Çukurova university institute of natural and applied ... · yapılarak fan-coil ve ısı pompası...

ÇUKUROVA UNIVERSITY

INSTITUTE OF NATURAL AND APPLIED SCIENCES

M. Sc. THESIS

İsmail KILIÇ

EVALUATION OF DIFFERENT DESING METHODS FOR GROUND

SOURCE HEAT PUMPS

DEPARTMENT OF MECHANICAL ENGINEERING

ADANA, 2006

ÇUKUROVA UNİVERSİTESİ

FEN BİLİMLERİ ENSTİTÜTÜ


SOURCE HEAT PUMPS

İsmail KILIÇ

MASTER TEZİ

MAKİNA MÜHENDİSLİĞİ ANBİLİM DALI

Bu Tez 25/12/2006 Tarihinde Aşağıdaki Jüri Üyeleri Tarafından

Oybirliği/Oyçokluğu İle Kabul Edilmiştir.

İmza:

İmza: İmza:

Prof. Dr. Tuncay YILMAZ DANIŞMAN

Prof. Dr. Orhan BÜYÜKALACA ÜYE

Yrd. Doç. Dr. Beytullah TEMEL ÜYE

Bu Tez Enstitümüz Makine Mühendisliği Anabilim Dalında Hazırlanmıştır.

Kod No:

Prof. Dr. Aziz ERTUNÇ

Enstitü Müdürü

Not: Bu tezde kullanılan özgün ve başka kaynaktan yapılan bildirişlerin, çizelge, şekil ve fotoğrafların kaynak gösterilmeden kullanımı, 5846 sayılı Fikir ve Sanat Eserleri Kanunundaki hükümlere tabidir.

I

ABSTRACT

M.Sc. THESIS


SOURCE HEAT PUMPS

İsmail KILIÇ

DEPARTMENT OF MECHANICAL ENGINEERING

INSTITUTE OF NATURAL AND APPLIED SCIENCES

UNIVERSITY OF ÇUKUROVA

Supervisor: Prof. Dr. Tuncay YILMAZ

Year: 2006, Pages: 85

Jury: Prof. Dr. Tuncay YILMAZ

: Prof. Dr. Orhan BÜYÜKALACA

: Yrd. Doç. Dr. Beytullah TEMEL

In this study, a Ground Source Heat Pump System is designed for a 280 m2

doublex villa which is located in Adana. The system can carry out heating and

cooling simultaneously. Firstly, the heat insulation, heat loss and heat gain

calculations are carried out, the heat pump and fan-coil types are chosen and pipe

diameters are determined. The ground heat exchanger’s length is determined with

two different methods for the model building and lastly the cost of the system is

calculated.

Key Words: Ground Source Heat Pump, Heat Loss, Heat Gain, Cost Price, Heat

Changer

II

ÖZ

YÜKSEK LİSANS TEZİ


SOURCE HEAT PUMPS

İsmail KILIÇ

ÇUKUROVA ÜNİVRSİTESİ

FEN BİLİMLERİ ENSTİTÜSÜ

MAKİNA MÜHENDİSLİĞİ ANABİLİM DALI

Danışman: Prof. Dr. Tuncay YILMAZ

Yıl: 2006, Sayfa: 85

Jüri: Prof. Dr. Tuncay YILMAZ

: Prof. Dr. Orhan BÜYÜKALACA

: Yrd. Doç. Dr. Beytullah TEMEL

Bu çalışmada, Adana’da bulunan 280 m2 iki katlı bir villada yer kaynaklı ısı

pompası sistemi tasarlanmıştır. Sistem hem ısıtma hem de soğutma işlemini

gerçekleştirmektedir. Öncelikle, ısı yalıtım, ısı kaybı ve ısı kazancı hesapları

yapılarak fan-coil ve ısı pompası tipleri seçilmiş ve boru çapları belirlenmiştir.

Toprak ısı değiştiricisinin boyu iki farklı method ile belirlenmiştir ve son olarak

sistemin maliyet hesabı yapılmıştır.

Anahtar Kelimeler: Toprak Kaynaklı Isı Pompası, Isı Kazancı, Isı Kaybı,

Maliyet Hesabı, Isı Değiştirici

III

ACKNOWLEDGMENTS

Many people assisted this work that has led to the development of this thesis.

Initially, I would like to thank to my advisor Mr. Professor Dr.-Ing. Tuncay

YILMAZ for his advice and guidance throughout my graduate studies.

I would like to thank Research Assistant Azmi AKTACİR for his great

support.

In addition, I also thank to all my friends for their continuous moral support,

motivation and friendship.

Last but not least, special thanks go to my family for their interest, support

and encouragement.

IV

TABLE OF CONTENTS ABSTRACT I

ÖZ II

ACKNOWLEDGMENTS III

TABLE OF CONTENTS IV

LIST OF FIGURES VII

LIST OF TABLES VIII

SYMBOLS X

1. INTRODUCTION 1

2. PREVIOUS STUDIES 2

3. MATERIAL and METHOD 6

3.1. Definition of the Ground Source Heat Pumps 6

3.1.1. Heat Pumps According to Thermodynamics Cycle 7

3.1.1.1.Vapor Compression Heat Pumps 7

3.1.1.2.Absorption Cycle Heat Pump 8

3.1.1.3.Thermoelectrical Heat Pump 9

3.1.2. Types of Ground Source Heat Pumps 9

3.2. Technical Plans of the Building 10

3.3. Heat Insulation Calculation of Building 13

3.3.1. Building Properties 13

3.3.2. Specific Heat Loss Calculation and Yearly

Needed Heat Energy Calculation 13

3.4. Heat Loss and Gain Calculations 13

3.4.1. Heat Loss Calculation 13

3.4.2. Heat Gain Calculation 14

3.5. Determination of Pipe Diameters 14

3.6. Choosing of Heat Pump’s Components 15

3.6.1. Fan Coil 15

3.6.2. Heat Pump 18

3.6.3. Circulation Pump 19

V

3.7. Ground Heat Exchanger’s Pressure Loss Calculation 20

3.7.1. Frictional Losses 20

3.7.2. Local Losses 20

3.8 Ground Heat Exchanger’s Length Calculation 21

3.8.1 Long Method 22

3.8.1.1 Heat Transfer in Heating Season ( evapQ& ) 22

3.8.1.2 Heat Transfer in Cooling Season ( conQ& ) 22

3.8.1.3 Heating Performance ( hCOP ) 23

3.8.1.4 Cooling Performance ( cCOP ) 23

3.8.1.5 Pipe Resistance ( pR ) 23

3.8.1.6 Ground Resistance ( gR ) 23

3.8.1.7 Maximum Ground Temperature ( HT )

and Minimum Ground Temperature ( LT ) 25

3.8.1.8 Maximum Temperature of Heat

Pump ( maxT ) 26

3.8.1.9 Minimum Temperature of Heat

Pump ( minT ) 26

3.8.1.10 Heating Working Factor ( hF ) 26

3.8.1.11 Cooling Working Factor ( cF ) 27

3.8.2 Short Method 28

3.8.2.1 Heat Transfer in Heating Season ( evapQ& ) 28

3.8.2.2 Heat Transfer in Cooling Season ( conQ& ) 28

3.8.2.3 Heat Transfer Coefficient (U) 29

3.8.2.4 Temperature Different for Heating (∆Th) 29

3.8.2.5 Temperature Different for Cooling (∆Tc) 29

3.9. Cost Price Calculations 46

3.9.1. Cost of Ground Source Heat Pump System 46

VI

3.9.1.1. Heat Pump 46

3.9.1.2. Ground Heat Exchanger 46

3.9.1.3. Expansion Tank 46

3.9.1.4. Fan Coil 47

3.9.1.5. Pipe System for Inside of Building 47

4. RESULTS and DISCUSSION 53

5. CONCLUSION 56

REFERENCES 57

CURRICULUM VITATE 60

Appendix -1.A Specific Heat Loss Calculation Form 61

Appendix -1.B Yearly Needed Heat Energy Calculation Form 62

Appendix -2.A Heat Loss Calculation Table 63

Appendix -3.A Heat Gains of the Rooms 69

Appendix -3.B Total Heat Gains of the Building 71

Appendix -3.C Pressure Loss Table in Pipes for 20 0C Temperature

Difference 72

Appendix -4.A Features of the Chosen Heat Pump 74

Appendix -4.B Capacity Diagram of the Heat Pump 75

Appendix -4.C Performance Diagram of the Heat Pump 76

Appendix -5.A Pipe Diameter Calculation Table 77

Appendix -5.B Local Loss Coefficient Calculation Form 83

Appendix -6.A The Sizes and Resistances for 1 Meter Length of the

Polyethylene and Polybuthilen Pipes 84

Appendix-6.B Model Building Picture 84

Appendix-6.C Fan Coil and Heat Exchanger Pictures of the Model

Building 85

VII

LIST OF FIGURES

Figure 1 Heating and Cooling Modes of a Heat Pump 7

Figure 2 Absorption Cycle Heat Pump 8

Figure 3 First Floor of the Villa 11

Figure 4 Second Floor of the Villa 12

Figure 5 Heating Cycle 18

Figure 6 Cooling Cycle 19

Figure 7 General Selection Charts for Flanged

Single Speed Circulation Pumps 19

Figure 8 General Selection Charts for Circulation Pumps 21

Figure 9 The Ground Temperatures of Adana in the

Different Depths. 26

VIII

LIST OF TABLES

Table 1 Different Types of Heat Pumps 10

Table 2 Technical Specifications of Fan Coil – 42 FA Type 16

Table 3 Models and Amounts of the Chosen Fan Coil 17

Table 4 Ground Resistance 24

Table 5 Thermal Diffusivity and Thermal Conductivity of

Different Grounds 25

Table 6 The Calculation Results Which is Calculated with Long Method

for the Different Max. (27 0C) and Min. (10 0C) Ground Temp. 31

Table 7 The Calculation Results Which is Calculated with Short Method




















IX







Table 20 Fan Coil Type’s Price 47

Table 21 The Materials and Their Prices for the Long Method’s Results 47

Table 22 The Materials and Their Prices for the Short Method’s Results 48

Table 23 Cost of Ground Source Heat Pump System 50

Table 24 Cost of Ground Source Heat Pump System Which is Calculated






Table 27 Ground Heat Exchanger’s Calculation Results 54

X

SYMBOLS

A : Surface area of the building elements

AAS : Surface area which is contacted with outside air

AC : Ceiling area

Ai : Total window area in ith direction

ALowTemp : Building elements area which are contacted with low temperature

inside place

AOW : Outside wall area

AS : Surface area

AW : Window area

AF : Amortization factor

aT : Thermal diffusivity

a : Leakage coefficient

CA : Yearly first investment cost

COM : Yearly cost

(COM)PW : Yearly cost of the system for today

Cp : Specific heat

COPc : Cooling Performance

COPh : Heating Performance

CT : Total cost

d : Building elements thickness

ef : Escalating factor

Fc : Cooling working factor

Fh : Heating working factor

f : Friction factor

GLRmonth : Monthly gain usage ratio

g month,i : Sun energy transfer factor of the transparent elements in ith direction

g ⊥ : Sun energy transfer factor of the beam which comes perpendicular

to the surface

Hi : Heat loss value for the infiltration and convection

Hv : Heat loss value from the ventilation

Hs : Specific heat lost value

H : Building status coefficient

IA : Total first investment cost

XI

I month,i : Monthly sun radiation factor which comes perpendicular to the

Surfaces in ith direction

(IOM)PW : Yearly total cost of the system for today

i : Yearly nominal interest

k : Thermal conductivity

l : Open sides of the length of windows and doors

n : System life

Lc : Pipe length, cooling

Lh : Pipe length, heating

Q : Yearly heating energy need

Qh : Total heat need

Qmonth : Monthly heating energy need

Qs : Heat need calculation for air leakage

Q’ : Heat energy value

pumpheat,cQ : Cooling capacity of the heat pump

cQ& : Heat Gain of the Model Building

ceQ& : Electric power for cooling

heQ& : Electric power for heating

hQ : Heat Loss of the Model Building

pumpheat,hQ : Heating capacity of the heat pump

R : Room status coefficient

Red : Reynolds number

Rg : Ground thermal resistance

Rp : Pipe thermal resistance

r month,i : Monthly shadow factor of the transparent surfaces in ith direction

TH : Maximum Ground Temperature

THV : Outlet temperature of the heating water

Ti : Inside temperature

TL : Minimum Ground Temperature

Tm : Average Yearly Total Temperature

Tmax : Maximum Temperature of Heat Pump

Tmin : Minimum Temperature of Heat Pump

To : Outside temperature

U : Overall heat transfer coefficient

XII

u : Speed

Vv : Ventilated volume

Vgross : Brut volume of the building

Z : Local resistance

ZD : United increasing coefficient

ZH : Direction increasing coefficient

ZT : Total increasing value

ZW : Floor height increasing coefficient

ε : Roughness value

M& : Mass flow rate

µ : Dynamic viscosity

λh : Thermal conductivity value

φ month,i : Monthly efficiency value

φ month,s : Monthly sun energy gain value

ηmonth : Monthly gain usage factor

∆T : Temperature difference

∆Ps : Total frictional losses

∆P : Total pressure losses

Σζζζζ : Total local pressure loss coefficients

V& : Pump’s Volume Rate Flow

ρ : Density

1. INTRODUCTION İsmail KILIÇ

1

1. INTRODUCTION

The problems about energy assurance and the increasing dimensions of

environmental pollution caused by energy consumption oblige to existing sources to

be evaluated well and spent as economic as possible as seen in the past and

nowadays. Therefore, after two petroleum crises following each other in 1970s,

industrialized countries gave importance to creating technologies causing less

environmental pollution. Because of this, ground source heat pumps are used widely.

The advantages of ground source heat pumps presented by Switzerland patent

for the first time in 1912. Then its thermodynamic advantages were shown in detail

in 1940s by entangling brine in metal serpentines buried as a heat source. The

problems of serpentine corrosion made ground serpentines useless and made the

development of air heat pumps necessary. Then, by using plastic pipes corrosion

problems were solved and studies on ground source heat pumps were accelerated

(Couvillion, 1985).

In USA, the interest in ground source heat pumps started in 1940s and 50s.

However, technology in those days was limited with improper pipe equipments and

decreased because of expensive natural gas. Technology refreshed again in Sweden

during the petroleum crisis and a few years later, a research programme was started

in Oklahoma State University (Hughes, Loomis, O’neil and Rizzuto, 1985). In 1988,

it was started that there were 134000 ground source heat pumps in Sweden with

respect to these developments (Sulatisky and Van Der Kamp, 1991).

2. PREVIOUS STUDIES İsmail KILIÇ

2

2. PREVIOUS STUDIES

The fundamental principle of the heat pump is suggested by the Nicolas

Carnot. In 1850 William Thomson suggested that the cooling machines can be used

for heating. He used the air as a fluid in his heat pump. In this machine, the air is

sucked up by the expansion. Thus it’s temperature and pressure decreases. And the

air passes from the heat exchanger. At this time the heat from the outside is

transferred to the air. Lastly the air passes from the compressor and heats the

building. This machine which is done in Sweden is used for heating and cooling of

the buildings (Thomson, 1852). Because of this the Carnot’s theory can not be

realized.

In 1870s the development of cooling equipments rapidly increased by putting

Thomson’s works into practice and a lot of cooling air equipments were produced in

order to meet the needs of frozen meat commerce. In 1879, cooling machines were

installed in the ships which were carrying meat from USA and Australia to United

Kingdom. Important developments took place in steam pressing machines which use

ether, ammonia and methyl chlorides as a cooling liquid (Coelman, 1879).

The development of heat pump paused after the developments in freezing

equipment. While the cooling machines were meeting the needs, the development of

heat pumps had to be based on the existence of the cost and availability of energy.

Indeed, the development of a heat pump was based on the development of cooling

equipments. When we look at the past of cooling establishments, it is obvious that in

1920s and 30s; the need to a heat pump has been rapidly increased compared to late

19th century.

The first practical heat pump (Haldane, 1930) was installed up experimentally

in Scotland to provide surroundings and water heating. By using environmental air

and network water as a heat source at a low temperature he increased the liquid’s

heat with a compressor. He gave this heat to water in condenser for heating the

water. He heated his house by circulating this water in radiators. Ammonia is used as

a refrigerant. The electricity needed for a compressor was provided from a

hydroelectric power central placed nearby a river close to his house. Haldane


3

installed up a machine as perfect as it is today. But he realized that the activity of the

device he set up in his house is not as good as for the bigger cooling circuits.

The first major heat pump installation in Europe was commissioned during

the period 1938 – 1939 in Zurich. This unit, which used river water as the heat

source, utilized a rotary compressor with R12 as the working fluid. Used to heat the

Town Hall, the output of the Zurich heat pump was 175 kW, delivering water at a

temperature of 60 0C for space heating. A thermal storage system was incorporated

in the circuit, in the form of a central heating system which could be boosted by

electric heating at periods of peak demand.

The economical problems in 1930s provided the necessary support needed for

the development of heat pumps in Europe and when the Electrical Service magazine

published a special report called “Energy Economy and Thermodynamic Heat

Pumps”, many heat pumps with a steam turbine which uses the potential steam

power in condenser process was offered. It’s stated as an air or water heat source for

building heating and recycling of the temperature of industrial waste. A bibliography

was published for the application of heat pumps in schools, offices, bureaus and

dairy farms (Anon, 1944).

In 1940, 15 commercial applications most of which use well water as a heat

source were presented in USA (Kemler and Oglesby, 1950).

In 1950, studies on house heat pumps which use ground as a heat source in

United Kingdom and USA were out. Baker, was projected an inverse unit which

worked with antifreeze store bath and he showed that COP was more then 3 (Baker,

1953).

A system, which is an experimental unit and designed for the building which

was built for the show in London in 1951 for cooling in summers and heating in

winters had 2.7 MW heating capacity. In the system which used Thames River as a

heat source, the outlet temperature of condenser water was 71 0C. Cooled water at 4 0C was produced in the process of cooling. The energy needed for a high speed

centrifugal compressor was obtained from a Roil-Royce Merlin engine. While the

COP of the system where R-12 was used as a refrigerant was 5.1 (Montagnon, 1954).


4

The first heat pump installed in the United Kingdom which successfully

demonstrated that a large building could be heated using this technique was located

in Norwich. The unit was installed in the offices of the Norwich Corporation

Electricity Department. The heat source used was a river and the heat sink was

circulating hot water, delivered at a temperature of 49 0C. Sulphur dioxide (SO2) was

used as the refrigerant and COP of the order of 3 were achieved (Sumner, 1955).

Many heat pumps were produced commercially to be used in buildings. One

of the most well-known one is Ferranti cooler and heater whose name is coming

from his inventor. This unit was used to heat water at a more high temperature by

absorbing the heat from food-storing room. The unit which spends 136 liters water

for storing heat had a heat exit at 1.2 kW in summer and 0.7 kW in winter. In spite of

being simple and its low cost, this unit couldn’t find an existing market. Nonetheless,

by developing small commercial machines at similar types, they were successfully

used for providing hot water from ice cream machines (Ferranti, 1955).

In the earliest 60’s, the air-air heat pumps used in houses were purchased at a

high rate in USA. Having been added a valve which made fluiding of refrigerant

reversible, the heat pumps became more important than air conditioners.

Unfortunately, the reliability of these systems was decreased as people couldn’t

understand it well. In 1964, as the reliability of them couldn’t be dissolved enough,

the military authorities in USA banned the use of heat pumps in military lodgings.

This prohibition lasted until 1975 (Halmos, 1975).

One of the heat pumps applied to house heating was installed successfully by

summer in United Kingdom. In this system, the heat pump was installed in a one-

floor house which was well isolated in order to heat everywhere in the house. Air

was used for firstly. Several years’ studies and then 1 meter deep ground was used.

The process of distributing heat in the house was made by the copper pipes. COP of

the unit which still being used was calculated to be 2, 8 (Sumner, 1955).

The studies of the use of heat pumps to meet hot water need in houses were

started in USA in 1950. The use of heat pumps for getting humidity and hot water

was offered in 1962; however, this idea was commonly refused or recently

researches showed that the use of heat pumps for producing hot water is more


5

economical than electric heating when compared. But this idea is valid for the places

where electricity can not be found. The interest in heat pump applications has been

accelerating as the cost of fuel has been increasing (Heap, 1979).

A Computer design model was developed for capillary piped air-air heat

pumps (Fisher and Rice, 1981). The studies were on the modeling of temporary COP

of heat pumps (Chi and Didion, 1983). A mathematical model was developed for

capillary piped air-air heat pumps (Domanski and Didion, 1984).

Aydın (1986) examined the physical and thermodynamic properties of

Refrigerant and the main elements of heat pumps such as evaporator, condenser,

compressor and capillary pipe in detail. He prepared a Fortran Computer programme

which calculates the dimensions and COP of heat pump elements in different

evaporator and condensers. He made the theoretical models of air-air, air-water,

water-air and water-water pumps in his study (Aydın, 1986).

The experiments were carried out to produce only air conditioner and cooling

hot water by changing a 3,5 kW office air conditioner to heat water and to cool

surroundings. It is shown that a changed unit can be used for heating water without

any changes in its capacity. More over, it is shown that some amount of hot water

can be stored in a small tank to provide hot water for a shower. It’s more productive

than direct electricity heating system (Ying, 1989).

Şendağ (1992) constructed and applied a heat pump which provides hot and

cold water in winters and summers. As a result of his experiments, he calculated the

heating and cooling COP’s and proved that the system can be applied well (Şendağ,

1992).

Pihtili and Bozkir (1996) stated that the need of hot water of buildings can be

provided with a heat pump system and made comparison of this system with an

electrical hot water heater. The experiments were carried out to heat 40 liters water

from 15 ºC to 50 ºC. They obtained the same heating capacity by using 55% of the

energy. The heating COP varied between 1.4 and 1.82 (Pihtili and Bozkir, 1996).

3. MATERIAL AND METHOD İsmail KILIÇ

6

3. MATERIAL AND METHOD

3.1. Definition of the Ground Source Heat Pumps

Heat pumps are generally more expensive to purchase and install than the

other heating systems. They are economical in the long run in some areas because

they lower the heating bill. Despite their relatively higher initial cost, the popularity

of heat pumps is increasing. About one third of all single family homebuilt in the

United States in 1984 are heated by heat pumps.

The most common energy source for heat pump is atmospheric air (air – to –

air systems), although water and soil are also used. The major problem with air –

source system is frosting which occurs in humid climates when the temperature falls

below 5 to 2 0C. The frost accumulation on the evaporator coils is highly undesirable

since it seriously disrupts the heat transfer. The coils can be defrosted however, by

reversing the heat pump cycle (running it as an air conditioner). This results in a

reduction in the efficiency of the system. Water source systems usually use well

water from depths of up to 80m in the temperature range of 5 to 18 0C, and they do

not have a frosting problem. They typically have higher COP’s but are more complex

and require easy access to a large body of water such as underground water. Soil –

source systems are also rather involved since they require long tubing placed deep in

the ground where the soil temperature is relatively constant. The COP of heat pumps

usually ranges between 1.5 and 4, depending on the particular system used and the

temperature of the source.

Both the capacity and the efficiency of a heat pump fall significantly at low

temperatures. Therefore, most air source heat pumps require a supplementary heating

system such as electric resistance heaters and oil or gas furnace. Since water and soil

temperatures do not fluctuate much, supplementary heating may not be required for

water source or soil systems. But the heat pump system must be large enough to meet

the maximum heating load.

Heat pumps and air conditioners have the same mechanical components.

Therefore it is not economical to have two separate systems to meet the heating and


7

cooling requirements of a building or a house. One system can be used as a heat

pump in winter and an air conditioner in summer. This is accomplished by adding a

reversing valve to the cycle as shown in Figure-1.

Power IN

Cooling Mode

Heating Mode

ReversingValve

Compressor

Condenser Evaporator

Capillary Tube

Condenser

Evaporator

Figure – 1. Heating and Cooling Modes of a Heat Pump

3.1.1.Heat Pumps According to Thermodynamics Cycle

3.1.1.1. Vapour Compression Heat Pumps

The simple vapour compression heat pumps are the most widely used

systems. The ordinary vapour compression heat pumps systems are simple,

inexpensive, reliable and practically maintenance – free. However for large industrial

applications efficiency not simplicity is the major concern.

The main parts of these systems are compressor, evaporator, condenser and

expansion device. There is a refrigerant (working fluid) in the system. It change

phase at certain temperatures and pressures. It absorbs heat by evaporation and it

delivers heat by condensation.


8

3.1.1.2. Absorption Cycle Heat Pump

Another form of refrigeration which becomes economically attractive when

there is a source of inexpensive heat energy at a temperature of 100 to 200 0C is

absorption refrigeration. As the name implies, absorption refrigeration systems

involve the absorption of a refrigerant by a transport medium. The most widely used

absorption refrigeration system is the ammonia – water system, where ammonia

(NH3) serves as the refrigerant and water (H2O) as the transport medium. Other

absorption refrigeration systems include water lithium bromide and water – lithium

chloride systems, where water serves as the refrigerant.

The basic components of an absorption cycle heat pump are the condenser,

the evaporator and the expansion device which of similar to the all vapor

compression system. The compressor in vapor compression system is replaced by an

absorber, a generator and a small pump in absorption refrigeration system. This part

is named as thermal compressor. This system is shown in Figure-2.

Heat removed

Heat supplied

ExpansionDevice

Thermal Compressor

Generator

Absorber

Condenser

Evaporator

Solution Pump

Heat removed

Heat supplied

Figure – 2.Absorption Cycle Heat Pump


9

3.1.1.3. Thermo Electrical Heat Pump

Consider two wires made from different metals joined at both ends forming a

closed circuit. Ordinarily, nothing will happen. But when one of the ends is heated

something interesting happens: A current flows continuously in the circuit. The

circuit which incorporates both thermal and electrical effects is called a

thermoelectric circuit and a device that operates on this circuit is called a

thermoelectric device.

Thermo electrical devices will not be competitive with vapor compressions

heat pumps in the foreseeable future, but they may find increasing use in specialized

cooling applications where power requirements are low or where silent operation is

necessary. Close temperature control of electronic components and cold stores in

nuclear submarines are examples of the thermo electrical system.

3.1.2. Types of Ground Source Heat Pumps

Heat pumps may be classified according to their heat source. Ambient source

heat pumps abstract heat from a source external to the process or building to which

heat is supplied. Heat recovery devices use heat produce as a by product of some

other process as such as cooling. The more commonly advocated source of heat for

both classes of heat pump are considered in Table 1.


10

Table 1.Different Types of Heat Pumps

NUMBER TERMS

1 Earth Energy Heat Pumping Systems

2 Surface Water Heat Pump Systems

3 Earth Energy Systems

4 Ground Source Systems

5 Ground Water Heat Pumps

6 Earth – Coupled Heat Pumps

7 Well – Source Heat Pumps

8 Ground – Source Heat Pumps

9 Geothermal Heat Pumps

10 Ground – Coupled Heat Pumps

11 Ground – Water Source Heat Pumps

12 Well – Water Heat Pumps

13 Solar Energy Heat Pumps

14 GoExchange Systems

15 GeoSource Heat Pumps

3.2. Technical Plans of the Building

In this study a Ground Source Heat Pump System was designed for a doublex

villa in Adana whose floor area is 280 m2. The technical plans of the first and second

floors of doublex villa are given in Figure-3 and 4.


11

Figure 3.First Floor of the Villa

NORTH

EAST

SOUTH

WEST


12

Figure-4.Second Floor of the Villa

EAST

NORTH

SOUTH

WEST


13

3.3.Heat Insulation Calculation of Building

According to TS 825 buildings must be insulated to build economical

buildings. Here necessary insulations of the building must be selected and calculation

must be carried out, whether the building as sufficiently insulated or not.

3.3.1. Building Properties

The values which are used to fill the heat insulation calculation form are given

below.

Ceiling Area = 140 m2

Surface Area = 140 m2

Wall Area = 259 m2

Glass Area = 38, 8 m2

Total Area = 586, 6 m2

Vgross = 924 m3

Vv = 0.8 x Vgross = 739, 2 m3

An = 0.32 x Vgross = 295, 68 m3

3.3.2. Specific Heat Loss Calculation and Yearly Needed Heat Energy

Calculation

These calculation forms are given in Appendix-1.A and Appendix-1.B.

3.4. Heat Loss and Gain Calculations

3.4.1.Heat Loss ( hQ& ) Calculation

The heat loss of the model building is found as 11597 W. The results of the

calculation are given in Appendix–2.A.


14

3.4.2.Heat Gain ( cQ& ) Calculation

The heat gain of the model building is found as 18056 W. The results of the

calculation are given in Appendix–3.A and 3.B.

3.5. Determination of Pipe Diameters

The pipe diameters are determinated and the results are given in Appendix–

5.A.

In critical circuit total frictional losses (ΣLR) and total local losses (ΣΖ) are

added and the total pressure loss is found with Eq. (3.1).

ΣLR= 603 mmWC ΣZ = 375 mmWC

∆P = ΣLR + ΣZ = 978 mmWC (3.1)

The total resistance also gives pump’s pressure value. However, in order to

work in safety, this value must be increased by 20%.

∆P = (ΣLR + ΣZ) 1, 2 = 1174 mmWC

Pump’s flow rate is calculated with Eq. (3.4).

∆TxCpxM.Q &=

(3.2)

VxM && ρ= (3.3)

TxCpx

QV

∆ρ=

&& (3.4)


15

h/m67,4~s/m00129,0V

5x4180x1000

27200V

33 ==

=

&

&

3.6.Choosing of Heat Pump’s Components

3.6.1. Fan Coil

According to the calculations, it has been found that total heat lost is 11, 597

kW and total heat gain is 18, 056 kW. As the heat gain is higher than the total heat

lost, fan coil selection must be made according to the cooling capacity.

The technical specifications and types of Fan Coil – 42 FA model for different

capacity are given in Table-2.

3. MA

TE

RIA

L A

ND

ME

TH

OD

İsmail K

ILIÇ

16

Table 2. Technical Specifications of Fan Coil – 42 FA Type

10 7

5, 51

1210

31

9, 4

328

165

43/51/63

563/1355/230

35

0, 72

165

08 4, 68

3, 95

784

30

6, 18

286

144

42/53/63

563/1355/230

33

0, 63

144

06 3, 85

3, 06

655

18

5, 08

197

122

44/53/63

563/915/230

21

0, 53

122

04 2, 85

2, 3

480

25

3, 8

135

72

39/49/54

563/915/230

20

0, 32

72

03 1, 84

1, 59

311

18

2, 42

102

62

39/48/53

563/695/230 18

0, 27

62

02 1, 49

1, 26

254

26, 1

1, 97

87

45

41/46/51

563/695/230

17

0, 20

45

01 1, 06

0, 93

188

10, 5

1, 29

Centrifugal

67

45

33/43/48

418/695/182

13, 5

0, 28

65

220/230-1-50

kW

kW

L/h

kPa

kW

L/s

W

dB(A)

mm

kg

A

W

V-Ph-Hz

Total

Sensible

Tip 42 FA Cooling

Capacity

Water Flow Rate

Pressure Drop

Heating Capacity

Fan Type

Air Flow Rate

Motor Power

Voice Power

Sizes H/W/D

Weight

Electricity Information

Current Drawn

Power Input

Power Supply


17

Fan coil models and amounts that were chosen for every room from Table – 2

and calculated according the highest sensible and total heat gain are given in Table-3.

Table 3. Models and Amounts of the Chosen Fan Coil

TOTAL COOLING LOAD ROOMS

Sensible Latent Total

FAN COIL TYPE

AMOUNT

Entrance (101) 516 174 690 42 FA 01 1 Unit

Bath (102) 376 83 459 42 FA 01 1 Unit

42 FA 03 2 Unit Sitting Room (103) 2925 265 3190

42 FA 02 1 Unit

Kitchen (104) 5024 174 5198 42 FA 03 3 Unit

Bath (201) 466 83 549 42 FA 01 1 Unit

Entrance (202) 625 174 799 42 FA 01 1 Unit

Bedroom (203) 324 83 407 42 FA 01 1 Unit

Bedroom (204) 1580 174 1754 42 FA 03 1 Unit

Bedroom (205) 1485 174 1659 42 FA 03 1 Unit

Bedroom (206) 2766 174 2940 42 FA 02 2 Unit

42 FA 03 1 Unit Bedroom (206) 2830 174 3004

42 FA 02 1 Unit


18

3.6.2. Heat Pump

Like fan-coil choice, heat pump choice should be made according to the

cooling capacity. VITOCAL 300 BW 220 type of VIESSMANN is chosen as heat

pump. The features of chosen heat pump are given in Appendix-4.A, 4.B and 4.C.

The features which are given in Appendix-4.A are for the 0 0C antifreeze inlet

temperature. But our antifreeze inlet temperature is 5 0C in cooling cycle and 10 0C

in heating cycle. Because of this we must use capacity diagram which is given in

Appendix-4.B and 4.C to find heating and cooling capacities, electric power and

COP for the heating and cooling seasons. These values are found as;

pumpheat,cQ = 21, 4 kW Qec = 4, 1 kW COPc = 5, 8 kW

pumpheat,hQ = 27, 2 kW Qeh = 6, 3 kW COPh = 4, 2 kW

Figure-5.Heating Cycle

5 0C 10 0C

45 0C 40 0C

Compressor

Expansion Device

Condenser

Evaporator


19

Figure-6.Cooling Cycle

3.6.3. Circulation Pump

Circulation pump is chosen from Figure-7 according to critical circuit

pressure loss and pump flow rate which is calculated in 3.5. SRP-Al 8 type

circulation pump of the ALARCO firm is chosen.

H (

m)

Q (m3/h)

Figure-7. General Selection Charts for Flanged Single Speed Circulation Pumps

30 0C 35

0C

10 0C 5 0C

Condenser

Evaporator

Compressor Expansion Device


20

3.7.Ground Heat Exchanger’s Pressure Loss Calculation

To find circulation pump type for the heat exchanger system we must

calculate the pressure loss of the underground pipe system. This calculation is given

below.

conQ& = Qc + Qec

conQ& = 18056 + 4100 = 22156 W

3.7.1.Frictional Losses

To find the frictional losses firstly we must find the R value from the Pressure

Loss Table in Pipes for 20 0C Temperature Difference which is given in Appendix-

3.C. This value is found as 22, 47 mmWC/m. The ground heat exchanger length is

found as 1164 meters. We used a collector and the heat exchangers are connected

parallel. Because of this we calculated 388 meters heat exchanger’s frictional losses.

But 33 meters of this heat exchanger is double bend (tight). The double bend (tight)

is shown in Appendix-5.B.

ΣLR= 388 x 22, 47 = 7977 mmWC = 7, 9 mSS

u = 0, 9 m/s

3.7.2.Local Losses

In the pipe system 23 units double bend (tight) is used. The ξ value of the

double bend (tight) is 2. The total ξ values are (23 x 2) = 46. The total special loss is

found as 13000 Pa = 1, 3 mWC from Z special resistance pressure loss diagram

(Genceli and Parmaksızoğlu, 2006).

The total pressure loss is found as 9, 2 mWC. However, in order to work in

safety, this value must be increased by 20%.

∆P = 9, 2 x 1, 2 = 11, 04 mWC


21

Technical specification of the water at 32, 5 0C temperature;

3m/kg995=ρ K.kg/kJ178,4CP ====

The flow rate value is found as 3, 97 m3/h.

TxCpx

QV c

∆ρ=

&&

h/m97,3~s/m0011,05x178,4x995

956,22V 33 ===&

Circulation pump is chosen from Figure-8 according to heat exchanger

pressure loss and pump flow rate which is calculated. HCPC-Al 5/10 type circulation

pump of the ALARCO is chosen.

2 4 6 8 10 12 14 16 18 20 22 24 26 28 30 32 34 36 38 40 42 44 46 48 50 52 54 56 58 60 62 64 66

Q(m3/h)

Figure-8. General Selection Charts for Circulation Pumps

3.8.Ground Heat Exchanger’s Length Calculation

Ground heat exchanger’s length is calculated with two different methods. These

methods are given below.


22

3.8.1 Long Method

This method is called long method. In this method ground heat changer’s

length is calculated both for cooling and heating needs with Eq. (3.5) and (3.6)

(KINCAY and TEMİR, 2002).

( )

minTLT

hFxgRPRhCOP

1hCOP

evap

.QhL

−

+

−

=

(3.5)

( )

hTmaxT

cFxgRPRcCOP

1cCOP

con

.QcL

−

+

+

=

(3.6)

3.8.1.1. Heat Transfer in Heating Season (evap

Q& )

This value is calculated with Eq. (3.7).

heQhQevapQ &&& −−−−==== (3.7)

evapQ& = 11597 – 6300 = 5297 W

3.8.1.2. Heat Transfer in Cooling Season ( conQ& )



23

ceQ

cQ

conQ &&& += (3.8)

conQ& = 18056 + 4100 = 22156 W

3.8.1.3. Heating Performance (h

COP )

This value is chosen as 4, 2 from Appendix-4.C.

3.8.1.4. Cooling Performance (c

COP )

This value is chosen as 5, 8 from Appendix-4.C.

3.8.1.5. Pipe Resistance (p

R )

Plastic pipes are made from polyethylene and polybutene. The plastic pipes

which are made from these materials are suitable to underground usage. The thermal

conductivities of the wall materials of these pipes are given below.

Polyethylene: k = 0, 39

Polybutene: k = 0, 22

The sizes and resistances for 1 meter length of the polyethylene and

polybutene pipes are given in Appendix – 6.A. In our model building we use 11/2”

Polyethylene SCH-40. The resistance of this pipe is 0, 068 m0C /W.

3.8.1.6. Ground Resistance (g

R )

The ground resistance for the different ground types and pipe diameters are

given in Table-4. This value is chosen as 0, 688 m0C /W for our system.

3. MA

TE

RIA

L A

ND

ME

TH

OD

S İsm

ail KIL

IÇ

24

Table 4. Ground Resistance (m0C / W)

Rg (Rock)

Rg (Low Moist)

R

0, 347

0, 613

0, 329

0, 584

0, 312

0, 555

0, 306

0, 543

0, 289

0, 514

3

4 2

1

R10

1, 22

1, 462

1, 064

1, 428

1, 035

1, 387

1, 017

1, 364

0, 988

1, 324

3

4 2

1

R9

1, 22

1, 647

1, 197

1, 607

1, 168

1, 659

1, 15

1, 543

1, 121

1, 509

6

7

5

4

R8

1, 243

1, 653

1, 214

1, 613

1, 185

1, 572

1, 168

1, 549

1, 145

1, 514

3

4

5

6

R7

1, 185

1, 59

1, 156

1, 665

1, 133

1, 509

1, 11

1, 486

1, 087

1, 451

6

4

R6

0, 792

1, 064

0, 763

1, 023

0, 734

0, 983

0, 723

0, 96

0, 694

0, 925

3

5

R5

0, 757

1, 023

0, 728

0, 983

0, 705

0, 942

0, 688

0, 919

0, 659

0, 884

6

R4

0, 642

0, 861

0, 613

0, 821

0, 584

0, 786

0, 566

0, 763

0, 543

0, 728

5

R3

0, 63

0,85

0, 601

0, 809

0, 572

0, 775

0, 561

0, 751

0, 532

0, 717

4

R2

0, 613

0, 832 0, 59 0, 792

0, 561 0, 757

0, 543 0, 734 0, 514 0, 694

Rg (Heavy Ground-Moist)

Rg (Heavy Ground-Dry Ground-Moist)

3

R1

0, 59 0, 798 0, 561 0, 763 0, 532 0, 723 0, 514 0, 699 0, 491 0, 665

3/4

1

1 1/4

1 1/2

2

PIP

E D

IAM

ET

ER

3. MATERIAL AND METHODS İsmail KILIÇ

25

3.8.1.7. Maximum Ground Temperature (H

T ) and Minimum Ground

Temperature (L

T )

To find maximum and minimum ground temperatures, firstly we must choose

the thermal diffusivity (aT) for the ground type. This value is 0, 048 m2 / day. And

then maximum and minimum temperatures are determined from the graph which is

given Figure-9. Then the average temperature of the ground is calculated with

Eq.(3.9).

2LTHT

0T+

= (3.9)

C202

13270T 0=

+=

Table 5 Thermal Diffusivity and Thermal Conductivity of Different Grounds

Type of Ground aT (m2 / day) k (W / m0C)

Pebble Ground 0. 012 0. 52

Sandy Ground - 1. 07

Heavy and Moist Ground 0. 056 1. 30

Dry and Heavy Ground 0. 045 0. 95

Dry Ground 0. 024 -

Low Moist Ground 0. 048 0. 87

Stone, Granite 0. 098 2. 93

Stone, Marble 0. 115 2. 80

Water 0. 012 0. 06

Air 1. 855 0. 026


26

Adana (a=0,045 m2/day)

0

5

10

15

20

25

30

0 30 60 90 120 150 180 210 240 270 300 330 360

t (day)

T

Y=0 Y=0,9 Y=1,2 Y=1,5 Y=1,8

Figure –9 .The Ground Temperatures of Adana in the Different Depths

3.8.1.8. Maximum Temperature of Heat Pump (max

T )

This value is given as 35 0C in figure-7.

3.8.1.9. Minimum Temperature of Heat Pump (min

T )

This value is given as 5 0C in figure-8.

3.8.1.10. Heating Working Factor (h

F )


pumpheat,h

h

Qx2

QhF

&

= (3.10)


27

213,02,27x2

597,11hF ==

3.8.1.11. Cooling Working Factor ( cF )


pumpheat,c

c

Qx2

QcF

&

= (3.11)

422,04,21x2

056,18cF ========

Lastly, the ground heat exchanger’s length is calculated both for cooling and

heating with Eq. (3.5) and (3.6).

(((( ))))(((( ))))

(((( ))))(((( ))))meters1164

2735

422,0x688,0068,08,5

18,5

22156cL

meters108513

213,0x688,0068,02,4

12,4

5297hL

====−−−−

++++++++

====

====−−−−

++++−−−−

====

The longer value is found for cooling and this value is chosen as heat

exchanger length. The system’s pictures are given in Appendix-6.B.


28

3.8.2 Short Method

This method is called short method. In this method ground heat changer’s

length is calculated both for cooling and heating needs with Eq. (3.12) and (3.13)

(Günerhan, Ülgen and Hepbaşlı, 2001).

cTxU

conQ

cL

∆=

&

(3.12)

hTxU

evapQ

hL

∆=

&

(3.13)

3.8.2.1. Heat Transfer in Heating Season (evap

Q& )

This value is calculated as 5296 W in 3.8.1.1.

3.8.2.2. Heat Transfer in Cooling Season (con

Q& )

This value is calculated as 22156 W in 3.8.1.2.

3.8.2.3. Heat Transfer Coefficient (U)

This value is calculated with Eq. (3.14). In this equation Rg and Rp values

are given as 0, 688 m0C / W and 0, 068 m0C / W in 3.8.1.5 and 3.8.1.6.


29

pR

gR

2U

+

π= (3.14)

068,0688,0

14,3x2U

+= = 8, 3 W / m0C

3.8.2.4. Temperature Different for Heating (∆∆∆∆Th)

This value is calculated with Eq. (3.15). In this equation Tih and Toh values

are the inlet and outlet temperatures of the heat pump and these values given as 10 0C

and 5 0C in figure-7. TL is the minimum temperature of the ground and this value is

given as 13 0C in 3.8.1.7.

2

TTTT ohih

Lh

+−=∆ (3.15)

2

51013Th

+−=∆ = 5, 5 0C

3.8.2.5. Temperature Different for Cooling (∆∆∆∆Tc)

This value is calculated with Eq. (3.16). In this equation Tic and Toc values

are the inlet and outlet temperatures of the heat pump and these values given as 30 0C

and 35 0C in figure-8. TH is the maximum temperature of the ground and this value is

given as 27 0C in 3.8.1.7.

Hocic

c T2

TTT −

+=∆ (3.16)


30

272

3530Tc −

+=∆ = 5, 5 0C

Lastly, the ground heat exchanger’s length is calculated both for cooling and

heating with Eq. (3.10) and (3.11). The longer value is chosen as heat exchanger

length

5,5x3,8

22156cL ==== = 485 meters

55,x38,

5297h

L = = 116 meters

We calculated the ground heat exchanger’s length for the 40-45 0C condenser

inlet and outlet temperatures in heating season and 5-10 0C evaporator inlet and

outlet temperatures in cooling season. At the same time the maximum and minimum

temperatures of the ground are taken as 27 0C and 13 0C. The heat exchanger’s

length is calculated again with the short and long methods to evaluation how it

changes with different ground and inlet-outlet temperatures. Firstly, the calculations

are done at the same inlet-outlet temperatures but different ground temperatures.

These calculations are given below.


31

Table-6. The Calculation Results Which is Calculated with Long Method for the Different Max. (27 0C) and Min. (10 0C) Ground Temperatures

Symbol Dimension Results

1 Heat Transfer in Heating Season evapQ& Watt 5297

2 Heat Transfer in Cooling Season conQ& Watt 22956

3 Heating Capacity of Chosen Heat Pump pumpheat,hQ Watt 27200

4 Cooling Capacity of Chosen Heat Pump pumpheat,cQ Watt 21400

5 Heating Performance h

COP - 4, 2

6 Cooling Performance c

COP - 5, 8

7 Pipe Resistance p

R - 0, 068

8 Ground Resistance g

R - 0, 668

9 Maximum Ground Temperature H

T 0C 27

10 Minimum Ground Temperature L

T 0C 10

11 Maximum Temperature of Heat Pump max

T 0C 35

12 Minimum Temperature of Heat Pump min

T 0C 5

13 Heating Working Factor h

F - 0, 213

14 Cooling Working Factor c

F - 0, 422

15 Ground Heat Changer’s Length for

Heating h

L m 173


Cooling c

L m 1164


32

Table-7. The Calculation Results Which is Calculated with Short Method for the Different Max. (27 0C) and Min. (10 0C) Ground Temperatures


1 Heat Loss hQ& Watt 11597

2 Heat Gain cQ& Watt 18056

3 Electric Power of the Heat Pump in Heating S. he

Q& Watt 6300

4 Electric Power of the Heat Pump in Cooling S. ce

Q& Watt 4100



7 Overall Heat Transfer Coefficient

U W/m 0C 8, 3

8 Pipe Resistance Rp - 0, 068

9 Ground Resistance Rg - 0, 668

10 Temperature Different for Heating ∆Th 0C 2, 5

11 Temperature Different for Cooling ∆Tc 0C 5, 5

12 Inlet Temp. of the H. P. in Cooling Season Tic 0C 30

13 Outlet Temp. of the H. P. in Cooling Season Toc 0C 35

14 Inlet Temp. of the H. P. in Heating Season Tih 0C 10

15 Outlet Temp. of the H. P. in Heating Season Toh 0C 5

16 Max. Ground Temperature TH 0C 27

17 Min. Ground Temperature TL 0C 10

18 Ground Heat Changer’s Length for Heating Lh m 255

19 Ground Heat Changer’s Length for Cooling Lc m 485


33








COP - 4, 2


COP - 5, 8

7 Pipe Resistance p

R - 0, 068


R - 0, 668


T 0C 24


T 0C 10


T 0C 35


T 0C 5


F - 0, 213


F - 0, 422


Heating h

L m 173


Cooling c

L m 846


34






Q& Watt 6300


Q& Watt 4100




U W/m 0C 8, 3














35








COP - 4, 2


COP - 5, 8

7 Pipe Resistance p

R - 0, 068


R - 0, 668


T 0C 24


T 0C 13


T 0C 35


T 0C 5


F - 0, 213


F - 0, 422


Heating h

L m 108


Cooling c

L m 846


36





3 Electric Power of the Heat Pump in Heating

Season heQ& Watt 6300

4 Electric Power of the Heat Pump in Cooling

Season ceQ& Watt 4100




U W/m 0C 8, 3














37

After these calculations, the inlet and outlet temperatures are changed as 40-

50 0C in heating season and 0-5 0C for cooling season. At these temperatures we can

use same model heat pump. The features of heat pump are;

cQ = 18, 2 kW Qec = 4, 2 kW COPc = 5, 2 kW

hQ = 26, 5 kW Qeh = 7 kW COPh = 3, 8 kW

heQ

hQ

evapQ &&& −=

evapQ& = 11597 – 7000 = 4597 W

ceQ

cQ

conQ &&& +=

conQ& = 18056 + 4200 = 22256 W

The results of the calculations are given below for the different ground

temperatures.


38








COP - 3, 8


COP - 5, 2

7 Pipe Resistance p

R - 0, 068


R - 0, 668


T 0C 27


T 0C 13


T 0C 35


T 0C 0


F - 0, 219


F - 0, 496


Heating h

L m 93


Cooling c

L m 1357


39












U W/m 0C 8, 3














40








COP - 3, 8


COP - 5, 2

7 Pipe Resistance p

R - 0, 068


R - 0, 668


T 0C 27


T 0C 10


T 0C 35


T 0C 0


F - 0, 219


F - 0, 496


Heating h

L m 148


Cooling c

L m 1357


41












U W/m 0C 8, 3














42








COP - 3, 8


COP - 5, 2

7 Pipe Resistance p

R - 0, 068


R - 0, 668


T 0C 24


T 0C 10


T 0C 35


T 0C 0


F - 0, 219


F - 0, 496


Heating h

L m 148


Cooling c

L m 987


43






Q& Watt 7000


Q& Watt 4200




U W/m 0C 8, 3














44








COP - 3, 8


COP - 5, 2

7 Pipe Resistance p

R - 0, 068


R - 0, 668


T 0C 24


T 0C 13


T 0C 35


T 0C 0


F - 0, 219


F - 0, 496


Heating h

L m 93


Cooling c

L m 987


45






Q& Watt 7000


Q& Watt 4200




U W/m 0C 8, 3














46

3.9.Cost Price Calculations

3.9.1.Cost of Ground Source Heat Pump System

The cost calculation is carried out for the 40-45 0C condenser inlet and outlet

temperatures in heating season and 5-10 0C evaporator inlet and outlet temperatures

in cooling season. At the same time the maximum and minimum temperatures of the

ground are taken as 27 0C and 13 0C. Also, this calculation is done for the long and

short method’s results.

The materials which are used in system and their prices are given below.

3.9.1.1.Heat Pump

Vitocal 300 BW 220 type heat pump’s price is 11198 €. This heat pump

contains circulation pumps and compressor.

3.9.1.2.Ground Heat Exchanger

In long method, the polyethylene pipe which is 1 1/2” diameter and 1164

meters length is used as ground heat exchanger. The 1, 5 meter depth and 356 m2

hollow must be used for this pipe. This process is costing 3293 €.

In the short method, the polyethylene pipe which is 1 1/2” diameter and 485

meters length is used as ground heat exchanger. The 1, 5 meter depth and 126 m2

hollow must be used for this pipe. This process is costing 1955 €.

3.9.1.3.Expansion Tank

MT 25 type of Alarco Carrier firm is chosen as expansion tank. This tank’s

price is 29 €.


47

3.9.1.4.Fan Coil

The prices of the Fan Coils are given in Table-6.

Table-20. Fan Coil Type’s Price

FAN COIL TYPE PRICE

42 FA 01 172 €

42 FA 02 177 €

42 FA 03 184 €

In our system 5 units 42 FA 01, 4 units 42 FA 02 and 8 units 42 FA 03 type

Fan Coil is used. Total prices of the fan coils are 3040 €.

3.9.1.5.Pipe System for Inside of Building

The pipe system’s price is 800 €.

Table-21. The materials and their prices for the long method’s results

MATERIALS PRICE

Heat Pump 11198 €

Ground Heat Exchanger 3293 €

Expansion Tank 29 €

Fan Coil 3040 €

Pipe System for inside of building 800 €

TOTAL ( AI ) 18360 €


48

Table-22. The materials and their prices for the short method’s results

MATERIALS PRICE

Heat Pump 11198 €

Ground Heat Exchanger 1955 €

Expansion Tank 29 €

Fan Coil 3040 €

Pipe System for inside of building 800 €

TOTAL ( AI ) 17022 €

“Present Worth Cost Method” is used while calculating cost price of the

ground source heat system (KINCAY and TEMİR, 2002).

Yearly nominal interest rate is taken 8% and total system life is determined 15

years. Amortization factor is calculated with Eq. (4.1) and found as 0, 11683.

( )( ) ii1

ixi1AF

n

n

−+

+=

(4.1)

Yearly first investment cost of the system is calculated with Eq. (4.2) and

found as 2145 € for the long method’s results. Also, it is found as 1989 € for the

short method’s results.

AFxAIAC = (4.2)

To find the yearly cost of the system for today, we must add the yearly

renovation cost and yearly electric cost.

The system works 10 hours a day and 120 days a year in cooling season. Also

it works 12 hours a day and 150 days a year in heating season. It works 1200 hours in

cooling season and 1800 hours in heating season.

The heat pump’s electric power for heating cycle is 6, 3 kW and for cooling

cycle is 4, 1 kW. Yearly electric power in heating season 11340 kWh and in cooling


49

season is 4920 kWh. Yearly total electric power is 16260 kWh. The price of the 1

kW electric is 0, 09 €. Yearly total electric price is 1463 €.

Yearly renovation cost of the system is the fife per cent of the first investment

cost. This value is found as 918 € for the long method’s results. It is found as 851 €

for the short method’s results.

Yearly cost of the system for today is found as 2381 € for the long method’s

results. For the long method’s results, this value is calculated as 2314 €.

Escalating factor which is used for electric in Eq. (4.3) is taken as 4% and

yearly total cost of the system for today is calculated as 25730 € for the long

method’s results. Also, it is found as 25006 € for the short method’s results.

(((( ))))(((( )))) (((( )))) (((( ))))

fei

ni1xnfe11

PWOMC

PWOMI−−−−

−−−−++++++++−−−−====

(4.3)

Yearly cost of the system is calculated with Eq. (4.4) and found as 3006 € for

the long method’s results and 2921 € for the short method’s results.

( ) AFxPWOMIOMC = (4.4)

And then the yearly total cost of the system is calculated with Eq. (4.5) and

found as 5151 € for the long method’s results and 4910 € for the short method’s

results.

OMC

AC

TC += (4.5)

The results of the cost price calculations for the long and short methods are

given in Table-23.


50

Table-23. Cost of Ground Source Heat Pump System

SYMBOL Ground Source Heat Pump Sys.

(For the Long Method’s Results)

Ground Source Heat Pump Sys.

(For the Short Method’s Results)

IA 18360 € 17022 €

CA 2145 €/year 1989 €/year

(COM)PW 2381 €/year 2314 €/year

(IOM)PW 25730 € 25006 €

COM 3006 €/year 2921 €/year

CT 5151 €/year 4910 €/year

This cost price calculation is carried out for the different ground temperatures.

But the cost price calculation is not carried out for the 27-10 0C ground temperatures.

Because the longer ground heat exchanger’s length is same with the 27-13 0C ground

temperatures. This calculation is done for the 24-100C ground temperatures and the

results are given in Table-24.


51

Table-24. Cost of Ground Source Heat Pump System Which is Calculated for the Different Max. (24 0C) and Min. (10 0C) Ground Temperature

SYMBOL Ground Heat Pump System


Ground Heat Pump System


IA 17734 € 16685 €

CA 2072 €/year 1949 €/year


(IOM)PW 25395 € 24823 €


CT 5039 €/year 4849 €/year

The inlet and outlet temperatures are changed as 40-50 0C in heating season

and 0-5 0C for cooling season. And the cost price calculation is done for the 27-130C

and 24-100C ground temperatures. The results of the calculations are given in Table-

25 and 26.


52






IA 18740 € 17026 €

CA 2189 €/year 1989 €/year


(IOM)PW 27286 € 26357 €


CT 5377 €/year 5068 €/year






IA 18011 € 16687 €

CA 2104 €/year 1950 €/year


(IOM)PW 26897 € 26173 €


CT 5246 €/year 5008 €/year

4. RESULTS AND DISCUSSION İsmail KILIÇ

53

4. RESULTS AND DISCUSSION

Before beginning with the design, ground source heat pump system for a

building, firstly the heat insulation, heat loss and heat gain calculations must be

carried out. Than, the heat pump and fan-coil types must be chosen, and pipe

diameters and ground heat exchanger’s length must be determined.

In this system the heat source must be researched very well. Because the

ground resistance, yearly average ground temperature and ground type are very

important for the cost price. Otherwise the system is not economical.

In this study, a ground source heat pump system is designed for a 280 m2

doublex villa which has been in Adana. The system can carry out heating and cooling

simultaneously. Firstly, the heat insulation, heat loss and heat gain calculations are

carried out, the heat pump and fan-coil types are chosen and pipe diameters and

ground heat exchanger’s length are determined for the model building with different

methods. Lastly the cost price of the system is calculated with the “Present Worth

Cost Method”.

Firstly, the condenser’s inlet and outlet temperatures are determined 40 0C -

45 0C in heating season and the evaporator’s inlet and outlet temperatures are

determined 5-10 0C in cooling season. The maximum and minimum ground

temperatures are taken as 27 0C and 13 0C and the ground heat exchanger’s length is

calculated with short and long methods. The ground heat exchanger’s length is found

1164 meters for cooling season and 108 meters for heating season with long method.

Also it is found as 485 meters for cooling season and 116 meters for heating season

with short method. And then all values are fixed and the low ground temperature is

taken as 10 0C. At the end of the calculation, the calculated ground heat exchanger’s

length for the cooling season does not change. But the calculated value for the

heating season is increased.

Secondly, the maximum and minimum ground temperatures are changed as

24 0C and 13 0C. At this time the calculated ground heat exchanger’s length for the

heating season does not change. But the calculated value for the cooling season is

decreased.


54

Lastly, the maximum and minimum ground temperatures are taken as 24 0C

and 10 0C. At the end of the calculation ground heat exchanger’s length is decreased

for the cooling season and it is increased for the heating season.

And then the condenser’s inlet and outlet temperatures are changed as 40-50 0C and the evaporator’s inlet and outlet temperatures are changed as 0-5 0C. The

calculations are done again with two methods and the same results are seen.

The calculation results are given in Table-27.

Table 27. Ground Heat Exchanger’s Length Calculation Results

Inlet and Outlet Temperatures

Max. and Min. Ground

Temperatures

Long Method Results

Short Method Results

Lh = 108 m Lh = 116 m 27

0C – 13

0C

Lc = 1164 m Lc = 485 m

Lh = 173 m Lh = 255 m 27

0C – 10

0C

Lc = 1164 m Lc = 485 m

Lh = 173 m Lh = 255 m 24

0C – 10

0C

Lc = 846 m Lc = 314 m

Lh = 108 m Lh = 116 m

Heating Season

Condenser (40 – 45

0C)

Evaporator (10 – 5

0C)

Cooling Season


0C)


0C)

24

0C – 13

0C

Lc = 846 m Lc = 314 m

Lh = 93 m Lh = 101 m 27

0C – 13

0C

Lc = 1357 m Lc = 487 m

Lh = 148 m Lh = 221 m 27

0C – 10

0C

Lc = 1357 m Lc = 487 m

Lh = 148 m Lh = 221 m 24

0C – 10

0C

Lc = 987 m Lc = 315 m

Lh = 93 m Lh = 101 m

Heating Season


0C)


0C)

Cooling Season


0C)

Evaporator (0 – 5

0C)

24

0C – 13

0C

Lc = 987 m Lc = 315 m

According to the calculations, if the ground temperature is low in cooling

season, transferred heat to the ground will be higher. Same reason, if the ground

temperature is high in heating season, transferred heat from the ground will be


55

higher. This is why; the ground heat exchanger’s length of the system is decreased.

In this way, the yearly total cost of the system is decreased.

There is a big different between calculated heat exchanger’s length with long

and short methods for cooling season. The COP and Fc values are used in long

method. But these values are not used in short method. Also, the maximum

temperature of the heat pump is used in long method. But the average temperature of

the condenser’s inlet and outlet temperatures is used in short method. At the same

time the (2π) value is used and this value is the biggest factor which is decreased the

heat exchanger’s length in short method.

Although the ground source heat pump system’s cost is much more then the

other systems, this system must be used because of its advantages which are given

below.

Advantages of the Ground Source Heat Pump System

� Heating without combustion of less fossil fuels

� No carbon monoxide or carbon dioxide

� Increased safety

� Simpler design, maintenance and operation

� Free hot water in the summer

� No unsightly/noisy air conditioning or air source heat pumps in the yard

� Smaller mechanical rooms or closets, saving space for other uses

� Lower annual maintenance costs

The ground source heat pump system is used in abroad commonly. We must

give importance to this system in our country especially for cold regions. For this

goal especially we must study how to decrease total cost of the system.

5. CONCLUSION İsmail KILIÇ

56

5. CONCLUSION

In this thesis, a Ground Source Heat Pump System is designed for a 280 m2

doublex villa which is located in Adana. The ground heat exchanger’s length is

determined with two different methods and the cost of the system is calculated. By

taking into consideration of the results, the initial cost of the system is found to be

more expensive than the other systems.

From the results, it can be concluded that ground heat exchanger’s length is

much longer for cooling then for heating. Therefore ground heat heat exchanger’s

length shoul be determined for cooling.

Considering the large amount of the energy consumed for heating and

cooling, the use of ground source heat pump systems should be encouraged.

Although the initial cost is expensive, importance should be given to ground

source heat pump systems that are used widespread in foreign countries.

57

REFERENCES

ANON, 1944. Energy Economy and the Thermodynamic Heat Pump, 7-9. 85-116.

AKBULUT, A., KURTBAŞ, İ., ve GÜLÇİMEN, F., 2006. Toprak Kaynaklı Isı

Pompası Destekli Bir Biyogaz Sisteminin Sera Isıtmasında Kullanımının

Deneysel Olarak İncelenmesi, Mühendis ve Makina, 47(555): 50-61.

ASHRE Fudamentals Handbook, 2001. Chapter 29: Nonresidential Cooling and

Heating Load Calculation Procedures, Atalanta.

______, 2001. Chapter 30: Fenestration, Atalanta.

AYDIN, K., 1986. Isı Pompası Teorik Modellemesi, Fen Bilimleri Enstitüsü

Makine Mühendisliği Anabilim Dalı Yüksek Lisans Tezi, Kod No:101,

Adana, 96s.

BAKER, M., 1953. Desing and Performance of Residential Earth Heat Pump,

ASHRE Trans, 59, 94-371.

CHI, J., DIDION, D.A., 1983. A Simulation Model of the Transient Performance of

a Heat Pump. International Journal of Refrigeration, 5/3. 176-183.

COELMAN, J.J., 1879. Air Refrigerating Machinery and Its Applications. Proc. Inst.

Civil Engrs, 68. 70-146.

COUVILLION, R.J., 1985. Field and Laboratory Simulation of Earth Coupled Heat

Pump Coils, 91. 1326-1334.

DOMANSKI, P., DIDION, D.A., 1984. Mathematical Model of an Air-to-Air Heat

Pump Equipped with a Capillary Tube. International Journal of Refrigeration,

7/4. 249-255.

ESEN, H., İNALLI, M., and ESEN, M., 2003. Yatay Toprak Kaynaklı Isı Pompası

Sisteminin Deneysel Uygulaması, Mühendis ve Makine, 44(523): 29-35.

FERRANTI, B.de., 1955. Heat Pumps in the House. Electrical Times 27, October,

8-627.

FISCHER, S.K., RICE, C.K., 1981. A Steady-State Computer Design Model for

Air-to-Air Heat Pumps. Oak Ridge National Laboratory. Report No:

ORCL/CON-80.

58

GENCELİ, F.O. and PARMAKSIZOĞLU, I.C, 2006. Kalorifer Tesisatı, MMO

Yayınları, Yayın No:MMO / 352 / 3, İstanbul, 410s.

GÜNERHAN, H., ÜLGEN, K. and HEPBAŞLI, A., 2001. Jeotermal (Toprak

Kaynaklı) Isı Pompalarında Toprak ısı Değiştiricisinin Tasarımı: Ege

Üniversitesi Uygulaması, 13. Ulusal Isı Bildirimi ve Tekniği Kongresi

HALDANE, T.G.N., 1930. The Heat Pump-An Economical Method of Producing

Low-Grade Heat from Electricity, J.I.E.E.E., 6-145.

HALMOS, E.E., 1975. Defense Dept. with Draws Ban. Air Conditioning, Heating

and Refrigeration News. 8 September. 1-4.

HEAP, R.D., 1979. Heat Pumps. E.F.N. Spon Ltd. LONDON.

HEPBAŞLI, A., ERTÖZ, A.Ö., 1999. Geleceğin Teknolojisi: Yer Kaynaklı Isı

Pompaları, Makina Mühendisleri Odası Teskon Program Bildirileri, 445-492.

HEPBAŞLI, A., HANCIOĞLU, E., 2001. Toprak Kaynaklı(Jeotermal) Isı

Pompalarının Tasarımı,Testi ve Fizibilitesi, Makina Mühendisleri Odası

Teskon Program Bildirileri, 339-382.

HUGHES, P.J, LOOMIS, L., O’NEIL, R.A. and RIZZUTO, J., 1985. Results of

the Residential Earth-Coupled Heat Pump Demonstration in Upstate New

York, ASHRAE Transactions, 91. 1307-1325.

KARAKOÇ, H. T., 2001. Kalorifer Tesisatı Hesabı, Demir Döküm Teknik

Yayınları No:1, 211s

KEMLER, E.N. and OGLESBY., 1950. Heat Pump Applications, McGraw-Hill.

New York.

KINCAY, O., TEMİR, G., 2002. Toprak ve Hava Kaynaklı, Isı Pompalı

Sistemlerin Ekonomik İncelenmesi, Tesisat Mühendisliği, 44(68): 31-37.

MAKİNA MÜHENDİSLERİ ODASI, 2002. Klima Tesisatı (İ.Y. URALCAN

editör), MMO Yayınları, Yayın No: MMO / 2002 / 296-2, Ankara, 458s.

MONTAGNON, P.E., and RUCKLEY, A.L., 1954. The Festival Hall Heat Pump,

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PIHTILI, K., BOZKIR, O., Isı Pompası ile Sıcak Su Üretimi, IV.Ulusal Soğutma

ve İklimlendirme Tekniği Kongresi, Adana, 295-302.

59

SULATISKY, M.T. and VAN DER KAMP, G., 1991. Ground-Source Heat

Pumps in the Canadian Prairies, ASHRAE Transactions, 97. 374-385.

SUMNER, J.A., 1955. Domestic Heating by the Heat Pump, J.Inst., Heating and

Ventilating Engrs., 23(July), 51-129.

ŞENDAĞ, M.T., 1992. Çok Amaçlı Isı Pompası İmalat ve Uygulaması, Fen

Bilimleri Enstitüsü Makine Mühendisliği Anabilim Dalı Yüksek Lisans Tezi,

Kod No:626, Adana, 86s.

THOMSON, W., 1852. On the economy of the heating or cooling of buildings by

means of currents of air. Glasgow Phil. Soc. Proc. 72-269.

TS 825, 1998. Binalarda Isı Yalıtım Kuralları, Birinci Baskı, Ankara, 62s.

YILMAZ, T., 2002. Isıtma ve İklimlendirme, Ç.Ü.Müh. Mim.Fakültesi, Yayın

No:39, Adana, 197s.

______, 2004. Soğutma Sistemleri ve Elemanları, Ç.Ü.Müh. Mim.Fakültesi,

Yayın No:03, Adana, 122s.

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Hot Water Heating, Technical and Symposium Papers Presented at the 1989

Winter Meeting in Chigago, Illinois, Vol.95, Part 1, 441-444.

60

CIRRICULUM VITATE

I was born on August 23, 1981 in Mersin. When I finished the primary school

in Hatay, I won the Silifke Anatolian High School. In 1999 I started the Mechanical

Engineering Department of the Hatay Mustafa Kemal University. I finished this

department in 2003. At the same year I started the MSc studies at the Department of

Mechanical Engineering of Çukurova University. Also in 2003, I started to work in

Silifke Pişirgen Makine İmalat Sanayi Ticaret Limited Company as a Manufacturing

Engineering. I am still working in this company.

61

APPENDİX – 1

A. Specific Heat Loss Calculation Form

1 2 3 4 5 6

Building Elements Thickness

Thermal Conductivity

Overall Heat

Transfer Coefficient

Heat Transfer Surface

Heat Loss

D λh

d/λ 1/x

U A UxA

Building Elements

M W/mK mK/W W/Mk m W/K

1/αi 0,13

Plaster 0,02 0,87 0,023

Concrete 0,18 2,1 0,086

Heat isola.Mate. 0,067 0,04 1,675

Plaster 0,02 1,4 0,014

Wall Surface

1/αd 0,04

Total 1,968 0,5 259 130

1/αi 0,13

Diamond Mosaic 0,03 1,3 0,023

Heat isola.Mate. 0,06 0,04 1,5

Concrete 0,03 1,4 0,021

Concrete 0,015 1,74 0,009

Blokaj 0,1 0,7 0,143

Sole

1/αd 0

Total 1,826 0,274 140 38

1/αi 0,13

Plaster 0,02 0,87 0,023

Concrete 0,15 1,3 0,115

Heat isola.Mate. 0,035 0,04 0,875

Ceiling

1/αd 0

Total 1,143 0,7 140 98

Glass 2,6 38,8 101

Heat loss total with building elements = 367

ΣAU= UOW. AOW + UW. AW + 0.8 UC. AC + 0.5 US. AS + UAS. AAS + 0.5 ULowTemp. ALowTemp

Specific Heat Loss

Hs = Hi + Hh = 367 + 244 = 611

Heat Loss With Convection

Hi =ΣΑU + Iui

Heat Loss With Ventilation

Hh = 0,33 x nh x Vh = 0,33 x 1 x 740 = 244

62

B. The Yearly Needed Heat Energy Calculation Form

Heat Loss Heat Gains

Specific Heat Loss

Temperature Difference

Heat Loss Inside Heat

Gain Sun Energy

Gain Total

Gain Loss Rate

Gain Usage Factor

Heating Energy Need

Hs=Hi+Hh Ti-Td H(Ti-Td) φi φg φt=φi+φg γ ηmonth Qmonth

Month

(W/K) (K, C) (W) (W) (W) (W) (-) (-) (kJ)

January 11 6721 787 2265 0,34 0,94 11902205

February 9,7 5927 969 2447 0,41 0,91 9590996

March 7,5 4583 1190 2668 0,58 0,82 6208462

April 3,3 2016 1210 2688 1,33 0,52 1602478

May 1447 2925

June 1526 3004

July 1483 2961

August 1393 2871

September 1181 2659

October 0,9 550 971 2449 4,45

November 5,7 3483 740 2218 0,64 0,79 4486182

December

611

9,6 5866

1478

690 2168 0,37 0,93 9978578

Qy=ΣQm= 43768901

Total Heat Lost Qyear = 0.278 x 0.001 x 43768901 = 12168 kWh

Inside Heat Gain for House φi,month < 5xAn (W)

Sun Energy Gain φg,month= Ση month x gi, month x Ii, month x Ai

Gain Loss Rate GLRmonth=(φi,ay+φg,ay)/H(Ti,ay-Td,ay)

Gain Used Factor ηmonth =1-e(-1/ GLRmonth)

The yearly needed heat energy which is required for the usage area An in the model building;

Q=Qyear / An = ………….. kWh/m2 An=0.32 Vbrüt= ……… m

2

The yearly needed heat energy which is required for the heated building volume in the model building;

Q = Qyıl / Vbrüt = 13,2 When the ratio Atop / Vbrüt = 0,63 is replaced with the

Q' =14.92x(A / V)+5.56 formula coming from addition for the first region, the biggest heat lost which is

expected for the model building is found Q' =.......kWh/m2 or Q' = 14,96 kWh/m

3 and comparing with

the value Q. The suitability of heat lost of the project is defined. Because 13,2 < 14,96

Q < Q' it is seen that the need of yearly heat energy is under the highest expected value. Then this project

is suitable for the calculation method in this standards.

63

APPENDİX – 2

A. Heat Loss Calculation Table

Building Components Area Calculate Heat Lost Calculate Savings 1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16

Sin

g

Dir

ectio

n

Thi

ckne

ss

Len

gth

Hig

ht

Tot

al A

rea

Am

ount

Ext

erna

l Are

a

Inte

rnal

Are

a

Ove

rall

Hea

t T

rans

fer

Coe

ffic

ient

Tem

pera

ture

Dif

fere

nt

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t Los

s

Uni

ted

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easi

ng

Coe

ffic

ient

Flo

or H

igh

Incr

easi

ng

Coe

ffic

ient

Dir

ecti

on I

ncre

asin

g C

oeff

icie

nt

Tot

al

Tot

al H

eat N

eed

Ao A U ∆T Qo ZD ZW ZH Z Qh = Qi + Qs

cm m m m2 Ad m2 m2 Watt m2K

Watt % % % 1+% Watt

101 ENTRANCE (15 OC) OD N 1 2,2 2,2 1 2,2 2,6 15 86

OW N 5,2 3,5 18,2 1 2,2 16 0,5 15 120

OD W 1 2,2 2,2 1 2,2 2,6 5 29

OW W 2,7 3,5 9,45 1 2,2 7,25 0,5 5 18 IW W 1,1 3,5 3,85 1 3,85 0,5 -5 -10 DGW E 0,5 0,5 0,25 1 0,25 2,6

15 10

OW E 2,7 3,5 9,45 1 0,25 9,2 0,5 15 69 ID S 0,8 2,2 1,76 2 3,52 2,6 -5 -46

IW S 2,3 3,5 8,05 1 3,52 4,53 1,61 -5 -36

ID E 0,8 2,2 1,76 1 1,76 2,6 -9 -41

IW E 1,1 3,5 3,85 1 1,76 2,09 1,61 -9 -30

169 0,1 0 0,05 1,12 189

Qs = ( 1 / 3,6 ) ∑ ( a x l ) x R x H x ∆T x Ze Qs = ( 1 / 3,6 ) x 2 x 13,24 x 1 x 2,43 x 18 x 1 290 479 Qs x 3600

n =

( c x r x Vroom x DT ) 290 x 3600

n =

( 1005 x 1,2 x 52,2 x 18 ) = 0,921

102 BATH (24 OC) IW N 2,7 3,5 9,45 1 9,45 1,61 9 137 DGW E 0,5 0,5 0,25 1 0,25 2,6

24 16

OW E 2,2 3,5 7,7 1 0,25 7,45 0,5 24 89

IW W 0,9 3,5 3,15 1 3,15 1,61 9 46

IW S 2,7 3,5 9,45 1 9,45 1,61 4 61

349 0,1 0 0 1,07 373

Qs = ( 1 / 3,6 ) ∑ ( a x l ) x R x H x ∆T x Ze Qs = ( 1 / 3,6 ) x 2 x 1,81 x 1 x 2,43 x 26 x 1 57 430 Qs x 3600

n =

( c x r x Vroom x DT ) 57 x 3600

n =

( 1005 x 1,2 x 20,25 x 26 ) = 0,323

64

A. Heat Loss Calculation Table(Continuing) Page Floor HEAT LOSS CALCULATION TABLE Date


Sin

g

Dir

ecti

on

Thi

ckne

ss

Len

gth

Hig

ht

Tot

al A

rea

Am

ount

Ext

erna

l Are

a

Inte

rnal

Are

a

Ove

rall

Hea

t T

rans

fer

Coe

ffic

ient

Tem

pera

ture

D

iffe

rent

Hea

t Los

s

Uni

ted

Incr

easi

ng

Coe

ffic

ient

Flo

or H

igh

Incr

easi

ng

Coe

ffic

ient

D

irec

tion

In

crea

sing

C

oeff

icie

nt

Tot

al

Tot

al H

eat N

eed

Ao A U ∆T Qo ZD ZW ZH Z Qh = Qi+Qs

cm m m m2 Ad m

2 m

2

Watt m

2K

Wat

t % % %

1+%

Watt

103 LIVING ROOM (20 OC)

IW W 4 3,5

12,775 1

12,775 1,61

0 0

OW N 1 3,5 3,5 1 3,5 0,5 20 35

DGW E 2 1,5 3 1 3 2,6 20 156

OW E 6 3,5 19,25 1 3 16,25 0,5 20 163

DGW S 3 2 6 1 6 2,6 20 312

OW S 6 3,5 22,4 1 6 16,4 0,5 20 164 ID W 1 2,2 1,76 1 1,76 2,6 0 0

IW W 2 3,5 5,775 1 2,2 3,575 1,61 0 0

IW N 2 3,5 8,05 1 8,05 1,61 0 0

830 0,1 0 -

0,05 1,02 847

Qs = ( 1 / 4 ) ∑ ( a x l ) x R x H x ∆T x Ze Qs = ( 1 / 4 ) x 2 x 27,9 x 1 x 2,4 x 22 x 1 746 1593 Qs x 3600

n =

( c x ρ x Vroom x ∆T ) 746 x 3600

n =

( 1005 x 1,2 x 108,24 x 18 ) = 1,143

104 KITCHEN (20 OC)

OW N 4 3,5 15,4 1 15,4 0,5 10 77

DGW W 1 1,5 1,95 2 3,9 2,6 20 203

OW W 6 3,5 19,25 1 3,9 15,35 0,5 20 154

OW N 1 3,5 2,8 1 2,8 0,5 20 28

DGW W 2 1,5 3 1 3 2,6 20 156

OW W 5 3,5 16,45 1 3 13,45 0,5 20 135

DGW S 2 1,5 3 1 3 2,6 20 156

OW S 5 3,5 18,9 1 3 15,9 0,5 20 159

OD E 1 2,2 2,2 1 2,2 2,6 20 114 OW E 2 3,5 8,05 1 1,5 6,55 0,5 20 66

1248 0,1 0

-0,05 1,02 1273

Qs = ( 1 / 4 ) ∑ ( a x l ) x R x H x ∆T x Ze Qs = ( 1 / 4 ) x 2 x 35,1 x 1 x 2,4 x 18 x 1,2 718 1991 Qs x 3600

n =

( c x ρ x Vroom x ∆T ) 718 x 3600

n =

( 1005 x 1,2 x 167 x 18 ) = 0,713

65

A. Heat Loss Calculation Table(Continuing)

Page Floor HEAT LOSS CALCULATION TABLE Date


Sin

g

Dir

ectio

n

Thi

ckne

ss

Len

gth

Hig

ht

Tot

al A

rea

Am

ount

Ext

erna

l Are

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icie

nt

Tot

al

Tot

al H

eat N

eed


cm m m m2 Ad m

2 m

2

Watt m

2K

Watt % % % 1+% Watt

201 BATH (24 OC)

DGW N 1 0,5 0,25 1 0,25 2,6 24 16

OW N 2 3,5 7 1 0,3 6,75 0,5 24 81

OW E 0 3,5 1,4 1 1,4 0,5 24 17 OW W 0 3,5 1,4 1 1,4 0,5 24 17

OD W 1 2,2 1,76 1 1,76 2,6 24 110

OW W 3 3,5 9,45 1 2,2 7,25 0,5 24 87

OW N 2 3,5 7 1 7 0,5 24 84

ID S 1 2,2 1,76 1 1,76 2,6 9 41

IW S 1 3,5 4,9 1 1,8 3,14 2,6 9 73 IW S 3 3,5 11,2 1 11,2 1,61 4 72

C 13,89 0,7 24 233

831 0,1 0 0 1,07 889


n =

( c x ρ x Voda x ∆T ) 181 x 3600

n = ( 1005 x 1,2 x 43 x 26 )

= 0,486

202 ENTRANCE (15 OC)

OD N 1 2,2 2,2 1 2,2 2,6 15 86 OW N 5 3,5 18,2 1 2,2 16 0,5 15 120

DGW E 1 0,5 0,25 1 0,25 2,6 15 10

OW E 3 3,5 9,45 1 0,3 9,2 0,5 15 69

IW S 3 3,5 9,45 1 9,45 1,61 -9 -137

IW E 1 3,5 3,85 1 3,85 1,61 -9 -56

IW W 3 3,5 9,45 1 9,45 1,61 -9 -137 ID S 1 2,2 1,76 1 1,76 2,6 -5 -23

IW S 2 3,5 8,05 1 2 6,07 1,61 -5 -49

C 16,57 0,7 15 174

57 0,1 0 0,05 1,12 64


n =

( c x ρ x Vroom x ∆T ) 164 x 3600

n =

( 1005 x 1,2 x 67 x 18 ) = 0,406

66




Sin

g

Dir

ecti

on

Thi

ckne

ss

Len

gth

Hig

ht

Tot

al A

rea

Am

ount

Ext

erna

l Are

a

Inte

rnal

Are

a

Ove

rall

Hea

t T

rans

fer

Coe

ffic

ient

Tem

pera

ture

D

iffe

rent

Hea

t Los

s

Uni

ted

Incr

easi

ng

Coe

ffic

ient

F

loor

Hig

h In

crea

sing

C

oeff

icie

nt

Dir

ecti

on

Incr

easi

ng

Coe

ffic

ient

Tot

al

Tot

al H

eat N

eed


cm m m m2 Ad m

2 m

2

Watt m

2K

Watt % % % 1+% Watt

203 BATH (24 OC)

DGW E 1 0,5 0,25 1 0,25 2,6 24 16

OW E 2 3,5 7,7 1 0,3 7,45 0,5 24 89

ID S 1 2,2 1,76 1 1,76 2,6 4 18

IW S 3 3,5 9,45 1 1,8 7,69 1,61 4 50

IW W 1 3,5 3,15 1 3,15 1,61 4 20

C 3 2,2 5,94 1 5,94 0,7 24 100

293 0,1 0 0 1,07 314

Qs = ( 1 / 4 ) ∑ ( a x l ) x R x H x ∆T x Ze

Qs = ( 1 / 4 ) x 2 x 1,81 x 1 x 2,4 x 18 x 1 40 354

Qs x 3600

n =

( c x ρ x Vroom x ∆T )

40 x 3600

n =

( 1005 x 1,2 x 19 x 26 ) = 0,242

204 BEDROOM (20 OC)

DGW W 1 1,5 1,95 1 1,95 2,6 20 101

OW W 3 3,5 10,15 1 2 8,2 0,5 20 82

OW S 1 3,5 4,2 1 4,2 0,5 20 42

OW N 1 3,5 3,15 1 3,15 0,5 20 32

IW S 3 3,5 10,15 1 10,15 1,61 0 0

ID E 1 2,2 1,76 1 1,76 2,6 5 23

IW E 3 3,5 10,15 1 2 8,17 1,61 5 66

C 4 2,9 12,47 1 12,47 0,7 20 175

521 0,1 0 0 1,07 557

Qs = ( 1 / 4 ) ∑ ( a x l ) x R x H x ∆T x Ze

Qs = ( 1 / 4 ) x 2 x 7,683 x 1 x 2,4 x 20 x 1 187 744

Qs x 3600

n =

( c x ρ x Vroom x ∆T ) 187 x 3600

n =

( 1005 x 1,2 x 50 x 20 ) = 0,559

67




Sin

g

Dir

ecti

on

Thi

ckne

ss

Len

gth

Hig

ht

Tot

al A

rea

Am

ount

Ext

erna

l Are

a

Inte

rnal

Are

a

Ove

rall

Hea

t T

rans

fer

Coe

ffic

ient

Tem

pera

ture

Dif

fere

nt

Hea

t Los

s

Uni

ted

Incr

easi

ng

Coe

ffic

ient

F

loor

Hig

h In

crea

sing

C

oeff

icie

nt

Dir

ectio

n In

crea

sing

C

oeff

icie

nt

Tot

al

Tot

al H

eat N

eed


cm m m m2 Ad m

2 m

2

Watt m

2K

Watt % % % 1+% Watt

205 BEDROOM (20 OC)

DGW W 1 1,5 1,95 1 1,95 2,6 20 101

OW W 3 3,5 8,75 1 2 6,8 0,5 20 68 ID E 1 2,2 1,76 1 1,76 2,6 5 23

İW E 3 3,5 8,75 1 2,1 6,68 1,61 5 54

İW S 3 3,5 10,15 1 10,15 1,61 0 0 C 3 2,5 7,25 1 7,25 0,7 20 102

348 0,1 0 0 1,07 372


n =

( c x ρ x Vroom x ∆T ) 187 x 3600

n =

( 1005 x 1,2 x 26 x 20 ) = 1,057

206 BEDROOM (20 OC)

İD N 1 2,2 1,76 1 1,76 2,6 5 23

İW N 1 3,5 4,9 1 1,8 3,14 1,61 5 25

OW N 1 3,5 2,8 1 2,8 1,61 20 90 DGW W 2 1,5 3 1 3 2,6 20 156

OW W 5 3,5 16,45 1 3 13,45 0,5 20 135

DGW S 2 1,5 3 1 3 2,6 20 156 OW S 3 3,5 11,55 1 3 8,55 0,5 20 86

OW S 2 3,5 5,95 1 5,95 0,5 20 60

OW W 2 3,5 7 1 7 0,5 20 70

OW E 3 3,5 11,55 1 11,55 0,5 20 116

C 32,64 0,7 20 457

1374 0,1 0 -0,05 1,02 1401

Qs = ( 1 / 4 ) ∑ ( a x l ) x R x H x ∆T x Ze Qs = ( 1 / 4 ) x 2 x 19,8 x 1 x 2,4 x 20 x 1,2 449 1850 Qs x 3600

n =

( c x ρ x Vroom x ∆T ) 449 x 3600

n =

( 1005 x 1,2 x 76 x 20 ) = 0,882

68


Page

Floor HEAT LOSS CALCULATION TABLE

Date

Building Components Area Calculate Heat Lost Calculate Savings

1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16

Sin

g

Dir

ecti

on

Thi

ckne

ss

Len

gth

Hig

ht

Tot

al A

rea

Am

ount

Ext

erna

l Are

a

Inte

rnal

Are

a

Ove

rall

Hea

t T

rans

fer

Coe

ffic

ient

Tem

pera

ture

Dif

fere

nt

Hea

t Los

s

Uni

ted

Incr

easi

ng

Coe

ffic

ient

Flo

or H

igh

Incr

easi

ng

Coe

ffic

ient

Dir

ecti

on I

ncre

asin

g C

oeff

icie

nt

Tot

al

Tot

al H

eat N

eed


cm m m m2 Ad m

2 m

2

Watt m

2K

Watt % % % 1+% Watt

207 BEDROOM (20 OC)

ÇCP E 2 1,5 3 1 3 2,6 20 156

OW E 3 3,5 11,2 1 3 8,2 0,5 20 82

OW N 2 3,5 6,3 1 6,3 0,5 20 63

OW S 2 3,5 6,3 1 6,3 0,5 20 63

OW E 1 3,5 3,325 1 3,325 0,5 20 33

OW E 1 3,5 3,325 1 3,325 0,5 20 33

DGW S 3 2 6 1 6 2,6 20 312

OW S 6 3,5 22,4 1 6 16,4 0,5 20 164

İW W 4 3,5 14,7 1 14,7 1,61 5 118

C 43,5 0,7 20 609

1633 0,1 0 -0,05 1,02 1666

Qs = ( 1 / 4 ) ∑ ( a x l ) x R x H x ∆T x Ze

Qs = ( 1 / 4 ) x 2 x 27,9 x 1 x 2,4 x 20 x 1,2 633

2299

Qs x 3600

n =

( c x ρ x Vroom x ∆T )

633 x 3600

n =

( 1005 x 1,2 x 104 x 20 ) = 0,908

TOTAL HEAT LOST = 11597

69

APPENDİX – 3

A. Heat Gains of the Rooms (Continuing)

70

A. Heat Gains of the Rooms (Continuing)

71

B.Total Heat Gains of the Building

TOTAL Time Sensible Latent Total

1 5381 820 6201

2 4835 820 5655

3 4359 820 5179

4 3902 820 4722

5 3680 820 4500

6 6077 820 6897

7 7763 820 8583

8 10317 1732 12049

9 11232 1732 12964

10 11804 1732 13536

11 11901 1732 13633

12 12072 1732 13804

13 13338 1732 15070

14 14927 1732 16659

15 15934 1732 17666

16 16324 1732 18056

17 15764 1732 17496

18 12897 1732 14629

19 9479 1732 11211

20 8527 1732 10259

21 8060 1732 9792

22 7737 1732 9469

23 7446 1732 9178

24 7179 1732 8911

72

C. Pressure Loss Table in Pipes for 20 0C Temperature Difference

73

C. Pressure Loss Table in Pipes for 20 0C Temperature Difference (Continuing)

74

APPENDİX – 4

A. Features of the Chosen Heat Pump

Vitocal 300 Type BW 220 Vitocal 300 Type BW 226

Capacity Values Electrical Datum

Heating Capacity kW 21 ,6 Heat pump

Operating Point B0 / W35 *1 Voltage 400V-50 Hz

Suitable to EN 255 standard Maximum Voltage A 15, 8

Cooling Capacity kW 16, 8 Current 30 *2

Electric Power kW 4, 8 (for every compressor)

COP 4, 49 Current A 51, 0

Antifreeze Side (primer cycle) (for every compressor)

Volume Liter 7,4 (rotor bloke)

Flow rate Liter / h 5400 Fuse A 3 x 20

Flow resistance mbar 110

Maximum inlet temperature 0C 25 Control current

Minimum inlet temperature 0C -5 Current 230V-50 Hz

Warm Water Side(secondary cycle) Fuse A 6, 3

Volume Liter 5, 4 Cooling Period

Flow rate Liter / h 1900 Cooing fluid R 407C

Flow resistance mbar 100 Fill amount kg 2 x 2, 6

Maximum output water temperature 0C 55 Compressor Type

Dimensions Connections

Total length mm 727 Primer output and input R(i) 1 ¼

Total width mm 760

Installation output and input R(i) 1

Total height mm 1270 Weight Kg 280

Maximum Pressure

Heating period (primer) bar 4

Heating period (secondary) bar 4

*1Operating Point: B0 = Antifreeze inlet temperature 0 0C / W35 = Heating water

outlet temperature 35 0C *2First motion must limit the voltage

75

B. Capacity Diagram of the Heat Pump

1510-5 50

0

5

10

15

20

25

30

35

C

BA Heating Capacity

Cooling Capacity

Electric Power

C

B

A

Cap

acity (

kW

)

Temperature (°C)

40

3 7

THV=35 0C

THV=45 0C

THV=55 0C

THV=35 0C

THV=45 0C

THV=55 0C

THV=55 0C

THV=45 0C

THV=35 0C

76

C. Performance Diagram of the Heat Pump

7

4

5

6

3

2

1

0 5-5 10 15

Temperature (°C)

CO

P

THV=35 0C

THV=45 0C

THV=55 0C

77

APPENDİX – 5

A Pipe Diameter Calculation Table

Page Pipe Diameter Calculation Table

Floor a b c d e f g h ı k l m n o p q r S

According to Approximate Pipe Diameter According to Changed Pipe Diameter

Different

Pip

e P

arts

Hea

t A

mou

nt

Heat Flow for the 50C Temperature Different

Len

gth

d W R LR Σζ Z d W R LR Σζ Z LR Z

Num. W W m m/s mmWC mmWC 34~45 796,5 3186 10,2 1/2" 0,2 4,6 47 12,8 25,6 33~36 1593 6372 8,1 1/2" 0,41 16,3 132 5,9 54,15 32~37 2023 8092 5,3 3/4" 0,29 5,9 31 5,9 24,82 31~38 2502 10008 28 3/4" 0,35 8,4 235 10,3 63,15 1~14 11597 46388 4,2 1¼" 0,55 10,9 46 9,5 142,5

491 310 491 + 310 = 801

39~40 925 3700 1 1/2" 0,24 6 6 9,4 27

6~9 1850 7400 8 3/4" 0,25 4,8 38 5,9 18,4 5~10 2409 9636 5,4 3/4" 0,33 7,8 42 5,1 28,2 4~11 3153 12612 14 3/4" 0,43 12,7 178 4,7 43,2 3~12 4223 16892 9,6 1" 0,37 7,3 70 4,7 32,6 2~13 7104 28416 5,2 1¼" 0,35 4,4 23 6 37,87 1~14 11597 46388 4,2 1¼" 0,55 10,9 46 9,5 142,5

403 330 403 + 330 = 733

41~42 1848 559 2236 1 3/8" 0,24 8,2 8 9,4 5~10 5181 2409 9636 5,4 3/4" 0,33 7,8 42 5,1 4~11 7228 3153 12612 14 3/4" 0,43 12,7 178 4,7 3~12 7941 4223 16892 9,6 1" 0,37 7,3 70 4,7 2~13 12881 7104 28416 5,2 1¼" 0,35 4,4 23 6 1~14 22391 11597 46388 4,2 1¼" 0,55 10,9 46 9,5

367 311 367 + 311 = 678

78

A Pipe Diameter Calculation Table (Continuing)

Page Pipe Diameter Calculation Table Floor

a b c d e f g h ı k l m n o p q r S According to Approximate Pipe Diameter According to Changed Pipe

Diameter Different

Pip

e P

arts

Hea

t A

mou

nt Heat Flow

for the 50C Temperature Different

Len

gth


No W W m m/s mmWC mmWC

7~8 925 3700 12,6 1/2" 0,24 6 76 11,8 33,9 6~9 1850 7400 8 3/4" 0,25 4,8 38 5,9 18,4

5~10 2409 9636 5,4 3/4" 0,33 7,8 42 5,1 28,2 4~11 3153 12612 14 3/4" 0,43 12,7 178 4,7 43,2 3~12 4223 16892 9,6 1" 0,37 7,3 70 4,7 32,6 2~13 7104 28416 5,2 1¼" 0,35 4,4 23 6 37,87 1~14 11597 46388 4,2 1¼" 0,55 10,9 46 9,5 142,5

473 337 473 + 337 = 810

18~19 1149,5 4598 11,6 1/2" 0,32 8,9 103 12,8 91,4 17~20 2299 9196 11,3 3/4" 0,32 7,1 80 5,9 30 16~21 2653 10612 5,3 3/4" 0,37 9,3 49 5,1 34,92 15~22 2881 11524 28 3/4" 0,39 10,8 302 5,1 38,75 2~13 7104 28416 5,2 1¼" 0,35 4,4 23 6 37,87 1~14 11597 46388 4,2 1¼" 0,55 10,9 46 9,5 142,5

603 375 603 + 375 = 978

26~27 497,75 1991 7,5 3/8" 0,21 6,7 50 11,4 25,15 25~28 995,5 3982 9 1/2" 0,25 6,8 61 5,9 18 24~29 1493,25 5973 6 1/2" 0,38 14,4 86 5,1 36,7 23~30 1991 7964 10,8 3/4" 0,28 5,5 59 10,3 40,2 1~14 11597 46388 4,2 1¼" 0,55 10,9 46 9,5 142,5

302 263 302 + 263 = 565

79



a b c d e f g h ı k l m n o p q r S According to Approximate Pipe

Diameter According to Changed Pipe

Diameter Different

Pip

e P

arts

Hea

t Am

ount


Len

gth


43~44 744 2976 1 3/8" 0,32 13,9 14 9,4 48 4~11 3153 12612 14 3/4" 0,43 12,7 178 4,7 43,2

3~12 4223 16892 9,6 1" 0,37 7,3 70 4,7 32,6 2~13 7104 28416 5,2 1¼" 0,35 4,4 23 6 37,87

1~14 11597 46388 4,2 1¼" 0,55 10,9 46 9,5 142,5

331 304 331 + 304 = 635

45~46 1070 4280 1 3/4" 0,28 7,8 8 9,4 36,6

3~12 4223 16892 9,6 1" 0,37 7,3 70 4,7 32,6

2~13 7104 28416 5,2 1¼" 0,35 4,4 23 6 37,87 1~14 11597 46388 4,2 1¼" 0,55 10,9 46 9,5 142,5

147 250

147 + 250 = 397

51~52 1149,5 4598 1 1/2" 0,32 8,9 14 9,4 48

17~20 2299 9196 11,3 3/4" 0,32 7,1 80 5,9 30 16~21 2653 10612 5,3 3/4" 0,37 9,3 49 5,9 34,92

15~22 2881 11524 28 3/4" 0,39 10,8 302 5,1 38,75 2~13 7104 28416 5,2 1¼" 0,35 4,4 23 6 37,87

1~14 11597 46388 4,2 1¼" 0,55 10,9 46 9,5 142,5

514 332 514 + 332 = 846

80



a b c d e f g h ı k l m n o p q r S


Different

Pip

e P

arts

Hea

t A

mou

nt


Len

gth d W R LR Σζ Z d W R LR Σζ Z LR Z

Num. W W m m/s mmWC mmWC

49~50 354 1416 1 3/8" 0,15 3,6 4 10 11,1

16~21 2653 10612 5,3 3/4" 0,37 9,3 49 5,9 34,92

15~22 2881 11524 28 3/4" 0,39 10,8 302 5,1 38,75

2~13 7104 28416 5,2 1¼" 0,35 4,4 23 6 37,87

1~14 11597 46388 4,2 1¼" 0,55 10,9 46 9,5 142,5

424 265

424 + 265 = 689

47~48 228 912 1 1/2" 0,27 7,8 8 10 36,25

15~22 2881 11524 28 3/4" 0,39 10,8 302 5,1 38,75

2~13 7104 28416 5,2 1¼" 0,35 4,4 23 6 37,87

1~14 11597 46388 4,2 1¼" 0,55 10,9 46 9,5 142,5

379 255

379 + 255 = 634

53~54 497,75 1991 1 3/8" 0,21 6,7 7 10 22

25~28 995,5 3982 8 1/2" 0,25 6,8 54 5,9 18

24~29 1493,25 5973 4,4 1/2" 0,38 14,4 63 5,1 36,7

23~30 1191 4764 28 3/4" 0,28 5,5 154 10,3 40,2

1~14 11597 46388 2,6 1¼" 0,55 10,9 28 5,9 142,5

306 259

306 + 259 = 565

81





Different

Pip

e P

arts

Hea

t Am

ount


Len



55~56 497,75 1991 1 3/8" 0,21 6,7 7 10 22

24~29 1493,25 5973 4,4 1/2" 0,38 14,4 63 5,1 36,7

23~30 1191 4764 28 3/4" 0,28 5,5 154 10,3 40,2

1~14 11597 46388 2,6 1¼" 0,55 10,9 28 5,9 142,5

252 241

252 + 241 = 493

57~58 497,75 1991 1 3/8" 0,21 6,7 7 10 22

23~30 1191 4764 28 3/4" 0,28 5,5 154 10,3 40,2

1~14 11597 46388 2,6 1¼" 0,55 10,9 28 5,9 142,5

189 205

189 + 205 = 394

63~64 796,5 3186 1 1/2" 0,21 4,6 5 12,8 28,3

33~36 1593 6372 9 1/2" 0,41 16,3 147 5,9 54,15

32~37 2072 8288 3,9 3/4" 0,29 5,9 23 5,1 24,82

31~38 2502 10008 7 3/4" 0,35 8,4 59 10,3 63,15

1~14 11597 46388 2,6 1¼" 0,55 10,9 28 5,9 142,5

262 313

262 + 313 = 575

82





Different

Pip

e P

arts

Hea

t A

mou

nt


Len



61~62 430 1720 1 3/8" 0,18 5,1 5 10 16,1

32~37 2072 8288 3,9 3/4" 0,29 5,9 23 5,1 24,82

31~38 2502 10008 7 3/4" 0,35 8,4 59 10,3 63,15

1~14 11597 46388 2,6 1¼" 0,55 10,9 28 5,9 142,5

115 247

115 + 247 = 362

59~60 479 1916 1 3/8" 0,2 6,1 6 10 20

31~38 2502 10008 7 3/4" 0,35 8,4 59 10,3 63,15

1~14 11597 46388 2,6 1¼" 0,55 10,9 28 5,9 142,5

93 226

93 + 226 = 319

83

B. Local Loss Coefficient Calculation Form

ζ ζ ζ ζ VALUES CALCULATION FORM

1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22

Tro

users

Part

S P

art

Double

Bend(L

arg

e)

Double

Bend(T

ight)

T U

nio

n

T S

epara

tion

Opposite C

urr

ent

Passin

g(S

epara

tion)

Inle

t(S

epara

tion)

Pip

e D

iam

ete

rs

Bend 9

00

Bend

Valv

e

Colu

mn V

alv

e

Colu

mn V

alv

e(inclin

ed)

Radia

tor

Sto

pcock(s

mooth

)

Radia

tor

Sto

pcock(c

orn

er)

1/2" 1,5 2 1,1 17 3 6,5 5

3/4" 1,1 2 0,6 13 3 6 3

1" 0,9 1 0,5 12 3 6 2

1 1/4" 0,5 1 0,4 10 2,5 5 2

Boile

r or

Radia

tor

Colle

cto

r In

let or

Outlet

1 1/2" 0,4 1 0,3 8 2,5 - -

Part

Num

ber

Pip

e D

iam

ete

r

3 0,5 1,6 0,5 1 2 1 1,5 3 0,5 1 2" 0,5 1 0,3 7 2 - -

TO

TA

L

1 α 14 2" 3 0,5 6 9,5

2 α 13 1 1/4" 6 6

3 α 12 1 1/4" 1 1,5 2 4,7

4 α 11 1 1/4" 1 1,5 2 4,7

5 α 10 1" 1 1,5 3 5,1

6 α 9 3/4" 1 1,5 3 5,9

7 α 8 3/4" 3 7 3 13

15 α 22 1" 1 1,5 3 5,1

16 α 21 3/4" 1 1,5 3 5,9

17 α 20 3/4" 1 1,5 3 5,9

18 α 19 3/4" 3 7 3 13

23 α 30 1" 1 1,5 8 10

24 α 29 1" 1 1,5 3 5,1

25 α 28 3/4" 1 1,5 3 5,9

26 α 27 1/2" 3 8 3 14

31 α 38 1" 1 1,5 8 10

32 α 37 1" 1 1,5 3 5,9

33 α 36 3/4" 1 1,5 3 5,9

34 α 35 1/2" 3 8 3 14

39 α 40 1/2" 3 6 9,4

41 α 42 1/2" 4 6 10

43 α 44 1/2" 4 6 10

45 α 46 1/2" 4 6 10

47 α 48 1/2" 4 6 10

49 α 50 1/2" 4 6 10

51 α 52 1/2" 4 6 10

53 α 54 1/2" 4 6 10

55 α 56 1/2" 4 6 10

57 α 58 1/2" 4 6 10

59 α 60 1/2" 4 6 10

61 α 62 1/2" 4 6 10

63 α 64 1/2" 4 6 10

84

APPENDİX -6

A. The Sizes and Thermal Resistances for 1 Meter Length of the Polyethylene

and Polybuthilen Pipes (m0C /W)

B. Model Building Picture

Rp (Horizontal) / Rp (Vertical)

Pipe Diameter PE SCH-40 PE SDR-11 PB SDR-17 PB SDR-13.5

0.098 0.083 0.092 0.116 3/4"

0.067 0.055 0.064 0.081

0.09 0.083 0.092 0.116 1”

0.063 0.055 0.064 0.081

0.075 0.083 0.092 0.116 1 1/4”

0.051 0.055 0.064 0.081

0.068 0.083 0.092 0.116 1 1/2”

0.046 0.055 0.064 0.081

0.057 0.083 0.092 0.116 2”

0.039 0.055 0.064 0.081

85

C. Fan Coil and Heat Exchanger Pictures of the Model Building

Çukurova university institute of natural and applied ... · yapılarak fan-coil ve ısı pompası...

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