calculated by

Ps(T) = 13332 e [183-3820 1(1-461)] (21 0)

44

(213)

(212)

endojcyclelime

endofcycletime

cycle

number of collector

ao -15587 bo -65314

aj 015915 bl 072452E-Ol

a2 -050612E-03 b2 -023951 E-03

a3 053290E-06 b3 025493E-06

231 Solar System

45

expressed as

where

(214)

(215)

(2 f6)

46

(217)

47

900800

f1E 700

~ 600c2 500+(U-o 400IIIs - 300_(U

0 200til

100o

bull

[l 06042009 RERC [JI

5 7 9 11 13 17 19

Day Time (Hoursl

April

48

49

(218)

am ~--~+-~-~ In ----------- 2 2 Daylength

50

~

i

51

I

161412

4

2

o

I

T 8 9 -10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

52

06

05

Gl 04]~ 03Ou 02

01

o

7 8 9 10 11 12 13 14 15 16 17 18 19

DayTIme (Hours)

03

025

02uIII0 0150u

01

20 collectors

I _~_L L__

i

8 9 10 11 12 13 14 15Day Time (Hours)

16 17 18 19

53

I

-

54

II

55

19

6 i-n bull ~

1715

13Day Time (Hours)

119

Day TIme (Hours)

8 9 10 11 12 13 14 15 16 17 -18 19

18

16

14

12

~ 10lII

Uu 8ctu

6

4

2

0

7

12

j 1~~ lt~

1 08 QI) U gtu 06

Q

0u04

02

0

7

56

191715

13

DayTime (Hours)

10 11 12 13 14 15 16 17 18 19

9

--r bull ~ --_- ---~~-~-~--~~~~- ~ 1~

~ ~

bullbull

8

7

a

03

04

01

u0 028

035

03

005

0

7

DayTime (Hours)

57

12 13

Daynme (Hours)

f f

~

~ 0 bull 0 Q

bull g -- ~

~

bull bull I bull

12 13

Day Time (Hours)

58

~gt =

1312

po 11-10

9

8

deg7

6

- 22collectors1000s

11191195 12 1205 121 1215 122 1225 123 1235

Day Time (Hours)

59

li

i ~

60

the sunset hours

(i) 800s

(ii) 800s 140 - 185 h 20 scycle

61

110100

P 90-~ 80J10 70~ 60~ 50I-

4030

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day TIme (Hours)

110 100 ~

4030

17 19

140h

62

decreasing gt I11i

1917151311

DayTime (Hours)

97

~ 100d1

f(

U 900-lt1l 80l+ 70(ll lt1lQ 60E 50

4030

5

Il

1917

uniform cycle 800s

9

11 13 15

Day Time (Hours)

()fJ

~~ 13

121110

9~ 8 7

7

63

1

08

41 06ugtua0 04u

02

o

7 8 9 10 11 12 13 14 15 16 i7 18 19

Day Time (Hours)

05

04

u 03VIa

0u 02

01

0

7 9 11 13

__ I

64

~

(J

1ltlt

1lt ~

lt)lt

(OC)(i) Uniform 95 87 71 119 065 0315

800s(ii) Non- 95 87 71 119 057 0314

uniform800s

(iii)Non- 93 85 74 118 056 0311uniform550s

65

12115

11

U 105a-~ 101i 95~ 9E~ 85

8757

1195

12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

r Co

66

67

II

U 100o- 90 bullbullJ 80tu~ 70~ 60

~ 504030

5 7 9 11 13 15 17 19Day TIme (Hours)

fr

Ii ~

110

40

30

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

68

Day Time (Hours)

-__-~--~-

(a) CACC

__ ~_L_~_~_

9 10 11 12 13 14 15 16 17 18 19

09

08

07

~ 06gtrr 058 04

03

02

01 -

o

13121110- 9

S 8 7-u 6uot 5u 4

3210

7 8

7 8 9 10 11 1213 14 15 16 17 18 19

Day rfme (Hours)

(b) COP cycle

69

19171513

Day Time (Hours)

(c) COPse

119

04

035

03

025uQ 020v

015

01

005

0

7

151413

U 12~ 11

543

00000deg(1

bull__ J 1 bull ~_J

i195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

70

outlet increases

peak hours

71

~

c

bull~

~r f

~

72

CHAPTER 3

31 Introduction

73

900

100 A 28032005 RERCa

5 7 9 11 13 15 17 19Day Time (Hoursl

III11I

I I

19171513119

900800

E700 ~~ ~ ~

c 600 EJ ~

1~~ ~~ c 300 I d ~ ~

5 7

Day Time (Hours)

74- _- - _~----~~------

800700-NS 600

~- 500c0- 400to-0 300IIIC

- 200nI0V) 100

a ~~ 5 7

II

15 17 19

lIII

600

0

5 7 9 11 13 15 17 19

Day Time (Hours)

75

600

500-NE--= 400A-t

0~ 300 A nl0ent

0 0710 007

5 7 9 11 13 15 17 19Day Time (Hours)

600[J

1500 ~

1

5 9 11 13 15 17 19Day Time (Hours)

76

77

HVm2(Average on 7

years)

March 712 300 188

April 771 340 240

June 568 314 258

August 546 325 266

October 536 312 250

78

-__-------------------------__-_-

l

79

~

125

bed 2

13

i (a) March

bed 2

~bull I

o

-~

85

~[35 LL

115

105 -

G 95o-

1J

(b) April

80

10090-u 800bull

OJl 70J+Ill 60GIQ

EGI 50I-

40

30

bull ~- 11 115 12

Day Time (Hours)

i ~

--J~ -

125 13 I I

I

(c) June

(d) August

115

_____ ~I _ bull i bull -- __

10090 --u 800-~

lo 70s+IVlo 60~Q

E 50~1-

4030

11

81

10- 60QJa-S 50QJl-

40

3011 115 12

Day Time (Hours)

(e) October

I

-J ii

125

J13

(f) December

125 13

82

_-----------------------------------

83

--April--October

Day Time (Hours)

10 11 12 13 14 15 16 17 18 19

bullbull

9

87

16151413121110987654321a

-S0-UUctu

DayTime (Hours)

191817161514

131210 11

(b) COPcycle

9

1

08QI 06Ugt-uQ

0 04u

02

07 8

-J __L- __--L- __ _____ --

Marchampgt=June

=-October

17 18 191614 151310 11 1298

0605

04tv

lVIQ 030u

02

01

0

7

Day Time (Hours)

(c) COPsc

84

85

(b) April

1

Day Time (Hours)

7 l-_---__ ~__ ~ __ ~ __ ~__ ~_~__

1195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

(a) March

12

1194 1199 1204 1209 1214 1219 1224 1229 1234 1239

12115

a- i1e 105C1I3 10~ 95~X 9E 85~ 8

757

Day Time (Hours)

(c) June

-evaporator outlet

1199 1204 1209 1214 1219 1224 1229 1234 1239

13

125

12115

~ 1095

9

1194

-evaporator outlet

13513

G 125o~ 12bullE 11510

~ 11E 105 -

10

959 1- I

1195 12 1205 121 1215 122 1225 123 1235 124

DayTime (Hours)

(d) August

86

r

P 125-

951205 121 1215 122 1225 123 1235 124 1245 125 1255

Day Time (Hours)

(e) October

EQj 11I-

10

1184 1189

___ L __ J__ ~_~ __ J __ -L

1194 1199 1204 1209 1214 1219 1224 1229

Day Time (Hours)

(1) December

87

_----- --------------------------------~-_---

33 Summary

88

---__----------------------------_ -__ _

tt~r~~~~

~

i ~ t

+ bull

1

CHAPTER 4

41 Introduction

89

___________ _ bull ~ bull 4lt

~ or

Chapter 2

90

j bull

1

Designl

Design 2

time

1 1 - 1400s - -End of the

91

V5VIO

SE2

V8

Evaporator

[ __ dere~~~d~I ~ I

1_ - - - -- - - - L - - - - - - -

I ~~-~~-~~=~~-~ II ( Condenser I)

III V4

III

IIIIIII1IIIf

- - - - - - - -1_-_1__-_-_-__-_-_-_Dcooling

loadO

V2

VI

V3

tt

J

i

design 1

bull

12

1

v1

HollVaer ollilel

if Cooling load

CondQnCQf

S IGlcqe tank

design 1

92

I]I]

~ V4III

IfI]I]

I

IVlO

-Evaporator

_ _W _ _ _ __ __r - - -__C_

Condenser

IIIIIII

lXt=-It2 I

I ----- -r------J - 1 r P- -r

IVbull ~

I

i

f t

if~Iii~~

~ t~ ~

design 2

93

_I

(41)

be expressed asdT -

I

1

(42)

(43)

And

Tcr 1in = Twt bull

in case of design 1

94

(45)

(48)

(47)

TbedoUI = Tcrin

nA Idtunrlsettme cr

and

bull

~

95

- __--------__-----__-----------------

96

i~

85

35

255 7 9 11 13 15 17 19 21 23

23

21

~j

19171513

I Jl I I

1197

---L-~ ____~_~ __ ~ I __J_ __ ~ __-

9085r 801

353025

5

Day Time (Hoursl

97

--__----------------------------

7 9 11 13 15 17 19 21 23 25Day Time (Hours)

353025

5

lJ~~(J~ lOS~~

1 ~ 100~- 95~

~ 90r u 85

40353025

5 7 9 11 13 15 17 19 21

I

23

Day Time (Hours)

98

99

--------- _ -- -__-

80-u 700-lt11~ 60J+-(U

50lt11aE 40lt11I-

30

5

DayTIme (Hours)

100

25

23

21

-

21

11 13 15 17 19

Da~Time (Hours)

9

7

90858075-u 700-Q) 65-s 60+ro 55-Q)

353025

5

~fj~

~

95lt

1 90t 85

80u 750- 70lt1J 65J+ 60((

lt1J 55Q

E 50lt1J 45~

40353025

5

101

~

105100

9590

85uo 80-4J 75J 701n 65~ 60e 55Q) 50 r 45 r ~

J 25 __----bull _~-- L I _ __ _~__- Jbull__ -__ _J__

5 7 9 11 11) 15 17 19 21 23

- lt

Day Time Hours)

102

offer better values

103

-

(

10

9

8

7

3

2

1

0

8

~--- bull~ - ct- -+ - - ~ 11 ~

0 ~~ t ~~ ~

~ ~~ ~f

il l 1

- 30 collectors 1400s_---_---_-- __ ---_----- ~_~ __ ~ __ l___ _______ ___ __

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

104

_-----------------------____ --------

(b) COPcycle

11

9

080706

~ 05ugtu 04a0u 03

0201a

7

~

005

03

~ 02c

025

bull~ 015aou 01

8 10 12 14 16 18Day Time(Hours)

20 24

(c) COP soiarnet

105

232119171513

11

Day TIme (Hours)

9

co- e bull

CIClK)ta ~

I

II

OJ

o

7

025

005

1312

1110

9

3 8 7~ 65 - 5

4321o

)

~ 015ltII0

8 01

bullbullbullltu 02c

7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24

DayTime (Hours)

106

~

ltflLIA IIl lj l

l ~ ~ bull j 1

J l f l I ~-

-- gt1 I I -1-_ I I I I I I 1 I

95

85

-u 750-C1l

65s+(0 55C1lcE

45C1l

bullbullbullbull

35

25

~

tIt[~I bull

~I J II

J~tI

~

Day Time Hours)

107

and COP solarnet

(41 Q)

(49)

108

i

~

23

21

ta 11k

19

I 1 J

1715131197

10595

3525

5

Day Time (Hours)

109

I

109

8

7

i 6II- 5uui3 4

3

2

1

0

8 9 10 11 12 13 14 15 16 _ 17 18 19 20 21 22 23 24

Day TIme (Ihours)

Ii

08

07

06

~ 05ugt-u 04

Q

0u 03

02

01

O- 8

1 bull

(b) COP cycle

23

110

10 12 -14 16 18 20 22 24

(c) COPsolarnet

24222Q181614

111

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

10908

Q) 07tl 06e 05~0 04U 03

02010

8

IIIIIIIII

Day Time (Homs)

(b) COP cycle

03025

005

8 10 12 14 16 18

- -

20 22 24

Day Tillie (Hours)

(c) COPsolarnet

112

gti

r-i~

121110

98

i 7II- 6uu~ 5u

4~ 3

21

0

8

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

2422

1-

10

1

09

08

07

06

tugt- 05u0-0u 04

03

02

01

a8

(b) COP cycle

113

2422201816141210

8

02

005

o

025

Day Time (Hours)

(c) COPsolarnet

-t +

40353025

5 7 9 11 13 15 17 1921 23

Day Time (Hours)

114

13-design =de~ign2

1482 1492 1502 1512 1522 1532 1542 1552 1562i

8

12

Day Time (Hours)

14

12 _ =uniform 1400s ~~

I ~- i~l ~

( -P amp- d 4-- ~r ~ ~ 4~

) V~ P~~r - 9 ~ ~ I f ~lt7 1 -

~ (=~

[

13

Elt1lI-

9

8

7

1365 1369 1373 1377 1381 1385 1389 1393 1397 1401 1405 1409

DayTime (Hours)

II115

~l

~~

~

3530

~design 2 -design 1

r _

5 7 9 11 13 15 17 19 21 23

Day Time (Hours)

I

~

~ ~ 116

---L__ _______ ___

~f 7 gt

ff

I I~

fi

07

06

05gtu 04c~u 03QJ

02

01

a

5 6 7 8 9 10 11 12 13 14 15 16 17 18Day Time (Hours)

117

~I

H

I

cycle time ~400s

118

119

I~

i

I-~j~

120

L fj

iI ~

J

~

CHAPTER 5

Thermal Collectors

~

I___L121

j

in Dhaka

dt l UCPiAcp]

122

(5 1 )

(52)

SolarI

Tlterloal Co8ector

(

household use

123

I _~

~Obil - Q

~ ~T ------[lt----------~

ll I~V4

___-L

l

~

(54)

124

-P~_ __ l J

~~ ~

I ~i~

- -- ~ r

~-i

125

125 13

36

33

21

186 8 ~o 12 14

Ibull

9 12

Day Time (Hoursl-

15 18

11bull

126

1 need

i

127

f

q

IjHlIIIiIIij~I

CHAPTER 6

~

bull

of the chiller

875degC

129

IIjf

performance

130

bull

peak hours

I

liters of water

bull

d

performance

131

compression chiller

system

132

~

d

References

133

II

d

J 50-62

134

J

135

J

136

Journal

~

137

_------- _- _ --_ _ __ _---------------------

IIi

-

138

00000001
00000002
00000003
00000004
00000005
00000006
00000007
00000008
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00000160
00000161

Page 7: Full Thesis - Bangladesh University of Engineering and ...

~---__- -----__ __

and advice

understanding

Vll

_ _--_--- -

Abstract

heating purposes

VIp

CONTENTS

Board of Examiners

Acknowledgements

Abstract

Nomenclature-

List of Tables

List of Figures

ii

v

vi

viii

xiii

xiv

xv

CHAPTERl (

124 Time Line

Cycle

IX

1

2

3

5

6

7

8

10

11

13

14

17

Refrigeration Cycle

CHAPTER 2

23 Formulation

231 Solar System

Cycle Time

25 Summary

x

18

26

27

353537

3738

39

4041

45

4750

51

54

6071

r ~-I

I j

------

CHAPTER 3

Dhaka

31 Introduction

33 Summary

CHAPTER 4

System Performance

41 Introduction

45 Summary

CHAPTERS

54 Summary

CHAPTER 6

Xl

73

88

89

899094

95

119

121

122

124

127

128

-

Future work

References

Xli

131

133137

r

Nomenclature

A Area (m2)

XliI

------------- __--------~ -_- --- _- _ -

I

r~-I

i

List of Tables

-

XIV

94

I

List of Figures

II

Figure 11

Figure 12

Figure 13

Figure 14

Figure 15

Figure 16

Figure 17

Figure 18

[2009]

cooling system

[2009]

xv

15

16

19

20

21

22

23

24

25

28

[2005])

April

optimum cycle time

XVI

Figure 24

Figure 25

(

cycle 800s

57

58

59

62

Figure 27

Figure 28

Figure 29

140h

then decreasing

cooling capacity

XVII

62

63

64

66

rttI

-

Figure210

Figure 710

Figure 211

Figure 212

Figure 31

hours

cycle -

(a) March

(b) April

(c) June

(d) August

68

69

70

74

75

Figure 31

bullbullbull

(e) October

(t) December

March

XVIII

76

80

months (a)CACC

months (c) COPse

XIX

gt

time 1400s

xx

~I

design 1

for design 2

cycle

COPsolarnet

XXI

104

105

106

107

109

110

III

111

Figure 412

Figure 413

Figure 414

Figure 415

Figure 4J5

COP cycle

COPsolarnet

cooling capacity

time

Figure 416

Figure 417

Figure 418

design 1

design 2

XXII

116

117

118

b

Figure 419

Figure 51

Figure 52

Figure 53

Figure 54

Figure 55

1400s

collector and tank

solar coupling

household

XXIII

CHAPTER

Introduction

11 Introduction

cycle begins again

I

2

--

f

3

e

4

I

i1

Japan

conditioning

cooking

residences

perishable goods

Kettering of GM

distribution

5

Superior Arizona

surface phenomenon

the adsorbate

6

t

--l

7

isotherm etc

8

f

9

(v) Low viscosity

water etc

10

-

io-(

11

I~

f

IIII[

f

I

i

1

12

I

t f

I

i

~~

13

lt A ~ -

of the liquid

cycles lie around 3

14

f

CompressorQpor

~vaporator

Expansion

Condenser

Uquid + porValve

15

-Isobars

( ~

t

~

1

~-

-I--

1 _

1-

f

----4-isobar

1gt1 Y Liquid

--_ 1 Vapor

High Pr

i NH3 Vapour

VapQufc ~

~~n~~t~

Q T j1gt~

1 1~ ~-~- ~ -

Strong Absorb~r -

NHJ solution

16

(Figurel3)

17

18

-~

LoP

II

I

~~

~

-lIT

-

AdsomedI

vapour

Ie

-~oCondensel

heat pumping [2014J

19

~

--

~

LnP

-lff

Q-

ht Qcs~---II

IIIII

bullbullII_~- -

20--_bullbull_--------_- -- _ --_-

-~ -

-

LnP

~

COtliBS + ltii

tlqmssumtttibn -lIT

heat pumping [2014]

21

LnP

-lIT

QcsTcs ===

IIIIIIIIIII_---

heat pumping [2014]

22

I ~ _

I -

i ~i

Ci Pc- bull Wo- InP

bull

PE

I)-

T-o

23

vm

Condenser

SE2

V8

EvaporatorV2 i

II i

r-------

VIrt

i =

Cooling load

system

24

deg IIIIII V4

vs

r -~---~- deg

VI IIi

~

i (IIi= Ii~Ii~ 0

~

V2 V8

Evaporator

adsorbero

SEl

25

installed

process)

26

~

27

8x+amp

lnP

~ ~

a2e a1 a1

bullbull1--T

28

29

)~ 737t tlOr~ lir ~ ~ t 4~24l

bull~f

1~8 234

~

]f~ 123~

o10 20 30 40 50 60 70 80

40

bullbullu30 L

4JI-

2~I-~p

fi20 -

1-ec~gt01)

10 bullbullCd3Cd

r

0

30

et)c~- (JJ-~deg0o~u

5

~

Heatrejected

VIO

Condenser

V8----

Evaporator

r------- J~~ ~_~ IIIIII V4

VI

V2

~

i=1

I

31

---_-bull_----_ - --

32

--_ bull__-----~----------__-__ __ _- -

jiJ

~iAff~l

CONO

(b) ModcB

CONOl

CONOI

(a) ModeA

33

denoted as mode D

mode A

34--_bull_ bull_-----------------__- _

Sumanthy [2004]

35

36

Figure 112

mathematically

ice making purpose

37

~

f ~

lower heat source

38

CHAPTER 2

ofDhaka

39

-~--_ ---_ _ _

40

I

41

-_ __-__-----__----__ __ ~

V4btgt~c- ()- ~0

VIO 00U-

5

VI

- ~~

bull t~

42

(23)

by

transfer fluid

(24)

43

(27)

(26)

(25)

loops

ToUl

state q

(29)

calculated by

Ps(T) = 13332 e [183-3820 1(1-461)] (21 0)

44

(213)

(212)

endojcyclelime

endofcycletime

cycle

number of collector

ao -15587 bo -65314

aj 015915 bl 072452E-Ol

a2 -050612E-03 b2 -023951 E-03

a3 053290E-06 b3 025493E-06

231 Solar System

45

expressed as

where

(214)

(215)

(2 f6)

46

(217)

47

900800

f1E 700

~ 600c2 500+(U-o 400IIIs - 300_(U

0 200til

100o

bull

[l 06042009 RERC [JI

5 7 9 11 13 17 19

Day Time (Hoursl

April

48

49

(218)

am ~--~+-~-~ In ----------- 2 2 Daylength

50

~

i

51

I

161412

4

2

o

I

T 8 9 -10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

52

06

05

Gl 04]~ 03Ou 02

01

o

7 8 9 10 11 12 13 14 15 16 17 18 19

DayTIme (Hours)

03

025

02uIII0 0150u

01

20 collectors

I _~_L L__

i

8 9 10 11 12 13 14 15Day Time (Hours)

16 17 18 19

53

I

-

54

II

55

19

6 i-n bull ~

1715

13Day Time (Hours)

119

Day TIme (Hours)

8 9 10 11 12 13 14 15 16 17 -18 19

18

16

14

12

~ 10lII

Uu 8ctu

6

4

2

0

7

12

j 1~~ lt~

1 08 QI) U gtu 06

Q

0u04

02

0

7

56

191715

13

DayTime (Hours)

10 11 12 13 14 15 16 17 18 19

9

--r bull ~ --_- ---~~-~-~--~~~~- ~ 1~

~ ~

bullbull

8

7

a

03

04

01

u0 028

035

03

005

0

7

DayTime (Hours)

57

12 13

Daynme (Hours)

f f

~

~ 0 bull 0 Q

bull g -- ~

~

bull bull I bull

12 13

Day Time (Hours)

58

~gt =

1312

po 11-10

9

8

deg7

6

- 22collectors1000s

11191195 12 1205 121 1215 122 1225 123 1235

Day Time (Hours)

59

li

i ~

60

the sunset hours

(i) 800s

(ii) 800s 140 - 185 h 20 scycle

61

110100

P 90-~ 80J10 70~ 60~ 50I-

4030

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day TIme (Hours)

110 100 ~

4030

17 19

140h

62

decreasing gt I11i

1917151311

DayTime (Hours)

97

~ 100d1

f(

U 900-lt1l 80l+ 70(ll lt1lQ 60E 50

4030

5

Il

1917

uniform cycle 800s

9

11 13 15

Day Time (Hours)

()fJ

~~ 13

121110

9~ 8 7

7

63

1

08

41 06ugtua0 04u

02

o

7 8 9 10 11 12 13 14 15 16 i7 18 19

Day Time (Hours)

05

04

u 03VIa

0u 02

01

0

7 9 11 13

__ I

64

~

(J

1ltlt

1lt ~

lt)lt

(OC)(i) Uniform 95 87 71 119 065 0315

800s(ii) Non- 95 87 71 119 057 0314

uniform800s

(iii)Non- 93 85 74 118 056 0311uniform550s

65

12115

11

U 105a-~ 101i 95~ 9E~ 85

8757

1195

12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

r Co

66

67

II

U 100o- 90 bullbullJ 80tu~ 70~ 60

~ 504030

5 7 9 11 13 15 17 19Day TIme (Hours)

fr

Ii ~

110

40

30

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

68

Day Time (Hours)

-__-~--~-

(a) CACC

__ ~_L_~_~_

9 10 11 12 13 14 15 16 17 18 19

09

08

07

~ 06gtrr 058 04

03

02

01 -

o

13121110- 9

S 8 7-u 6uot 5u 4

3210

7 8

7 8 9 10 11 1213 14 15 16 17 18 19

Day rfme (Hours)

(b) COP cycle

69

19171513

Day Time (Hours)

(c) COPse

119

04

035

03

025uQ 020v

015

01

005

0

7

151413

U 12~ 11

543

00000deg(1

bull__ J 1 bull ~_J

i195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

70

outlet increases

peak hours

71

~

c

bull~

~r f

~

72

CHAPTER 3

31 Introduction

73

900

100 A 28032005 RERCa

5 7 9 11 13 15 17 19Day Time (Hoursl

III11I

I I

19171513119

900800

E700 ~~ ~ ~

c 600 EJ ~

1~~ ~~ c 300 I d ~ ~

5 7

Day Time (Hours)

74- _- - _~----~~------

800700-NS 600

~- 500c0- 400to-0 300IIIC

- 200nI0V) 100

a ~~ 5 7

II

15 17 19

lIII

600

0

5 7 9 11 13 15 17 19

Day Time (Hours)

75

600

500-NE--= 400A-t

0~ 300 A nl0ent

0 0710 007

5 7 9 11 13 15 17 19Day Time (Hours)

600[J

1500 ~

1

5 9 11 13 15 17 19Day Time (Hours)

76

77

HVm2(Average on 7

years)

March 712 300 188

April 771 340 240

June 568 314 258

August 546 325 266

October 536 312 250

78

-__-------------------------__-_-

l

79

~

125

bed 2

13

i (a) March

bed 2

~bull I

o

-~

85

~[35 LL

115

105 -

G 95o-

1J

(b) April

80

10090-u 800bull

OJl 70J+Ill 60GIQ

EGI 50I-

40

30

bull ~- 11 115 12

Day Time (Hours)

i ~

--J~ -

125 13 I I

I

(c) June

(d) August

115

_____ ~I _ bull i bull -- __

10090 --u 800-~

lo 70s+IVlo 60~Q

E 50~1-

4030

11

81

10- 60QJa-S 50QJl-

40

3011 115 12

Day Time (Hours)

(e) October

I

-J ii

125

J13

(f) December

125 13

82

_-----------------------------------

83

--April--October

Day Time (Hours)

10 11 12 13 14 15 16 17 18 19

bullbull

9

87

16151413121110987654321a

-S0-UUctu

DayTime (Hours)

191817161514

131210 11

(b) COPcycle

9

1

08QI 06Ugt-uQ

0 04u

02

07 8

-J __L- __--L- __ _____ --

Marchampgt=June

=-October

17 18 191614 151310 11 1298

0605

04tv

lVIQ 030u

02

01

0

7

Day Time (Hours)

(c) COPsc

84

85

(b) April

1

Day Time (Hours)

7 l-_---__ ~__ ~ __ ~ __ ~__ ~_~__

1195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

(a) March

12

1194 1199 1204 1209 1214 1219 1224 1229 1234 1239

12115

a- i1e 105C1I3 10~ 95~X 9E 85~ 8

757

Day Time (Hours)

(c) June

-evaporator outlet

1199 1204 1209 1214 1219 1224 1229 1234 1239

13

125

12115

~ 1095

9

1194

-evaporator outlet

13513

G 125o~ 12bullE 11510

~ 11E 105 -

10

959 1- I

1195 12 1205 121 1215 122 1225 123 1235 124

DayTime (Hours)

(d) August

86

r

P 125-

951205 121 1215 122 1225 123 1235 124 1245 125 1255

Day Time (Hours)

(e) October

EQj 11I-

10

1184 1189

___ L __ J__ ~_~ __ J __ -L

1194 1199 1204 1209 1214 1219 1224 1229

Day Time (Hours)

(1) December

87

_----- --------------------------------~-_---

33 Summary

88

---__----------------------------_ -__ _

tt~r~~~~

~

i ~ t

+ bull

1

CHAPTER 4

41 Introduction

89

___________ _ bull ~ bull 4lt

~ or

Chapter 2

90

j bull

1

Designl

Design 2

time

1 1 - 1400s - -End of the

91

V5VIO

SE2

V8

Evaporator

[ __ dere~~~d~I ~ I

1_ - - - -- - - - L - - - - - - -

I ~~-~~-~~=~~-~ II ( Condenser I)

III V4

III

IIIIIII1IIIf

- - - - - - - -1_-_1__-_-_-__-_-_-_Dcooling

loadO

V2

VI

V3

tt

J

i

design 1

bull

12

1

v1

HollVaer ollilel

if Cooling load

CondQnCQf

S IGlcqe tank

design 1

92

I]I]

~ V4III

IfI]I]

I

IVlO

-Evaporator

_ _W _ _ _ __ __r - - -__C_

Condenser

IIIIIII

lXt=-It2 I

I ----- -r------J - 1 r P- -r

IVbull ~

I

i

f t

if~Iii~~

~ t~ ~

design 2

93

_I

(41)

be expressed asdT -

I

1

(42)

(43)

And

Tcr 1in = Twt bull

in case of design 1

94

(45)

(48)

(47)

TbedoUI = Tcrin

nA Idtunrlsettme cr

and

bull

~

95

- __--------__-----__-----------------

96

i~

85

35

255 7 9 11 13 15 17 19 21 23

23

21

~j

19171513

I Jl I I

1197

---L-~ ____~_~ __ ~ I __J_ __ ~ __-

9085r 801

353025

5

Day Time (Hoursl

97

--__----------------------------

7 9 11 13 15 17 19 21 23 25Day Time (Hours)

353025

5

lJ~~(J~ lOS~~

1 ~ 100~- 95~

~ 90r u 85

40353025

5 7 9 11 13 15 17 19 21

I

23

Day Time (Hours)

98

99

--------- _ -- -__-

80-u 700-lt11~ 60J+-(U

50lt11aE 40lt11I-

30

5

DayTIme (Hours)

100

25

23

21

-

21

11 13 15 17 19

Da~Time (Hours)

9

7

90858075-u 700-Q) 65-s 60+ro 55-Q)

353025

5

~fj~

~

95lt

1 90t 85

80u 750- 70lt1J 65J+ 60((

lt1J 55Q

E 50lt1J 45~

40353025

5

101

~

105100

9590

85uo 80-4J 75J 701n 65~ 60e 55Q) 50 r 45 r ~

J 25 __----bull _~-- L I _ __ _~__- Jbull__ -__ _J__

5 7 9 11 11) 15 17 19 21 23

- lt

Day Time Hours)

102

offer better values

103

-

(

10

9

8

7

3

2

1

0

8

~--- bull~ - ct- -+ - - ~ 11 ~

0 ~~ t ~~ ~

~ ~~ ~f

il l 1

- 30 collectors 1400s_---_---_-- __ ---_----- ~_~ __ ~ __ l___ _______ ___ __

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

104

_-----------------------____ --------

(b) COPcycle

11

9

080706

~ 05ugtu 04a0u 03

0201a

7

~

005

03

~ 02c

025

bull~ 015aou 01

8 10 12 14 16 18Day Time(Hours)

20 24

(c) COP soiarnet

105

232119171513

11

Day TIme (Hours)

9

co- e bull

CIClK)ta ~

I

II

OJ

o

7

025

005

1312

1110

9

3 8 7~ 65 - 5

4321o

)

~ 015ltII0

8 01

bullbullbullltu 02c

7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24

DayTime (Hours)

106

~

ltflLIA IIl lj l

l ~ ~ bull j 1

J l f l I ~-

-- gt1 I I -1-_ I I I I I I 1 I

95

85

-u 750-C1l

65s+(0 55C1lcE

45C1l

bullbullbullbull

35

25

~

tIt[~I bull

~I J II

J~tI

~

Day Time Hours)

107

and COP solarnet

(41 Q)

(49)

108

i

~

23

21

ta 11k

19

I 1 J

1715131197

10595

3525

5

Day Time (Hours)

109

I

109

8

7

i 6II- 5uui3 4

3

2

1

0

8 9 10 11 12 13 14 15 16 _ 17 18 19 20 21 22 23 24

Day TIme (Ihours)

Ii

08

07

06

~ 05ugt-u 04

Q

0u 03

02

01

O- 8

1 bull

(b) COP cycle

23

110

10 12 -14 16 18 20 22 24

(c) COPsolarnet

24222Q181614

111

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

10908

Q) 07tl 06e 05~0 04U 03

02010

8

IIIIIIIII

Day Time (Homs)

(b) COP cycle

03025

005

8 10 12 14 16 18

- -

20 22 24

Day Tillie (Hours)

(c) COPsolarnet

112

gti

r-i~

121110

98

i 7II- 6uu~ 5u

4~ 3

21

0

8

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

2422

1-

10

1

09

08

07

06

tugt- 05u0-0u 04

03

02

01

a8

(b) COP cycle

113

2422201816141210

8

02

005

o

025

Day Time (Hours)

(c) COPsolarnet

-t +

40353025

5 7 9 11 13 15 17 1921 23

Day Time (Hours)

114

13-design =de~ign2

1482 1492 1502 1512 1522 1532 1542 1552 1562i

8

12

Day Time (Hours)

14

12 _ =uniform 1400s ~~

I ~- i~l ~

( -P amp- d 4-- ~r ~ ~ 4~

) V~ P~~r - 9 ~ ~ I f ~lt7 1 -

~ (=~

[

13

Elt1lI-

9

8

7

1365 1369 1373 1377 1381 1385 1389 1393 1397 1401 1405 1409

DayTime (Hours)

II115

~l

~~

~

3530

~design 2 -design 1

r _

5 7 9 11 13 15 17 19 21 23

Day Time (Hours)

I

~

~ ~ 116

---L__ _______ ___

~f 7 gt

ff

I I~

fi

07

06

05gtu 04c~u 03QJ

02

01

a

5 6 7 8 9 10 11 12 13 14 15 16 17 18Day Time (Hours)

117

~I

H

I

cycle time ~400s

118

119

I~

i

I-~j~

120

L fj

iI ~

J

~

CHAPTER 5

Thermal Collectors

~

I___L121

j

in Dhaka

dt l UCPiAcp]

122

(5 1 )

(52)

SolarI

Tlterloal Co8ector

(

household use

123

I _~

~Obil - Q

~ ~T ------[lt----------~

ll I~V4

___-L

l

~

(54)

124

-P~_ __ l J

~~ ~

I ~i~

- -- ~ r

~-i

125

125 13

36

33

21

186 8 ~o 12 14

Ibull

9 12

Day Time (Hoursl-

15 18

11bull

126

1 need

i

127

f

q

IjHlIIIiIIij~I

CHAPTER 6

~

bull

of the chiller

875degC

129

IIjf

performance

130

bull

peak hours

I

liters of water

bull

d

performance

131

compression chiller

system

132

~

d

References

133

II

d

J 50-62

134

J

135

J

136

Journal

~

137

_------- _- _ --_ _ __ _---------------------

IIi

-

138

00000001
00000002
00000003
00000004
00000005
00000006
00000007
00000008
00000009
00000010
00000011
00000012
00000013
00000014
00000015
00000016
00000017
00000018
00000019
00000020
00000021
00000022
00000023
00000024
00000025
00000026
00000027
00000028
00000029
00000030
00000031
00000032
00000033
00000034
00000035
00000036
00000037
00000038
00000039
00000040
00000041
00000042
00000043
00000044
00000045
00000046
00000047
00000048
00000049
00000050
00000051
00000052
00000053
00000054
00000055
00000056
00000057
00000058
00000059
00000060
00000061
00000062
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00000064
00000065
00000066
00000067
00000068
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00000070
00000071
00000072
00000073
00000074
00000075
00000076
00000077
00000078
00000079
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00000089
00000090
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00000100
00000101
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00000123
00000124
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00000159
00000160
00000161

Page 8: Full Thesis - Bangladesh University of Engineering and ...

_ _--_--- -

Abstract

heating purposes

VIp

CONTENTS

Board of Examiners

Acknowledgements

Abstract

Nomenclature-

List of Tables

List of Figures

ii

v

vi

viii

xiii

xiv

xv

CHAPTERl (

124 Time Line

Cycle

IX

1

2

3

5

6

7

8

10

11

13

14

17

Refrigeration Cycle

CHAPTER 2

23 Formulation

231 Solar System

Cycle Time

25 Summary

x

18

26

27

353537

3738

39

4041

45

4750

51

54

6071

r ~-I

I j

------

CHAPTER 3

Dhaka

31 Introduction

33 Summary

CHAPTER 4

System Performance

41 Introduction

45 Summary

CHAPTERS

54 Summary

CHAPTER 6

Xl

73

88

89

899094

95

119

121

122

124

127

128

-

Future work

References

Xli

131

133137

r

Nomenclature

A Area (m2)

XliI

------------- __--------~ -_- --- _- _ -

I

r~-I

i

List of Tables

-

XIV

94

I

List of Figures

II

Figure 11

Figure 12

Figure 13

Figure 14

Figure 15

Figure 16

Figure 17

Figure 18

[2009]

cooling system

[2009]

xv

15

16

19

20

21

22

23

24

25

28

[2005])

April

optimum cycle time

XVI

Figure 24

Figure 25

(

cycle 800s

57

58

59

62

Figure 27

Figure 28

Figure 29

140h

then decreasing

cooling capacity

XVII

62

63

64

66

rttI

-

Figure210

Figure 710

Figure 211

Figure 212

Figure 31

hours

cycle -

(a) March

(b) April

(c) June

(d) August

68

69

70

74

75

Figure 31

bullbullbull

(e) October

(t) December

March

XVIII

76

80

months (a)CACC

months (c) COPse

XIX

gt

time 1400s

xx

~I

design 1

for design 2

cycle

COPsolarnet

XXI

104

105

106

107

109

110

III

111

Figure 412

Figure 413

Figure 414

Figure 415

Figure 4J5

COP cycle

COPsolarnet

cooling capacity

time

Figure 416

Figure 417

Figure 418

design 1

design 2

XXII

116

117

118

b

Figure 419

Figure 51

Figure 52

Figure 53

Figure 54

Figure 55

1400s

collector and tank

solar coupling

household

XXIII

CHAPTER

Introduction

11 Introduction

cycle begins again

I

2

--

f

3

e

4

I

i1

Japan

conditioning

cooking

residences

perishable goods

Kettering of GM

distribution

5

Superior Arizona

surface phenomenon

the adsorbate

6

t

--l

7

isotherm etc

8

f

9

(v) Low viscosity

water etc

10

-

io-(

11

I~

f

IIII[

f

I

i

1

12

I

t f

I

i

~~

13

lt A ~ -

of the liquid

cycles lie around 3

14

f

CompressorQpor

~vaporator

Expansion

Condenser

Uquid + porValve

15

-Isobars

( ~

t

~

1

~-

-I--

1 _

1-

f

----4-isobar

1gt1 Y Liquid

--_ 1 Vapor

High Pr

i NH3 Vapour

VapQufc ~

~~n~~t~

Q T j1gt~

1 1~ ~-~- ~ -

Strong Absorb~r -

NHJ solution

16

(Figurel3)

17

18

-~

LoP

II

I

~~

~

-lIT

-

AdsomedI

vapour

Ie

-~oCondensel

heat pumping [2014J

19

~

--

~

LnP

-lff

Q-

ht Qcs~---II

IIIII

bullbullII_~- -

20--_bullbull_--------_- -- _ --_-

-~ -

-

LnP

~

COtliBS + ltii

tlqmssumtttibn -lIT

heat pumping [2014]

21

LnP

-lIT

QcsTcs ===

IIIIIIIIIII_---

heat pumping [2014]

22

I ~ _

I -

i ~i

Ci Pc- bull Wo- InP

bull

PE

I)-

T-o

23

vm

Condenser

SE2

V8

EvaporatorV2 i

II i

r-------

VIrt

i =

Cooling load

system

24

deg IIIIII V4

vs

r -~---~- deg

VI IIi

~

i (IIi= Ii~Ii~ 0

~

V2 V8

Evaporator

adsorbero

SEl

25

installed

process)

26

~

27

8x+amp

lnP

~ ~

a2e a1 a1

bullbull1--T

28

29

)~ 737t tlOr~ lir ~ ~ t 4~24l

bull~f

1~8 234

~

]f~ 123~

o10 20 30 40 50 60 70 80

40

bullbullu30 L

4JI-

2~I-~p

fi20 -

1-ec~gt01)

10 bullbullCd3Cd

r

0

30

et)c~- (JJ-~deg0o~u

5

~

Heatrejected

VIO

Condenser

V8----

Evaporator

r------- J~~ ~_~ IIIIII V4

VI

V2

~

i=1

I

31

---_-bull_----_ - --

32

--_ bull__-----~----------__-__ __ _- -

jiJ

~iAff~l

CONO

(b) ModcB

CONOl

CONOI

(a) ModeA

33

denoted as mode D

mode A

34--_bull_ bull_-----------------__- _

Sumanthy [2004]

35

36

Figure 112

mathematically

ice making purpose

37

~

f ~

lower heat source

38

CHAPTER 2

ofDhaka

39

-~--_ ---_ _ _

40

I

41

-_ __-__-----__----__ __ ~

V4btgt~c- ()- ~0

VIO 00U-

5

VI

- ~~

bull t~

42

(23)

by

transfer fluid

(24)

43

(27)

(26)

(25)

loops

ToUl

state q

(29)

calculated by

Ps(T) = 13332 e [183-3820 1(1-461)] (21 0)

44

(213)

(212)

endojcyclelime

endofcycletime

cycle

number of collector

ao -15587 bo -65314

aj 015915 bl 072452E-Ol

a2 -050612E-03 b2 -023951 E-03

a3 053290E-06 b3 025493E-06

231 Solar System

45

expressed as

where

(214)

(215)

(2 f6)

46

(217)

47

900800

f1E 700

~ 600c2 500+(U-o 400IIIs - 300_(U

0 200til

100o

bull

[l 06042009 RERC [JI

5 7 9 11 13 17 19

Day Time (Hoursl

April

48

49

(218)

am ~--~+-~-~ In ----------- 2 2 Daylength

50

~

i

51

I

161412

4

2

o

I

T 8 9 -10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

52

06

05

Gl 04]~ 03Ou 02

01

o

7 8 9 10 11 12 13 14 15 16 17 18 19

DayTIme (Hours)

03

025

02uIII0 0150u

01

20 collectors

I _~_L L__

i

8 9 10 11 12 13 14 15Day Time (Hours)

16 17 18 19

53

I

-

54

II

55

19

6 i-n bull ~

1715

13Day Time (Hours)

119

Day TIme (Hours)

8 9 10 11 12 13 14 15 16 17 -18 19

18

16

14

12

~ 10lII

Uu 8ctu

6

4

2

0

7

12

j 1~~ lt~

1 08 QI) U gtu 06

Q

0u04

02

0

7

56

191715

13

DayTime (Hours)

10 11 12 13 14 15 16 17 18 19

9

--r bull ~ --_- ---~~-~-~--~~~~- ~ 1~

~ ~

bullbull

8

7

a

03

04

01

u0 028

035

03

005

0

7

DayTime (Hours)

57

12 13

Daynme (Hours)

f f

~

~ 0 bull 0 Q

bull g -- ~

~

bull bull I bull

12 13

Day Time (Hours)

58

~gt =

1312

po 11-10

9

8

deg7

6

- 22collectors1000s

11191195 12 1205 121 1215 122 1225 123 1235

Day Time (Hours)

59

li

i ~

60

the sunset hours

(i) 800s

(ii) 800s 140 - 185 h 20 scycle

61

110100

P 90-~ 80J10 70~ 60~ 50I-

4030

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day TIme (Hours)

110 100 ~

4030

17 19

140h

62

decreasing gt I11i

1917151311

DayTime (Hours)

97

~ 100d1

f(

U 900-lt1l 80l+ 70(ll lt1lQ 60E 50

4030

5

Il

1917

uniform cycle 800s

9

11 13 15

Day Time (Hours)

()fJ

~~ 13

121110

9~ 8 7

7

63

1

08

41 06ugtua0 04u

02

o

7 8 9 10 11 12 13 14 15 16 i7 18 19

Day Time (Hours)

05

04

u 03VIa

0u 02

01

0

7 9 11 13

__ I

64

~

(J

1ltlt

1lt ~

lt)lt

(OC)(i) Uniform 95 87 71 119 065 0315

800s(ii) Non- 95 87 71 119 057 0314

uniform800s

(iii)Non- 93 85 74 118 056 0311uniform550s

65

12115

11

U 105a-~ 101i 95~ 9E~ 85

8757

1195

12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

r Co

66

67

II

U 100o- 90 bullbullJ 80tu~ 70~ 60

~ 504030

5 7 9 11 13 15 17 19Day TIme (Hours)

fr

Ii ~

110

40

30

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

68

Day Time (Hours)

-__-~--~-

(a) CACC

__ ~_L_~_~_

9 10 11 12 13 14 15 16 17 18 19

09

08

07

~ 06gtrr 058 04

03

02

01 -

o

13121110- 9

S 8 7-u 6uot 5u 4

3210

7 8

7 8 9 10 11 1213 14 15 16 17 18 19

Day rfme (Hours)

(b) COP cycle

69

19171513

Day Time (Hours)

(c) COPse

119

04

035

03

025uQ 020v

015

01

005

0

7

151413

U 12~ 11

543

00000deg(1

bull__ J 1 bull ~_J

i195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

70

outlet increases

peak hours

71

~

c

bull~

~r f

~

72

CHAPTER 3

31 Introduction

73

900

100 A 28032005 RERCa

5 7 9 11 13 15 17 19Day Time (Hoursl

III11I

I I

19171513119

900800

E700 ~~ ~ ~

c 600 EJ ~

1~~ ~~ c 300 I d ~ ~

5 7

Day Time (Hours)

74- _- - _~----~~------

800700-NS 600

~- 500c0- 400to-0 300IIIC

- 200nI0V) 100

a ~~ 5 7

II

15 17 19

lIII

600

0

5 7 9 11 13 15 17 19

Day Time (Hours)

75

600

500-NE--= 400A-t

0~ 300 A nl0ent

0 0710 007

5 7 9 11 13 15 17 19Day Time (Hours)

600[J

1500 ~

1

5 9 11 13 15 17 19Day Time (Hours)

76

77

HVm2(Average on 7

years)

March 712 300 188

April 771 340 240

June 568 314 258

August 546 325 266

October 536 312 250

78

-__-------------------------__-_-

l

79

~

125

bed 2

13

i (a) March

bed 2

~bull I

o

-~

85

~[35 LL

115

105 -

G 95o-

1J

(b) April

80

10090-u 800bull

OJl 70J+Ill 60GIQ

EGI 50I-

40

30

bull ~- 11 115 12

Day Time (Hours)

i ~

--J~ -

125 13 I I

I

(c) June

(d) August

115

_____ ~I _ bull i bull -- __

10090 --u 800-~

lo 70s+IVlo 60~Q

E 50~1-

4030

11

81

10- 60QJa-S 50QJl-

40

3011 115 12

Day Time (Hours)

(e) October

I

-J ii

125

J13

(f) December

125 13

82

_-----------------------------------

83

--April--October

Day Time (Hours)

10 11 12 13 14 15 16 17 18 19

bullbull

9

87

16151413121110987654321a

-S0-UUctu

DayTime (Hours)

191817161514

131210 11

(b) COPcycle

9

1

08QI 06Ugt-uQ

0 04u

02

07 8

-J __L- __--L- __ _____ --

Marchampgt=June

=-October

17 18 191614 151310 11 1298

0605

04tv

lVIQ 030u

02

01

0

7

Day Time (Hours)

(c) COPsc

84

85

(b) April

1

Day Time (Hours)

7 l-_---__ ~__ ~ __ ~ __ ~__ ~_~__

1195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

(a) March

12

1194 1199 1204 1209 1214 1219 1224 1229 1234 1239

12115

a- i1e 105C1I3 10~ 95~X 9E 85~ 8

757

Day Time (Hours)

(c) June

-evaporator outlet

1199 1204 1209 1214 1219 1224 1229 1234 1239

13

125

12115

~ 1095

9

1194

-evaporator outlet

13513

G 125o~ 12bullE 11510

~ 11E 105 -

10

959 1- I

1195 12 1205 121 1215 122 1225 123 1235 124

DayTime (Hours)

(d) August

86

r

P 125-

951205 121 1215 122 1225 123 1235 124 1245 125 1255

Day Time (Hours)

(e) October

EQj 11I-

10

1184 1189

___ L __ J__ ~_~ __ J __ -L

1194 1199 1204 1209 1214 1219 1224 1229

Day Time (Hours)

(1) December

87

_----- --------------------------------~-_---

33 Summary

88

---__----------------------------_ -__ _

tt~r~~~~

~

i ~ t

+ bull

1

CHAPTER 4

41 Introduction

89

___________ _ bull ~ bull 4lt

~ or

Chapter 2

90

j bull

1

Designl

Design 2

time

1 1 - 1400s - -End of the

91

V5VIO

SE2

V8

Evaporator

[ __ dere~~~d~I ~ I

1_ - - - -- - - - L - - - - - - -

I ~~-~~-~~=~~-~ II ( Condenser I)

III V4

III

IIIIIII1IIIf

- - - - - - - -1_-_1__-_-_-__-_-_-_Dcooling

loadO

V2

VI

V3

tt

J

i

design 1

bull

12

1

v1

HollVaer ollilel

if Cooling load

CondQnCQf

S IGlcqe tank

design 1

92

I]I]

~ V4III

IfI]I]

I

IVlO

-Evaporator

_ _W _ _ _ __ __r - - -__C_

Condenser

IIIIIII

lXt=-It2 I

I ----- -r------J - 1 r P- -r

IVbull ~

I

i

f t

if~Iii~~

~ t~ ~

design 2

93

_I

(41)

be expressed asdT -

I

1

(42)

(43)

And

Tcr 1in = Twt bull

in case of design 1

94

(45)

(48)

(47)

TbedoUI = Tcrin

nA Idtunrlsettme cr

and

bull

~

95

- __--------__-----__-----------------

96

i~

85

35

255 7 9 11 13 15 17 19 21 23

23

21

~j

19171513

I Jl I I

1197

---L-~ ____~_~ __ ~ I __J_ __ ~ __-

9085r 801

353025

5

Day Time (Hoursl

97

--__----------------------------

7 9 11 13 15 17 19 21 23 25Day Time (Hours)

353025

5

lJ~~(J~ lOS~~

1 ~ 100~- 95~

~ 90r u 85

40353025

5 7 9 11 13 15 17 19 21

I

23

Day Time (Hours)

98

99

--------- _ -- -__-

80-u 700-lt11~ 60J+-(U

50lt11aE 40lt11I-

30

5

DayTIme (Hours)

100

25

23

21

-

21

11 13 15 17 19

Da~Time (Hours)

9

7

90858075-u 700-Q) 65-s 60+ro 55-Q)

353025

5

~fj~

~

95lt

1 90t 85

80u 750- 70lt1J 65J+ 60((

lt1J 55Q

E 50lt1J 45~

40353025

5

101

~

105100

9590

85uo 80-4J 75J 701n 65~ 60e 55Q) 50 r 45 r ~

J 25 __----bull _~-- L I _ __ _~__- Jbull__ -__ _J__

5 7 9 11 11) 15 17 19 21 23

- lt

Day Time Hours)

102

offer better values

103

-

(

10

9

8

7

3

2

1

0

8

~--- bull~ - ct- -+ - - ~ 11 ~

0 ~~ t ~~ ~

~ ~~ ~f

il l 1

- 30 collectors 1400s_---_---_-- __ ---_----- ~_~ __ ~ __ l___ _______ ___ __

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

104

_-----------------------____ --------

(b) COPcycle

11

9

080706

~ 05ugtu 04a0u 03

0201a

7

~

005

03

~ 02c

025

bull~ 015aou 01

8 10 12 14 16 18Day Time(Hours)

20 24

(c) COP soiarnet

105

232119171513

11

Day TIme (Hours)

9

co- e bull

CIClK)ta ~

I

II

OJ

o

7

025

005

1312

1110

9

3 8 7~ 65 - 5

4321o

)

~ 015ltII0

8 01

bullbullbullltu 02c

7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24

DayTime (Hours)

106

~

ltflLIA IIl lj l

l ~ ~ bull j 1

J l f l I ~-

-- gt1 I I -1-_ I I I I I I 1 I

95

85

-u 750-C1l

65s+(0 55C1lcE

45C1l

bullbullbullbull

35

25

~

tIt[~I bull

~I J II

J~tI

~

Day Time Hours)

107

and COP solarnet

(41 Q)

(49)

108

i

~

23

21

ta 11k

19

I 1 J

1715131197

10595

3525

5

Day Time (Hours)

109

I

109

8

7

i 6II- 5uui3 4

3

2

1

0

8 9 10 11 12 13 14 15 16 _ 17 18 19 20 21 22 23 24

Day TIme (Ihours)

Ii

08

07

06

~ 05ugt-u 04

Q

0u 03

02

01

O- 8

1 bull

(b) COP cycle

23

110

10 12 -14 16 18 20 22 24

(c) COPsolarnet

24222Q181614

111

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

10908

Q) 07tl 06e 05~0 04U 03

02010

8

IIIIIIIII

Day Time (Homs)

(b) COP cycle

03025

005

8 10 12 14 16 18

- -

20 22 24

Day Tillie (Hours)

(c) COPsolarnet

112

gti

r-i~

121110

98

i 7II- 6uu~ 5u

4~ 3

21

0

8

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

2422

1-

10

1

09

08

07

06

tugt- 05u0-0u 04

03

02

01

a8

(b) COP cycle

113

2422201816141210

8

02

005

o

025

Day Time (Hours)

(c) COPsolarnet

-t +

40353025

5 7 9 11 13 15 17 1921 23

Day Time (Hours)

114

13-design =de~ign2

1482 1492 1502 1512 1522 1532 1542 1552 1562i

8

12

Day Time (Hours)

14

12 _ =uniform 1400s ~~

I ~- i~l ~

( -P amp- d 4-- ~r ~ ~ 4~

) V~ P~~r - 9 ~ ~ I f ~lt7 1 -

~ (=~

[

13

Elt1lI-

9

8

7

1365 1369 1373 1377 1381 1385 1389 1393 1397 1401 1405 1409

DayTime (Hours)

II115

~l

~~

~

3530

~design 2 -design 1

r _

5 7 9 11 13 15 17 19 21 23

Day Time (Hours)

I

~

~ ~ 116

---L__ _______ ___

~f 7 gt

ff

I I~

fi

07

06

05gtu 04c~u 03QJ

02

01

a

5 6 7 8 9 10 11 12 13 14 15 16 17 18Day Time (Hours)

117

~I

H

I

cycle time ~400s

118

119

I~

i

I-~j~

120

L fj

iI ~

J

~

CHAPTER 5

Thermal Collectors

~

I___L121

j

in Dhaka

dt l UCPiAcp]

122

(5 1 )

(52)

SolarI

Tlterloal Co8ector

(

household use

123

I _~

~Obil - Q

~ ~T ------[lt----------~

ll I~V4

___-L

l

~

(54)

124

-P~_ __ l J

~~ ~

I ~i~

- -- ~ r

~-i

125

125 13

36

33

21

186 8 ~o 12 14

Ibull

9 12

Day Time (Hoursl-

15 18

11bull

126

1 need

i

127

f

q

IjHlIIIiIIij~I

CHAPTER 6

~

bull

of the chiller

875degC

129

IIjf

performance

130

bull

peak hours

I

liters of water

bull

d

performance

131

compression chiller

system

132

~

d

References

133

II

d

J 50-62

134

J

135

J

136

Journal

~

137

_------- _- _ --_ _ __ _---------------------

IIi

-

138

00000001
00000002
00000003
00000004
00000005
00000006
00000007
00000008
00000009
00000010
00000011
00000012
00000013
00000014
00000015
00000016
00000017
00000018
00000019
00000020
00000021
00000022
00000023
00000024
00000025
00000026
00000027
00000028
00000029
00000030
00000031
00000032
00000033
00000034
00000035
00000036
00000037
00000038
00000039
00000040
00000041
00000042
00000043
00000044
00000045
00000046
00000047
00000048
00000049
00000050
00000051
00000052
00000053
00000054
00000055
00000056
00000057
00000058
00000059
00000060
00000061
00000062
00000063
00000064
00000065
00000066
00000067
00000068
00000069
00000070
00000071
00000072
00000073
00000074
00000075
00000076
00000077
00000078
00000079
00000080
00000081
00000082
00000083
00000084
00000085
00000086
00000087
00000088
00000089
00000090
00000091
00000092
00000093
00000094
00000095
00000096
00000097
00000098
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00000100
00000101
00000102
00000103
00000104
00000105
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00000107
00000108
00000109
00000110
00000111
00000112
00000113
00000114
00000115
00000116
00000117
00000118
00000119
00000120
00000121
00000122
00000123
00000124
00000125
00000126
00000127
00000128
00000129
00000130
00000131
00000132
00000133
00000134
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00000136
00000137
00000138
00000139
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00000143
00000144
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00000159
00000160
00000161

Page 9: Full Thesis - Bangladesh University of Engineering and ...

CONTENTS

Board of Examiners

Acknowledgements

Abstract

Nomenclature-

List of Tables

List of Figures

ii

v

vi

viii

xiii

xiv

xv

CHAPTERl (

124 Time Line

Cycle

IX

1

2

3

5

6

7

8

10

11

13

14

17

Refrigeration Cycle

CHAPTER 2

23 Formulation

231 Solar System

Cycle Time

25 Summary

x

18

26

27

353537

3738

39

4041

45

4750

51

54

6071

r ~-I

I j

------

CHAPTER 3

Dhaka

31 Introduction

33 Summary

CHAPTER 4

System Performance

41 Introduction

45 Summary

CHAPTERS

54 Summary

CHAPTER 6

Xl

73

88

89

899094

95

119

121

122

124

127

128

-

Future work

References

Xli

131

133137

r

Nomenclature

A Area (m2)

XliI

------------- __--------~ -_- --- _- _ -

I

r~-I

i

List of Tables

-

XIV

94

I

List of Figures

II

Figure 11

Figure 12

Figure 13

Figure 14

Figure 15

Figure 16

Figure 17

Figure 18

[2009]

cooling system

[2009]

xv

15

16

19

20

21

22

23

24

25

28

[2005])

April

optimum cycle time

XVI

Figure 24

Figure 25

(

cycle 800s

57

58

59

62

Figure 27

Figure 28

Figure 29

140h

then decreasing

cooling capacity

XVII

62

63

64

66

rttI

-

Figure210

Figure 710

Figure 211

Figure 212

Figure 31

hours

cycle -

(a) March

(b) April

(c) June

(d) August

68

69

70

74

75

Figure 31

bullbullbull

(e) October

(t) December

March

XVIII

76

80

months (a)CACC

months (c) COPse

XIX

gt

time 1400s

xx

~I

design 1

for design 2

cycle

COPsolarnet

XXI

104

105

106

107

109

110

III

111

Figure 412

Figure 413

Figure 414

Figure 415

Figure 4J5

COP cycle

COPsolarnet

cooling capacity

time

Figure 416

Figure 417

Figure 418

design 1

design 2

XXII

116

117

118

b

Figure 419

Figure 51

Figure 52

Figure 53

Figure 54

Figure 55

1400s

collector and tank

solar coupling

household

XXIII

CHAPTER

Introduction

11 Introduction

cycle begins again

I

2

--

f

3

e

4

I

i1

Japan

conditioning

cooking

residences

perishable goods

Kettering of GM

distribution

5

Superior Arizona

surface phenomenon

the adsorbate

6

t

--l

7

isotherm etc

8

f

9

(v) Low viscosity

water etc

10

-

io-(

11

I~

f

IIII[

f

I

i

1

12

I

t f

I

i

~~

13

lt A ~ -

of the liquid

cycles lie around 3

14

f

CompressorQpor

~vaporator

Expansion

Condenser

Uquid + porValve

15

-Isobars

( ~

t

~

1

~-

-I--

1 _

1-

f

----4-isobar

1gt1 Y Liquid

--_ 1 Vapor

High Pr

i NH3 Vapour

VapQufc ~

~~n~~t~

Q T j1gt~

1 1~ ~-~- ~ -

Strong Absorb~r -

NHJ solution

16

(Figurel3)

17

18

-~

LoP

II

I

~~

~

-lIT

-

AdsomedI

vapour

Ie

-~oCondensel

heat pumping [2014J

19

~

--

~

LnP

-lff

Q-

ht Qcs~---II

IIIII

bullbullII_~- -

20--_bullbull_--------_- -- _ --_-

-~ -

-

LnP

~

COtliBS + ltii

tlqmssumtttibn -lIT

heat pumping [2014]

21

LnP

-lIT

QcsTcs ===

IIIIIIIIIII_---

heat pumping [2014]

22

I ~ _

I -

i ~i

Ci Pc- bull Wo- InP

bull

PE

I)-

T-o

23

vm

Condenser

SE2

V8

EvaporatorV2 i

II i

r-------

VIrt

i =

Cooling load

system

24

deg IIIIII V4

vs

r -~---~- deg

VI IIi

~

i (IIi= Ii~Ii~ 0

~

V2 V8

Evaporator

adsorbero

SEl

25

installed

process)

26

~

27

8x+amp

lnP

~ ~

a2e a1 a1

bullbull1--T

28

29

)~ 737t tlOr~ lir ~ ~ t 4~24l

bull~f

1~8 234

~

]f~ 123~

o10 20 30 40 50 60 70 80

40

bullbullu30 L

4JI-

2~I-~p

fi20 -

1-ec~gt01)

10 bullbullCd3Cd

r

0

30

et)c~- (JJ-~deg0o~u

5

~

Heatrejected

VIO

Condenser

V8----

Evaporator

r------- J~~ ~_~ IIIIII V4

VI

V2

~

i=1

I

31

---_-bull_----_ - --

32

--_ bull__-----~----------__-__ __ _- -

jiJ

~iAff~l

CONO

(b) ModcB

CONOl

CONOI

(a) ModeA

33

denoted as mode D

mode A

34--_bull_ bull_-----------------__- _

Sumanthy [2004]

35

36

Figure 112

mathematically

ice making purpose

37

~

f ~

lower heat source

38

CHAPTER 2

ofDhaka

39

-~--_ ---_ _ _

40

I

41

-_ __-__-----__----__ __ ~

V4btgt~c- ()- ~0

VIO 00U-

5

VI

- ~~

bull t~

42

(23)

by

transfer fluid

(24)

43

(27)

(26)

(25)

loops

ToUl

state q

(29)

calculated by

Ps(T) = 13332 e [183-3820 1(1-461)] (21 0)

44

(213)

(212)

endojcyclelime

endofcycletime

cycle

number of collector

ao -15587 bo -65314

aj 015915 bl 072452E-Ol

a2 -050612E-03 b2 -023951 E-03

a3 053290E-06 b3 025493E-06

231 Solar System

45

expressed as

where

(214)

(215)

(2 f6)

46

(217)

47

900800

f1E 700

~ 600c2 500+(U-o 400IIIs - 300_(U

0 200til

100o

bull

[l 06042009 RERC [JI

5 7 9 11 13 17 19

Day Time (Hoursl

April

48

49

(218)

am ~--~+-~-~ In ----------- 2 2 Daylength

50

~

i

51

I

161412

4

2

o

I

T 8 9 -10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

52

06

05

Gl 04]~ 03Ou 02

01

o

7 8 9 10 11 12 13 14 15 16 17 18 19

DayTIme (Hours)

03

025

02uIII0 0150u

01

20 collectors

I _~_L L__

i

8 9 10 11 12 13 14 15Day Time (Hours)

16 17 18 19

53

I

-

54

II

55

19

6 i-n bull ~

1715

13Day Time (Hours)

119

Day TIme (Hours)

8 9 10 11 12 13 14 15 16 17 -18 19

18

16

14

12

~ 10lII

Uu 8ctu

6

4

2

0

7

12

j 1~~ lt~

1 08 QI) U gtu 06

Q

0u04

02

0

7

56

191715

13

DayTime (Hours)

10 11 12 13 14 15 16 17 18 19

9

--r bull ~ --_- ---~~-~-~--~~~~- ~ 1~

~ ~

bullbull

8

7

a

03

04

01

u0 028

035

03

005

0

7

DayTime (Hours)

57

12 13

Daynme (Hours)

f f

~

~ 0 bull 0 Q

bull g -- ~

~

bull bull I bull

12 13

Day Time (Hours)

58

~gt =

1312

po 11-10

9

8

deg7

6

- 22collectors1000s

11191195 12 1205 121 1215 122 1225 123 1235

Day Time (Hours)

59

li

i ~

60

the sunset hours

(i) 800s

(ii) 800s 140 - 185 h 20 scycle

61

110100

P 90-~ 80J10 70~ 60~ 50I-

4030

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day TIme (Hours)

110 100 ~

4030

17 19

140h

62

decreasing gt I11i

1917151311

DayTime (Hours)

97

~ 100d1

f(

U 900-lt1l 80l+ 70(ll lt1lQ 60E 50

4030

5

Il

1917

uniform cycle 800s

9

11 13 15

Day Time (Hours)

()fJ

~~ 13

121110

9~ 8 7

7

63

1

08

41 06ugtua0 04u

02

o

7 8 9 10 11 12 13 14 15 16 i7 18 19

Day Time (Hours)

05

04

u 03VIa

0u 02

01

0

7 9 11 13

__ I

64

~

(J

1ltlt

1lt ~

lt)lt

(OC)(i) Uniform 95 87 71 119 065 0315

800s(ii) Non- 95 87 71 119 057 0314

uniform800s

(iii)Non- 93 85 74 118 056 0311uniform550s

65

12115

11

U 105a-~ 101i 95~ 9E~ 85

8757

1195

12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

r Co

66

67

II

U 100o- 90 bullbullJ 80tu~ 70~ 60

~ 504030

5 7 9 11 13 15 17 19Day TIme (Hours)

fr

Ii ~

110

40

30

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

68

Day Time (Hours)

-__-~--~-

(a) CACC

__ ~_L_~_~_

9 10 11 12 13 14 15 16 17 18 19

09

08

07

~ 06gtrr 058 04

03

02

01 -

o

13121110- 9

S 8 7-u 6uot 5u 4

3210

7 8

7 8 9 10 11 1213 14 15 16 17 18 19

Day rfme (Hours)

(b) COP cycle

69

19171513

Day Time (Hours)

(c) COPse

119

04

035

03

025uQ 020v

015

01

005

0

7

151413

U 12~ 11

543

00000deg(1

bull__ J 1 bull ~_J

i195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

70

outlet increases

peak hours

71

~

c

bull~

~r f

~

72

CHAPTER 3

31 Introduction

73

900

100 A 28032005 RERCa

5 7 9 11 13 15 17 19Day Time (Hoursl

III11I

I I

19171513119

900800

E700 ~~ ~ ~

c 600 EJ ~

1~~ ~~ c 300 I d ~ ~

5 7

Day Time (Hours)

74- _- - _~----~~------

800700-NS 600

~- 500c0- 400to-0 300IIIC

- 200nI0V) 100

a ~~ 5 7

II

15 17 19

lIII

600

0

5 7 9 11 13 15 17 19

Day Time (Hours)

75

600

500-NE--= 400A-t

0~ 300 A nl0ent

0 0710 007

5 7 9 11 13 15 17 19Day Time (Hours)

600[J

1500 ~

1

5 9 11 13 15 17 19Day Time (Hours)

76

77

HVm2(Average on 7

years)

March 712 300 188

April 771 340 240

June 568 314 258

August 546 325 266

October 536 312 250

78

-__-------------------------__-_-

l

79

~

125

bed 2

13

i (a) March

bed 2

~bull I

o

-~

85

~[35 LL

115

105 -

G 95o-

1J

(b) April

80

10090-u 800bull

OJl 70J+Ill 60GIQ

EGI 50I-

40

30

bull ~- 11 115 12

Day Time (Hours)

i ~

--J~ -

125 13 I I

I

(c) June

(d) August

115

_____ ~I _ bull i bull -- __

10090 --u 800-~

lo 70s+IVlo 60~Q

E 50~1-

4030

11

81

10- 60QJa-S 50QJl-

40

3011 115 12

Day Time (Hours)

(e) October

I

-J ii

125

J13

(f) December

125 13

82

_-----------------------------------

83

--April--October

Day Time (Hours)

10 11 12 13 14 15 16 17 18 19

bullbull

9

87

16151413121110987654321a

-S0-UUctu

DayTime (Hours)

191817161514

131210 11

(b) COPcycle

9

1

08QI 06Ugt-uQ

0 04u

02

07 8

-J __L- __--L- __ _____ --

Marchampgt=June

=-October

17 18 191614 151310 11 1298

0605

04tv

lVIQ 030u

02

01

0

7

Day Time (Hours)

(c) COPsc

84

85

(b) April

1

Day Time (Hours)

7 l-_---__ ~__ ~ __ ~ __ ~__ ~_~__

1195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

(a) March

12

1194 1199 1204 1209 1214 1219 1224 1229 1234 1239

12115

a- i1e 105C1I3 10~ 95~X 9E 85~ 8

757

Day Time (Hours)

(c) June

-evaporator outlet

1199 1204 1209 1214 1219 1224 1229 1234 1239

13

125

12115

~ 1095

9

1194

-evaporator outlet

13513

G 125o~ 12bullE 11510

~ 11E 105 -

10

959 1- I

1195 12 1205 121 1215 122 1225 123 1235 124

DayTime (Hours)

(d) August

86

r

P 125-

951205 121 1215 122 1225 123 1235 124 1245 125 1255

Day Time (Hours)

(e) October

EQj 11I-

10

1184 1189

___ L __ J__ ~_~ __ J __ -L

1194 1199 1204 1209 1214 1219 1224 1229

Day Time (Hours)

(1) December

87

_----- --------------------------------~-_---

33 Summary

88

---__----------------------------_ -__ _

tt~r~~~~

~

i ~ t

+ bull

1

CHAPTER 4

41 Introduction

89

___________ _ bull ~ bull 4lt

~ or

Chapter 2

90

j bull

1

Designl

Design 2

time

1 1 - 1400s - -End of the

91

V5VIO

SE2

V8

Evaporator

[ __ dere~~~d~I ~ I

1_ - - - -- - - - L - - - - - - -

I ~~-~~-~~=~~-~ II ( Condenser I)

III V4

III

IIIIIII1IIIf

- - - - - - - -1_-_1__-_-_-__-_-_-_Dcooling

loadO

V2

VI

V3

tt

J

i

design 1

bull

12

1

v1

HollVaer ollilel

if Cooling load

CondQnCQf

S IGlcqe tank

design 1

92

I]I]

~ V4III

IfI]I]

I

IVlO

-Evaporator

_ _W _ _ _ __ __r - - -__C_

Condenser

IIIIIII

lXt=-It2 I

I ----- -r------J - 1 r P- -r

IVbull ~

I

i

f t

if~Iii~~

~ t~ ~

design 2

93

_I

(41)

be expressed asdT -

I

1

(42)

(43)

And

Tcr 1in = Twt bull

in case of design 1

94

(45)

(48)

(47)

TbedoUI = Tcrin

nA Idtunrlsettme cr

and

bull

~

95

- __--------__-----__-----------------

96

i~

85

35

255 7 9 11 13 15 17 19 21 23

23

21

~j

19171513

I Jl I I

1197

---L-~ ____~_~ __ ~ I __J_ __ ~ __-

9085r 801

353025

5

Day Time (Hoursl

97

--__----------------------------

7 9 11 13 15 17 19 21 23 25Day Time (Hours)

353025

5

lJ~~(J~ lOS~~

1 ~ 100~- 95~

~ 90r u 85

40353025

5 7 9 11 13 15 17 19 21

I

23

Day Time (Hours)

98

99

--------- _ -- -__-

80-u 700-lt11~ 60J+-(U

50lt11aE 40lt11I-

30

5

DayTIme (Hours)

100

25

23

21

-

21

11 13 15 17 19

Da~Time (Hours)

9

7

90858075-u 700-Q) 65-s 60+ro 55-Q)

353025

5

~fj~

~

95lt

1 90t 85

80u 750- 70lt1J 65J+ 60((

lt1J 55Q

E 50lt1J 45~

40353025

5

101

~

105100

9590

85uo 80-4J 75J 701n 65~ 60e 55Q) 50 r 45 r ~

J 25 __----bull _~-- L I _ __ _~__- Jbull__ -__ _J__

5 7 9 11 11) 15 17 19 21 23

- lt

Day Time Hours)

102

offer better values

103

-

(

10

9

8

7

3

2

1

0

8

~--- bull~ - ct- -+ - - ~ 11 ~

0 ~~ t ~~ ~

~ ~~ ~f

il l 1

- 30 collectors 1400s_---_---_-- __ ---_----- ~_~ __ ~ __ l___ _______ ___ __

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

104

_-----------------------____ --------

(b) COPcycle

11

9

080706

~ 05ugtu 04a0u 03

0201a

7

~

005

03

~ 02c

025

bull~ 015aou 01

8 10 12 14 16 18Day Time(Hours)

20 24

(c) COP soiarnet

105

232119171513

11

Day TIme (Hours)

9

co- e bull

CIClK)ta ~

I

II

OJ

o

7

025

005

1312

1110

9

3 8 7~ 65 - 5

4321o

)

~ 015ltII0

8 01

bullbullbullltu 02c

7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24

DayTime (Hours)

106

~

ltflLIA IIl lj l

l ~ ~ bull j 1

J l f l I ~-

-- gt1 I I -1-_ I I I I I I 1 I

95

85

-u 750-C1l

65s+(0 55C1lcE

45C1l

bullbullbullbull

35

25

~

tIt[~I bull

~I J II

J~tI

~

Day Time Hours)

107

and COP solarnet

(41 Q)

(49)

108

i

~

23

21

ta 11k

19

I 1 J

1715131197

10595

3525

5

Day Time (Hours)

109

I

109

8

7

i 6II- 5uui3 4

3

2

1

0

8 9 10 11 12 13 14 15 16 _ 17 18 19 20 21 22 23 24

Day TIme (Ihours)

Ii

08

07

06

~ 05ugt-u 04

Q

0u 03

02

01

O- 8

1 bull

(b) COP cycle

23

110

10 12 -14 16 18 20 22 24

(c) COPsolarnet

24222Q181614

111

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

10908

Q) 07tl 06e 05~0 04U 03

02010

8

IIIIIIIII

Day Time (Homs)

(b) COP cycle

03025

005

8 10 12 14 16 18

- -

20 22 24

Day Tillie (Hours)

(c) COPsolarnet

112

gti

r-i~

121110

98

i 7II- 6uu~ 5u

4~ 3

21

0

8

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

2422

1-

10

1

09

08

07

06

tugt- 05u0-0u 04

03

02

01

a8

(b) COP cycle

113

2422201816141210

8

02

005

o

025

Day Time (Hours)

(c) COPsolarnet

-t +

40353025

5 7 9 11 13 15 17 1921 23

Day Time (Hours)

114

13-design =de~ign2

1482 1492 1502 1512 1522 1532 1542 1552 1562i

8

12

Day Time (Hours)

14

12 _ =uniform 1400s ~~

I ~- i~l ~

( -P amp- d 4-- ~r ~ ~ 4~

) V~ P~~r - 9 ~ ~ I f ~lt7 1 -

~ (=~

[

13

Elt1lI-

9

8

7

1365 1369 1373 1377 1381 1385 1389 1393 1397 1401 1405 1409

DayTime (Hours)

II115

~l

~~

~

3530

~design 2 -design 1

r _

5 7 9 11 13 15 17 19 21 23

Day Time (Hours)

I

~

~ ~ 116

---L__ _______ ___

~f 7 gt

ff

I I~

fi

07

06

05gtu 04c~u 03QJ

02

01

a

5 6 7 8 9 10 11 12 13 14 15 16 17 18Day Time (Hours)

117

~I

H

I

cycle time ~400s

118

119

I~

i

I-~j~

120

L fj

iI ~

J

~

CHAPTER 5

Thermal Collectors

~

I___L121

j

in Dhaka

dt l UCPiAcp]

122

(5 1 )

(52)

SolarI

Tlterloal Co8ector

(

household use

123

I _~

~Obil - Q

~ ~T ------[lt----------~

ll I~V4

___-L

l

~

(54)

124

-P~_ __ l J

~~ ~

I ~i~

- -- ~ r

~-i

125

125 13

36

33

21

186 8 ~o 12 14

Ibull

9 12

Day Time (Hoursl-

15 18

11bull

126

1 need

i

127

f

q

IjHlIIIiIIij~I

CHAPTER 6

~

bull

of the chiller

875degC

129

IIjf

performance

130

bull

peak hours

I

liters of water

bull

d

performance

131

compression chiller

system

132

~

d

References

133

II

d

J 50-62

134

J

135

J

136

Journal

~

137

_------- _- _ --_ _ __ _---------------------

IIi

-

138

00000001
00000002
00000003
00000004
00000005
00000006
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00000161

Page 10: Full Thesis - Bangladesh University of Engineering and ...

Refrigeration Cycle

CHAPTER 2

23 Formulation

231 Solar System

Cycle Time

25 Summary

x

18

26

27

353537

3738

39

4041

45

4750

51

54

6071

r ~-I

I j

------

CHAPTER 3

Dhaka

31 Introduction

33 Summary

CHAPTER 4

System Performance

41 Introduction

45 Summary

CHAPTERS

54 Summary

CHAPTER 6

Xl

73

88

89

899094

95

119

121

122

124

127

128

-

Future work

References

Xli

131

133137

r

Nomenclature

A Area (m2)

XliI

------------- __--------~ -_- --- _- _ -

I

r~-I

i

List of Tables

-

XIV

94

I

List of Figures

II

Figure 11

Figure 12

Figure 13

Figure 14

Figure 15

Figure 16

Figure 17

Figure 18

[2009]

cooling system

[2009]

xv

15

16

19

20

21

22

23

24

25

28

[2005])

April

optimum cycle time

XVI

Figure 24

Figure 25

(

cycle 800s

57

58

59

62

Figure 27

Figure 28

Figure 29

140h

then decreasing

cooling capacity

XVII

62

63

64

66

rttI

-

Figure210

Figure 710

Figure 211

Figure 212

Figure 31

hours

cycle -

(a) March

(b) April

(c) June

(d) August

68

69

70

74

75

Figure 31

bullbullbull

(e) October

(t) December

March

XVIII

76

80

months (a)CACC

months (c) COPse

XIX

gt

time 1400s

xx

~I

design 1

for design 2

cycle

COPsolarnet

XXI

104

105

106

107

109

110

III

111

Figure 412

Figure 413

Figure 414

Figure 415

Figure 4J5

COP cycle

COPsolarnet

cooling capacity

time

Figure 416

Figure 417

Figure 418

design 1

design 2

XXII

116

117

118

b

Figure 419

Figure 51

Figure 52

Figure 53

Figure 54

Figure 55

1400s

collector and tank

solar coupling

household

XXIII

CHAPTER

Introduction

11 Introduction

cycle begins again

I

2

--

f

3

e

4

I

i1

Japan

conditioning

cooking

residences

perishable goods

Kettering of GM

distribution

5

Superior Arizona

surface phenomenon

the adsorbate

6

t

--l

7

isotherm etc

8

f

9

(v) Low viscosity

water etc

10

-

io-(

11

I~

f

IIII[

f

I

i

1

12

I

t f

I

i

~~

13

lt A ~ -

of the liquid

cycles lie around 3

14

f

CompressorQpor

~vaporator

Expansion

Condenser

Uquid + porValve

15

-Isobars

( ~

t

~

1

~-

-I--

1 _

1-

f

----4-isobar

1gt1 Y Liquid

--_ 1 Vapor

High Pr

i NH3 Vapour

VapQufc ~

~~n~~t~

Q T j1gt~

1 1~ ~-~- ~ -

Strong Absorb~r -

NHJ solution

16

(Figurel3)

17

18

-~

LoP

II

I

~~

~

-lIT

-

AdsomedI

vapour

Ie

-~oCondensel

heat pumping [2014J

19

~

--

~

LnP

-lff

Q-

ht Qcs~---II

IIIII

bullbullII_~- -

20--_bullbull_--------_- -- _ --_-

-~ -

-

LnP

~

COtliBS + ltii

tlqmssumtttibn -lIT

heat pumping [2014]

21

LnP

-lIT

QcsTcs ===

IIIIIIIIIII_---

heat pumping [2014]

22

I ~ _

I -

i ~i

Ci Pc- bull Wo- InP

bull

PE

I)-

T-o

23

vm

Condenser

SE2

V8

EvaporatorV2 i

II i

r-------

VIrt

i =

Cooling load

system

24

deg IIIIII V4

vs

r -~---~- deg

VI IIi

~

i (IIi= Ii~Ii~ 0

~

V2 V8

Evaporator

adsorbero

SEl

25

installed

process)

26

~

27

8x+amp

lnP

~ ~

a2e a1 a1

bullbull1--T

28

29

)~ 737t tlOr~ lir ~ ~ t 4~24l

bull~f

1~8 234

~

]f~ 123~

o10 20 30 40 50 60 70 80

40

bullbullu30 L

4JI-

2~I-~p

fi20 -

1-ec~gt01)

10 bullbullCd3Cd

r

0

30

et)c~- (JJ-~deg0o~u

5

~

Heatrejected

VIO

Condenser

V8----

Evaporator

r------- J~~ ~_~ IIIIII V4

VI

V2

~

i=1

I

31

---_-bull_----_ - --

32

--_ bull__-----~----------__-__ __ _- -

jiJ

~iAff~l

CONO

(b) ModcB

CONOl

CONOI

(a) ModeA

33

denoted as mode D

mode A

34--_bull_ bull_-----------------__- _

Sumanthy [2004]

35

36

Figure 112

mathematically

ice making purpose

37

~

f ~

lower heat source

38

CHAPTER 2

ofDhaka

39

-~--_ ---_ _ _

40

I

41

-_ __-__-----__----__ __ ~

V4btgt~c- ()- ~0

VIO 00U-

5

VI

- ~~

bull t~

42

(23)

by

transfer fluid

(24)

43

(27)

(26)

(25)

loops

ToUl

state q

(29)

calculated by

Ps(T) = 13332 e [183-3820 1(1-461)] (21 0)

44

(213)

(212)

endojcyclelime

endofcycletime

cycle

number of collector

ao -15587 bo -65314

aj 015915 bl 072452E-Ol

a2 -050612E-03 b2 -023951 E-03

a3 053290E-06 b3 025493E-06

231 Solar System

45

expressed as

where

(214)

(215)

(2 f6)

46

(217)

47

900800

f1E 700

~ 600c2 500+(U-o 400IIIs - 300_(U

0 200til

100o

bull

[l 06042009 RERC [JI

5 7 9 11 13 17 19

Day Time (Hoursl

April

48

49

(218)

am ~--~+-~-~ In ----------- 2 2 Daylength

50

~

i

51

I

161412

4

2

o

I

T 8 9 -10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

52

06

05

Gl 04]~ 03Ou 02

01

o

7 8 9 10 11 12 13 14 15 16 17 18 19

DayTIme (Hours)

03

025

02uIII0 0150u

01

20 collectors

I _~_L L__

i

8 9 10 11 12 13 14 15Day Time (Hours)

16 17 18 19

53

I

-

54

II

55

19

6 i-n bull ~

1715

13Day Time (Hours)

119

Day TIme (Hours)

8 9 10 11 12 13 14 15 16 17 -18 19

18

16

14

12

~ 10lII

Uu 8ctu

6

4

2

0

7

12

j 1~~ lt~

1 08 QI) U gtu 06

Q

0u04

02

0

7

56

191715

13

DayTime (Hours)

10 11 12 13 14 15 16 17 18 19

9

--r bull ~ --_- ---~~-~-~--~~~~- ~ 1~

~ ~

bullbull

8

7

a

03

04

01

u0 028

035

03

005

0

7

DayTime (Hours)

57

12 13

Daynme (Hours)

f f

~

~ 0 bull 0 Q

bull g -- ~

~

bull bull I bull

12 13

Day Time (Hours)

58

~gt =

1312

po 11-10

9

8

deg7

6

- 22collectors1000s

11191195 12 1205 121 1215 122 1225 123 1235

Day Time (Hours)

59

li

i ~

60

the sunset hours

(i) 800s

(ii) 800s 140 - 185 h 20 scycle

61

110100

P 90-~ 80J10 70~ 60~ 50I-

4030

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day TIme (Hours)

110 100 ~

4030

17 19

140h

62

decreasing gt I11i

1917151311

DayTime (Hours)

97

~ 100d1

f(

U 900-lt1l 80l+ 70(ll lt1lQ 60E 50

4030

5

Il

1917

uniform cycle 800s

9

11 13 15

Day Time (Hours)

()fJ

~~ 13

121110

9~ 8 7

7

63

1

08

41 06ugtua0 04u

02

o

7 8 9 10 11 12 13 14 15 16 i7 18 19

Day Time (Hours)

05

04

u 03VIa

0u 02

01

0

7 9 11 13

__ I

64

~

(J

1ltlt

1lt ~

lt)lt

(OC)(i) Uniform 95 87 71 119 065 0315

800s(ii) Non- 95 87 71 119 057 0314

uniform800s

(iii)Non- 93 85 74 118 056 0311uniform550s

65

12115

11

U 105a-~ 101i 95~ 9E~ 85

8757

1195

12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

r Co

66

67

II

U 100o- 90 bullbullJ 80tu~ 70~ 60

~ 504030

5 7 9 11 13 15 17 19Day TIme (Hours)

fr

Ii ~

110

40

30

5 6 7 8 9 10 11 12 13 14 15 16 17 18 19

Day Time (Hours)

68

Day Time (Hours)

-__-~--~-

(a) CACC

__ ~_L_~_~_

9 10 11 12 13 14 15 16 17 18 19

09

08

07

~ 06gtrr 058 04

03

02

01 -

o

13121110- 9

S 8 7-u 6uot 5u 4

3210

7 8

7 8 9 10 11 1213 14 15 16 17 18 19

Day rfme (Hours)

(b) COP cycle

69

19171513

Day Time (Hours)

(c) COPse

119

04

035

03

025uQ 020v

015

01

005

0

7

151413

U 12~ 11

543

00000deg(1

bull__ J 1 bull ~_J

i195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

70

outlet increases

peak hours

71

~

c

bull~

~r f

~

72

CHAPTER 3

31 Introduction

73

900

100 A 28032005 RERCa

5 7 9 11 13 15 17 19Day Time (Hoursl

III11I

I I

19171513119

900800

E700 ~~ ~ ~

c 600 EJ ~

1~~ ~~ c 300 I d ~ ~

5 7

Day Time (Hours)

74- _- - _~----~~------

800700-NS 600

~- 500c0- 400to-0 300IIIC

- 200nI0V) 100

a ~~ 5 7

II

15 17 19

lIII

600

0

5 7 9 11 13 15 17 19

Day Time (Hours)

75

600

500-NE--= 400A-t

0~ 300 A nl0ent

0 0710 007

5 7 9 11 13 15 17 19Day Time (Hours)

600[J

1500 ~

1

5 9 11 13 15 17 19Day Time (Hours)

76

77

HVm2(Average on 7

years)

March 712 300 188

April 771 340 240

June 568 314 258

August 546 325 266

October 536 312 250

78

-__-------------------------__-_-

l

79

~

125

bed 2

13

i (a) March

bed 2

~bull I

o

-~

85

~[35 LL

115

105 -

G 95o-

1J

(b) April

80

10090-u 800bull

OJl 70J+Ill 60GIQ

EGI 50I-

40

30

bull ~- 11 115 12

Day Time (Hours)

i ~

--J~ -

125 13 I I

I

(c) June

(d) August

115

_____ ~I _ bull i bull -- __

10090 --u 800-~

lo 70s+IVlo 60~Q

E 50~1-

4030

11

81

10- 60QJa-S 50QJl-

40

3011 115 12

Day Time (Hours)

(e) October

I

-J ii

125

J13

(f) December

125 13

82

_-----------------------------------

83

--April--October

Day Time (Hours)

10 11 12 13 14 15 16 17 18 19

bullbull

9

87

16151413121110987654321a

-S0-UUctu

DayTime (Hours)

191817161514

131210 11

(b) COPcycle

9

1

08QI 06Ugt-uQ

0 04u

02

07 8

-J __L- __--L- __ _____ --

Marchampgt=June

=-October

17 18 191614 151310 11 1298

0605

04tv

lVIQ 030u

02

01

0

7

Day Time (Hours)

(c) COPsc

84

85

(b) April

1

Day Time (Hours)

7 l-_---__ ~__ ~ __ ~ __ ~__ ~_~__

1195 12 1205 121 1215 122 1225 123 1235 124

Day Time (Hours)

(a) March

12

1194 1199 1204 1209 1214 1219 1224 1229 1234 1239

12115

a- i1e 105C1I3 10~ 95~X 9E 85~ 8

757

Day Time (Hours)

(c) June

-evaporator outlet

1199 1204 1209 1214 1219 1224 1229 1234 1239

13

125

12115

~ 1095

9

1194

-evaporator outlet

13513

G 125o~ 12bullE 11510

~ 11E 105 -

10

959 1- I

1195 12 1205 121 1215 122 1225 123 1235 124

DayTime (Hours)

(d) August

86

r

P 125-

951205 121 1215 122 1225 123 1235 124 1245 125 1255

Day Time (Hours)

(e) October

EQj 11I-

10

1184 1189

___ L __ J__ ~_~ __ J __ -L

1194 1199 1204 1209 1214 1219 1224 1229

Day Time (Hours)

(1) December

87

_----- --------------------------------~-_---

33 Summary

88

---__----------------------------_ -__ _

tt~r~~~~

~

i ~ t

+ bull

1

CHAPTER 4

41 Introduction

89

___________ _ bull ~ bull 4lt

~ or

Chapter 2

90

j bull

1

Designl

Design 2

time

1 1 - 1400s - -End of the

91

V5VIO

SE2

V8

Evaporator

[ __ dere~~~d~I ~ I

1_ - - - -- - - - L - - - - - - -

I ~~-~~-~~=~~-~ II ( Condenser I)

III V4

III

IIIIIII1IIIf

- - - - - - - -1_-_1__-_-_-__-_-_-_Dcooling

loadO

V2

VI

V3

tt

J

i

design 1

bull

12

1

v1

HollVaer ollilel

if Cooling load

CondQnCQf

S IGlcqe tank

design 1

92

I]I]

~ V4III

IfI]I]

I

IVlO

-Evaporator

_ _W _ _ _ __ __r - - -__C_

Condenser

IIIIIII

lXt=-It2 I

I ----- -r------J - 1 r P- -r

IVbull ~

I

i

f t

if~Iii~~

~ t~ ~

design 2

93

_I

(41)

be expressed asdT -

I

1

(42)

(43)

And

Tcr 1in = Twt bull

in case of design 1

94

(45)

(48)

(47)

TbedoUI = Tcrin

nA Idtunrlsettme cr

and

bull

~

95

- __--------__-----__-----------------

96

i~

85

35

255 7 9 11 13 15 17 19 21 23

23

21

~j

19171513

I Jl I I

1197

---L-~ ____~_~ __ ~ I __J_ __ ~ __-

9085r 801

353025

5

Day Time (Hoursl

97

--__----------------------------

7 9 11 13 15 17 19 21 23 25Day Time (Hours)

353025

5

lJ~~(J~ lOS~~

1 ~ 100~- 95~

~ 90r u 85

40353025

5 7 9 11 13 15 17 19 21

I

23

Day Time (Hours)

98

99

--------- _ -- -__-

80-u 700-lt11~ 60J+-(U

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5

DayTIme (Hours)

100

25

23

21

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21

11 13 15 17 19

Da~Time (Hours)

9

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90858075-u 700-Q) 65-s 60+ro 55-Q)

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5 7 9 11 11) 15 17 19 21 23

- lt

Day Time Hours)

102

offer better values

103

-

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10

9

8

7

3

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1

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~--- bull~ - ct- -+ - - ~ 11 ~

0 ~~ t ~~ ~

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- 30 collectors 1400s_---_---_-- __ ---_----- ~_~ __ ~ __ l___ _______ ___ __

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

Day Time (Hours)

104

_-----------------------____ --------

(b) COPcycle

11

9

080706

~ 05ugtu 04a0u 03

0201a

7

~

005

03

~ 02c

025

bull~ 015aou 01

8 10 12 14 16 18Day Time(Hours)

20 24

(c) COP soiarnet

105

232119171513

11

Day TIme (Hours)

9

co- e bull

CIClK)ta ~

I

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9

3 8 7~ 65 - 5

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7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24

DayTime (Hours)

106

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l ~ ~ bull j 1

J l f l I ~-

-- gt1 I I -1-_ I I I I I I 1 I

95

85

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35

25

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tIt[~I bull

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Day Time Hours)

107

and COP solarnet

(41 Q)

(49)

108

i

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ta 11k

19

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1715131197

10595

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5

Day Time (Hours)

109

I

109

8

7

i 6II- 5uui3 4

3

2

1

0

8 9 10 11 12 13 14 15 16 _ 17 18 19 20 21 22 23 24

Day TIme (Ihours)

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08

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Q

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02

01

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1 bull

(b) COP cycle

23

110

10 12 -14 16 18 20 22 24

(c) COPsolarnet

24222Q181614

111

9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

10908

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02010

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IIIIIIIII

Day Time (Homs)

(b) COP cycle

03025

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8 10 12 14 16 18

- -

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Day Tillie (Hours)

(c) COPsolarnet

112

gti

r-i~

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21

0

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9 10 11 12 13 14 15 16 17 18 19 20 21 22 23

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2422

1-

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1

09

08

07

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113

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02

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Day Time (Hours)

(c) COPsolarnet

-t +

40353025

5 7 9 11 13 15 17 1921 23

Day Time (Hours)

114

13-design =de~ign2

1482 1492 1502 1512 1522 1532 1542 1552 1562i

8

12

Day Time (Hours)

14

12 _ =uniform 1400s ~~

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7

1365 1369 1373 1377 1381 1385 1389 1393 1397 1401 1405 1409

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II115

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r _

5 7 9 11 13 15 17 19 21 23

Day Time (Hours)

I

~

~ ~ 116

---L__ _______ ___

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ff

I I~

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07

06

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02

01

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5 6 7 8 9 10 11 12 13 14 15 16 17 18Day Time (Hours)

117

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H

I

cycle time ~400s

118

119

I~

i

I-~j~

120

L fj

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J

~

CHAPTER 5

Thermal Collectors

~

I___L121

j

in Dhaka

dt l UCPiAcp]

122

(5 1 )

(52)

SolarI

Tlterloal Co8ector

(

household use

123

I _~

~Obil - Q

~ ~T ------[lt----------~

ll I~V4

___-L

l

~

(54)

124

-P~_ __ l J

~~ ~

I ~i~

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~-i

125

125 13

36

33

21

186 8 ~o 12 14

Ibull

9 12

Day Time (Hoursl-

15 18

11bull

126

1 need

i

127

f

q

IjHlIIIiIIij~I

CHAPTER 6

~

bull

of the chiller

875degC

129

IIjf

performance

130

bull

peak hours

I

liters of water

bull

d

performance

131

compression chiller

system

132

~

d

References

133

II

d

J 50-62

134

J

135

J

136

Journal

~

137

_------- _- _ --_ _ __ _---------------------

IIi

-

138

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Full Thesis - Bangladesh University of Engineering and ...

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