Литература
1.
Болонский процесс.Гарантия качества образования: Сборник документов/Под ред.Г.Н.Мотовой,
В.Г.Наводнова, .Ж.Шахановой- Москва-Астана: Нац.аккредитационное агенство в сфере
образования РФ, Нац. Аккредитационный центр МОН РК,2008,-том 2-136 с.
2.
Болонский процесс: результаты обучения и компетентностный подход /Под науч.ред.д-ра пед.
Наук,профессора
В.И.Байденко,-сследовательский
центр
проблем
качества
подготовки
специалистов,Независимое казахстанское агенство по обеспечению качества в образовании
(НКАОКО)-2010.-536с.
252
THE SAMPLE OF HEAT PUMP APPLICATION IN ANTALYA
Ahmet ÇOŞGUN
1
, Cemal OKUYAN
2
1
Akdeniz Üniversity, Antalya-Turkey. acoskun@akdeniz.edu.tr
2
Balıkesir Üniversity, Balikesir- Turkey. cokuyan@balikesir.edu.tr
ABSTRACT
In this study, an application of heat pump originating from aqua-air in Isısan showroom existing in Antalya
and some experiments with R514 type heat pump devices existing in air conditioning-cooling lab in Akdeniz
University Technical Sciences Vocational High School have been carried out. In both devices in variable conditions
water discharge entering into condenser on R514 type testing machine has been considered as 10-50 gr/h variable
and accordingly it is observed that the real heating factor of action differ 2,25-7,4 values. On the other hand, the
heating factor of action in theoretical state have been calculated and the correlation between them have been
examined. Besides this, in LHK-10 type heat pump originating from aqua-air in Antalya Isısan Showroom and the
application is completed, temperature rating entering into condenser has been changed between 16 and 32 °C and
the heating and cooling factor of action(for both theoretical and real occasions) affecting the heat pump have been
calculated. The experimental and the practical results getting from two different places have been analyzed
respectively.
РЕЗЮМЕ
В данном исследовании рассмотрено применение тепловых насосов типа аква-воздух, установленных
в салоне Isisan, в Анталии и некоторые эксперименты, проведенные с устройством теплового насоса типа
R514 в кондиционерах для охлаждения лабораторий в профессионально-технической школе университета
технических наук Акдениз В обоих устройствах с различными условиями сброса воды, находящейся в
конденсаторе испытательные машины типа R514 переменная составляла 10-50 гр / ч и, следовательно,
реальный фактор действия отопления различался на 2,25-7,4 значения. С другой стороны, были
рассчитаны факторы, влияющие на систему отопления в теоретическом состоянии и рассмотрена
корреляция между ними. Кроме того, были рассчитаны факторы процессов нагревания и охлаждения (как
для теории, так и в практических случаях), влияющие на действие тепловых насосовы типа ЛХК-10,
работающих по принципу аква-воздух в Isisan Showroom Анталии при изменении температуры
компонентов конденсатора с 16 до 32 °С. Были проанализированы экспериментальные и практические
результаты, полученные в двух случаях соответственно.
1. INTRODUCTION
For the purpose of partially reduce the disadvantages brought by the energy crisis that gained
importance world wide as well as in Turkey in this century; it is necessary to develop and practically use
thermal systems that will reduce the thermal energy to minimum level. Heat pumps can be shown as a sample
to this systems [1].
In the very simple expression, Heat Pumps are thermodynamic systems that are transferring low
temperature from a resource to a resource with higher temperature. Heat pumps are working on a base by
water, air or other fluids heating and ejaculating the high temperature from the condenser. The main purpose
of this is to obtain hot water or air for heating, drying and similar actions. Aqua-Air heat pumps means a heat
pump that is obtaining hot water by absorbing the heat from the air. It is also possible to avail the energy
discharged by the heat pumps. However, it is not always possible to use the heat pumps everywhere.
Especially regarded to the discharged heat energy, taking in consideration the size in W, the temperature,
regaining ways, the cold environment where the heat is absorbed from, constructive specifications, the
physical and chemical characteristics of the discharged fluid, etc that will be used, it is necessary to do a
versatile analyze. Sometimes, heating pumps are the best solution when both, heating and cooling required
places is requested. As an example to this, drying plants, sporting complexes and places like food and
industrial plants where bi-directional applications are used can be mentioned [2].
The interest in heat pumps increased after the Energy crisis in year 1973, and in 1976, 300.000 unites
of heat pumps have been manufactured. Till the end of 1978 the manufactured heat pump total amount in
America was more than 2.000.000 pieces. 25 % of the buildings established after the year of 1978 have been
planed and applied as to be heated with the heating pumps. Nowadays in worlds developed countries, like
America, Canada, Germany, Switzerland, etc., heat pumps are being used widely in housing as well as
industrial fields [3].
In this study, experiments were based on R514 Type aqua-air heat pump devices current in Air
Conditioning Cooling Laboratory of Vocational Technical Sciences High school of Akdeniz University and in
Isısan Showroom building in Antalya. For both devices used in the experiments various conditions were
applied; for R514 experimental device the water flow between 10-50 gr/sec trough the condenser was taken as
253
the variable. In this study the variation of heat efficiency coefficient depending on the water flow was tried to
be determined.
On the other hand, in the experimental study done with the LHK-10 type aqua-air soured heat pump
current in Isısan Showroom Building; the variation of water temperature entering the condenser between 16-
32°C was taken as parameter, and according to that the operatic and theoretical cooling and heating effective
coefficient were computed. The aim of this study was to analyze the both experimental results with
engineering methods and to provide benefits in their practical use to applicants and engineers.
2. MATERIAL – METHOD
The efficiency of the heat pumps is showing big differences according to the temperature of the external
environments where the energy is pumped. On the other hand the confort conditions requested from people
during the winter and summer moths are remaining the same. It is around +/- 24°C. The warm water
temperature used for shower/bath and similar application remain, s for both summer and winter months,
around 45°C. In case that the heating necessity reaches the maximum, this indicated that the exterior
temperature has reached the minimum[4].
As known I the II.Law of Thermodynamics, the heat transmission a colder heating source to a hotter
environment can only occur when the second energy source energy is thermal or mechanic and the
transmission from the cold heat device to the hot environment can occur in various ways. Accordingly the heat
pump types can be ranged as follows: vapor pressed circular heat pump, absorption heat pump, absorption heat
pump, gas circular heat pump, jet steam circular heat pump, Stirling circulated heat pump, resorption heat
pump, Rankine/ vapor pressed circular heat pump and Thermo electrical heat pump.
2.1. Thermodynamically Heat pumps: Although Carnot cycle is nonexisted it is a totally reversible
cycle. Therefore it is used in the comparison of power cycles. Carnot cycle is, in given temperature range the
highest heating exothermic cycle. It is also possible that change of states in Car not cycle, the heat and working
transaction reverse. This I called the reversed Carnot cycle. Heat pump and cooling machines are working
according to the reverse Carnot cyle [5].
In heat pumps, the cooler heat is taken and this mentioned heat is by the refrigerant fluid transmitted to
heat source, transformed to elevated temperature. As refrigerant in vapor pressed circular liquid steam is used.
A heat pump is consisted of four main parts: 1- Evaporator, 2- Condenser, 3 – Expansion valve, 4 –
Compressor [6].
2.2. Different sourced Heat Pumps: The low energy in heat pumps is obtained free of charge from
different natural resources. During obtaining this energy neither the source temperature changed nor negative
effects are added to the environmental conditions. The application can be grouped as follows [7]:
In heat pump systems the environment that the evaporator is absorbing the energy is called the heat
source. For using this energy source, which is very important for the heat pump, efficient in the system
depends on the below mentioned conditions.
1 – to posses high resolute hat during the heating season, 2 – to be easy to find, 3 – not to have corrosive
and pollutant effects, 4 – to have appropriate thermo physical characteristics, 5 – to have low investment cost
for reaching the source.
2.3.The Thermodynamically Comparison of Power Machines and Heating Pumps
Picture 1. The Carnot cycles of a powe machine and heat pump.[2].
As it can be seen n the Picture 1, the Carnot cycle in te power machines are:
Q
C
: is given heat (evaporation), W
: is received energy (Exergy), Q
OC
: is anenergia.
Q
C
= W + Q
OC
As is known the usable part of energy is the Exergy. The non usable energy is named as anenergia.
Regarding to this, the relation between Exergy and anenergia can be shown as:
Energy = Exergy + anenergia
(1)
Along the cycle:
η
c
=
T
T
T
0
= 1-
T
T
0
with this expression the Carnot efficiency is determined.
(2)
Also W = Q
C
* η
c
In case of heat pumps it is like:
Exhaust heat = Given energy + received energy
(3)
254
Heat Effect Coefficient HEC (IEK) is like [2]:
IEK
=
W
Q
C
=
0
T
T
T
The experimental pump used in this study is a direct expansion pump, therefore it s possible to draw
an InP-h diagram as shown below on picture 2.
Picture 2. The ln P-h diagram (presenting a single-stage systems with and without heat exchanger).
Reversible Carnot cooling cycle consist from two constant temperature and their operational procedure,
total four thermodynamic operation (picture 2). In the diagram the 1-2-3-4 operations are reversible. The
Carnot cycle, is not reversible to 1
‘
-2
‘
-3
‘
-4
‘
thermodynamic operations and shows the Carnot cycle. It is:
1-2: The adiabatic isentropic compression in the Compressor,
2-3: The constant pressure and temperature compression in the Condenser,
3-4: The isentropic extension of the Extension Valve, 4-1: the extension f the evaporator under constant
pressure and teperture. The 1-2 and 3-4 thermodynamic activities are based on transaction basis.
1-2: it is presenting the operation done over the working fluid with W
el
operation out of system borders
3-4: it is presenting the over border systems transferable operation in reversible and non reversible
systems.
To prevent the fluid from the intake line to run into the compressor during the application the system is
changed into heat exchanger. The heat exchanger transforms the coolant liquid at the entrance of the
compressor by overheating first into the steam faze, than the fluid at the exit condenser by overcooling into
overcooled and liquid faze[7].
In the reversible Carnot cycle, the entrance of the saturated vapor phase liquid into the compressor
under constant pressure is considered as the 1 point, after compression with adiabatic constant entropy the
transfer from the compressor to the condenser as the 2 point, the transformation under constant pressure in the
condenser from superheated steam into saturated steam phase still as the 2 point and entering the extension
valve in the phase of saturated liquid as the 3 point, after extending in the adiabatic entropy, the transfer from
the extension valve to the evaporator as the 4 point, by absorbing heat under constant pressure in the
evaporator the transformation to the saturated vapor and entrance to the compressor as the 1 point. If the mass
flow of the coolant fluid in the system is chosen as m
r
(kg/h) and the enthalpy as (kJ/h) than the capacity
evaluation can be calculated with the below mentioned equation,
W =m
r
(h
2
–h
1
)
(Compressor‘s compression activity ) (kJ/h)
(4)
Q
C
= m
r
(h
2
–h
3,4
) (Condenser condensation capacity) ( kJ/h)
(5)
Q
0
= m
r
(h
4
–h
1
)
(Cooling load) (kJ/h)
(6)
3. EXPERIMENT PERFORMING AND INTERPRETING THE FINDINGS
3.1. Experimental Study carried out in the Akdeniz University Laboratory (Group I: GI)
Photographs from a R514 aqua/air mechanical heat pump current in Air-conditioning – Cooling
Laboratory, Technical Sciences
Vocational High
School, Mediterranean University are shown on picture 3‘ a
and b. Exploded view of the Mechanical heat pup device used in experiment of GI picture 4‘(c)
(a)
(b)
(c)
Picture 3. Heat pump belonging to a Laboratory device (a): general view, (b): Coactionel,
condenser with pipes and water,
Picture 4. Exploded view of the Mechanical heat pup device used in experiment of GI (c) [8,10].
255
3.1.2. GI Experimental Device’s Specifications:
GI experimental heat pump device consists from: 1 piece of, 1/3 HP hermetic type compressor, 1 piece
of, 1/3 type air cooler evaporator, 1 piece of, water condenser with interpenetrated (coaxsionel) pipes, 1 piece
of, R134 gas measuring flow meter, 1 piece of rout meter type flow meter which is measuring the water flow
(kg/sec) circulated in the condenser, 1 piece of, annular balanced thermostatic extension valve, 1 piece of filter
(dryer), 1 piece of pressure manometers showing low and high pressures, 1 piece of, pressure automatic and 1
piece of, condenser fan from power of, 40W. Also one Wattmeter (it is measuring the system‘s total
consumption of electrical energy as (Watt/sec), 8 pieces of temperature measuring sensors (trough this sensors
the results of measurements are transferred to the Regulator switch indicator), one of each, water input and
water output (drainage) lines are existing. In order not to be effected by the ambient conditions the temperature
measuring sensors were isolated with polyurethane material during the 8 digital temperature measurements
[8,9].
The temperature points taken from the GI device were respectively as follows; the coolant fluid‘s
compressor input (incoming) temperature (t
1
), the coolant fluid‘s compressor output (outgoing) temperature
(t
2
), the condenser condensation temperature (t
ky
),
the coolant fluid‘s condenser output (outgoing) temperature
(t
3
), the coolant fluid‘s evaporator input (incoming) temperature (t
4
), the coolant fluid‘s evaporation
temperature in the evaporator (t
eb
), the water input (incoming) temperature into the condenser (t
5
), the water
output (outgoing) temperature from the condenser (t
6
), and the ambient temperature (t
7
).
During the estimation, the air/aqua heat pump was activated and operated idle without load for one hour
time. Later on for evaluation the elapsed periods for the determined load taken from the Wattmeter (each 0,5
kW from the total consumed electrical energy) were estimated with a chronometer. R134a was used as the
coolant fluid. The estimation results are shown in the sheet 1 mentioned below.
Sheet 1. GI Experiments and evaluation results of the heat pump
Evaluation Parameters
1.
Evaluation
2.
Evaluation
3.
Evaluation
4.
Evaluation
5.
Evaluation
6.
Evaluation
m
su
(gr/sec)
50
40
30
20
10
4
m
r
(134 a gas, gr/sec)
6
6
6
6
6
7
P
k
(High-pressure side, bar )
6
6,45
7
7,9
10,8
13,9
P
e
(Low-pressure side, bar)
2,75
2,92
3
3,18
3,22
3,40
t
ky
(Condenser condensation Temp.
°C)
28
30
32
34
43
55
t
eb
(Evaporator evaporation temp.,
°C)
6
7
8
9
9
11
t
1
(Compressor income temp., °C)
16,6
13
10
7,5
8,5
9,6
Overheating (°C)
-10,6
- 6
- 2
1,5
0,5
1,4
t
2
(Compressor outcome temp., °C)
51,6
54,1
52,9
53,4
57,3
61,8
t
3
(Condenser outcome temp., °C)
23,3
24,6
22,7
32,3
42,2
54
t
4
(Evaporator income temp., °C)
8,9
9,6
10,8
11,4
12,0
13,1
t
5
(Mains water income temp., °C)
18,6
18,7
19,1
19,3
20,3
22,6
t
6
(Condenser/evap. water outcome
temp., °C)
24,3
26
29,2
34,3
45,3
55,1
t
7
(Ambient Temperature, °C)
20
20
20
20
20
20
Device‘s operating time (min)
(for 0,5 kW/h)
10,10
9,56
9,28
9,02
8,06
6,42
Q
k
=m
su
x Cp
su
x (t
5-
t
6
)
(Kondenserden suya verilen ısı W)
1191,3
1220,5
1266,5
1254
1045
543,4
W
el
=m
r
x (h
2
-h
1
)
(The action shared on Working fluid,
W)
150
192
240
242
240
241
IEK
g
=Q
k
/Wel
(real heat effect coefficient )
7,4
6,3
5,2
5,18
4,35
2,25
IEK
t
=T
ky
/(T
ky
- T
b
)
(theoretical heat effect coefficient )
13,68
13,17
12,7
12,28
9,29
7.45
256
Picture 5
Picture 6
Picture 5. The temperature differences appeared by using variable water flows for GI.
Picture 6. The effect of the variable water flow to IEK in GI (IEK
g
= real heating effect coefficient,
IEK
t
=Theoretical heating effect coefficient)
3.2. The experimental Activities in Antalya Isısan Showroom Building (Group II: GII)
3.2.1.The Characteristics of the Isısan Showroom Building in Antalya:
The Isısan Company showroom building in Antalya consists of a basement, ground floor an one normal floor.
The ground floor has a clerestory. This buildings heating – cooling activities are fulfilled with an Aqua / air
heat pump with additional Water VRV system (picture 7). For this one external unite from 10 BG power and
in accordance to the gaining heat and losses calculation 8 system connected internal unites with appropriate
volumes were placed. Three internal unites of 36000 BTU, 48000 BTU and 60000 BTU were placed in the
same location where de current heat pump is placed.
Sheet 2. GII aqua / water pump evaluation results
Evaluation Parameters
The values taken when the device
is operating (heating)
The values taken when the
device is operating (cooling)
Numbers of Evaluation
1.E
2.E
3.E
4.E
1.E
2.E
3.E
4.E
Pe (evaporator pressure, bar)
9,6
10,8
11,5
11,7
8,1
7,8
7,9
9
Pk (Condenser pressure, bar)
20,4
21,5
24,2
27,8
24
25,1
26
27,2
t
eb
(Pe equal evaporation temperature,
°C)
6
8
12
13
1
0
0
4
t
ky
(Pk equal condensation temperture,
°C)
33
36
40
46
40
41
43
45
m
r
(410A gas, gr/sec)
400
400
400
400
400
400
400
400
t
1
(compressor income temperature, °C)
16
16,7
17,2
19,1
8,5
9,2
9,7
9,9
t
2
(compressor outgoing temperature, °C) 41,8
41,7
42
41,6
62,7
62,8
62,9
62
t
3
(condenser outgoing temperature, °C)
32,9
33
32,8
33,2
11,2
10,7
11,1
12
t
5
(mains water income temperature, °C)
16
21
27
32
16
21
27
32
t
6
(condenser/evap. Water output temp.,
°C)
32,8
31,1
30,6
30,9
12
16,2
23,1
25,1
t
7
(ambient temperture, °C)
20
20,7
20,4
21,1
20
20,3
20,4
20,6
m
su
(the circulated water flow in
cond./evap., m
3
/h )
2,5
2,5
2,5
2,5
2,5
2,5
2,5
2,5
Absorbed air (°C)
29,9
30
30,1
30,5
24,7
26,7
27,9
28,9
Blower air (°C)
41
40,8
41,4
41,6
9,8
10,1
12,5
11,9
257
Q
k
=m
su
Cp
su
(t
5-
t
6
) (the heat given to water
by the condenser, W)
37182 29317
9005
3195
----
----
----
-----
Q
e
=m
su
Cp
su
(t
5-
t
6)
(the heat given to the
water by evaporator, W )
------
------
------
------
11619
1394
3
11328 20043
W
el
=m
r
(h
2
-h
1
)
(The action shared on Working fluid, W )
8800
6800
7200
8000
12000
1400
0
12000 12800
IEK
g
=Q
k
/Wel (Heating effect coefficient)
4,2
4,3
1,25
0,39
---
---
---
---
IEK
t
= T
ky
/(T
ky
- T
b
)
11,33
11,03
11,17
9,66
---
---
---
---
SEK
g
=Q
e
/W
el
(Cooling effect coefficient)
---
---
---
---
0,96
0.99
1,05
1,56
SEK
t
= T
b/
(T
ky
- T
b
)
---
---
---
---
7,02
6,65
6,34
6,75
y
= -0.24x
2
- 0.248x + 4.955
R
2
= 0.8826
y = -0.3025x
2
+ 1.0255x + 10.502
R
2
= 0.8766
0
2
4
6
8
10
12
16
21
27
32
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