Category Archives: EuroSun2004

EXPERIMENTAL EQUIPMENT

The hybrid system consisted of a PV module, where a glass plate window (jacket) was layed over the front surface, a circulating pump and a heat exchanger. The glass plate was temporarily attached and could be removed at any time without much effort. A fluid, distilled water, was circulated between the front surface of the PV module and the jacket layed on the front surface.

The incident solar radiation first passed through the glass jacket and the layer of circulating water before reaching the module. The high transmittance of glass and water layers for the visible radiation, ensured that the silicone cells of the PV module would receive most of the visible radiation to generate electricity without much sacrifice in power. Infra-red part of the incident radiation is essentially absorbed by the glass-water and module structure combination leading to warming of the solar cells. It is this excess heat that the hybrid unit is designed to remove, by circulating water, and utilize in domestic applications. While the circulating water removes the heat and leads to cooling of the module, at the same time it provides a source of warmed water for preheating applications in a domestic use.

A standard commercial module, M, rated at 55 Watt peak, with dimensions 130x47x5 cm was used. The jacket, J, had the diamensions of 130x47x1.5 cm (Fig. 4) and was placed over the module surface with a gap, about 0.4 cm to allow flow of water. The PV module was tilted 45 degrees to horizontal and faced south for maximum solar insolation, I. Initially pure water, Q, was circulated at the rate of 36 liters per hour. An identical PV module was used as a control and measurements were performed on both the hybrid and the control modules at the same time and location.

A data acquisition card was used to record a range of data. Meteorological information published by the Statistics office[1] was used. The electrical characteristics of both modules and thermal performance of the hybrid system were measured. The data listed below were recorded at various times from 9.00-17.00 hrs. each day and the average values were plotted. The temperature of the circulated water, at input/output Tin, Tout, the ambient temperature, Tamb, and surface temperatures, Tsc, Tsh, on the control and hybrid modules respectively were recorded. All temperatures were recorded in degrees centigrade. The short-circuit currents, Iscc, Isch and open-circuit voltages, Voc, Voh of both control and hybrid modules respectively were recorded. The maximum operating power of each module is defined as P = Voc Iscc FF (1)

The fill factor, FF, was taken as 0.7, which is typical of single crystal silicone cells.

The electrical energy, Ec and Eh, of control and hybrid module respectively were calculated using numerical integration. Hence, the area under the power-time curve, was taken at various one-hour periods.

Thermal energy collected by the circulating water in one-hour period, can be defined as Qw = Q Cp AT (2)

where Q is the volune flow rate of the water in lt/hr, Cp is the specific heat at constant pressure (4187J/kg. °C), and AT is the temperature difference (Tout — Tin ).

Temperature distributions according to the different tank models

The obstacle types, have supplied higher thermal stratification, have been determined numerically by using computer simulation. In this situation, the aim is supply hot water as long times as possible with high thermal stratification between the temperatures T4 (cold water enter to the tank from main lines) and T2 (hot water supplied by solar collector). Different kinds of obstacle as in figure 3 with different assembly as in figure 2 have been placed in the tank in order to obtain this higher thermal stratification. These obstacles are placed in the tank with suitable angles and coordinates to decrease contact area between cold and hot water in the tank. T4 flow fibers don’t have to destroy hot water gradient. However, the hot water entering the tank (T2) would destroy the stratification. Therefore, hot water velocity is taken as 0.2 m/s for forced circulation. The flow rate of the hot water from tank to usage must be equal to the cold water flow rate entering to the tank. Therefore, the cold water velocity is assumed as 1 m/s.

Vortexes have occurred in the tank because of the mixing of two different fluids. These two fluids would hit each other towards to the wall and obstacle surfaces. Therefore, calculations are carried out by using wall functions method and standard k — s turbulent models with FLUENT [10] code.

The cold water enters and exit pipes in radial direction are in the same axis as symmetrical condition. So, higher percentage of the cold water entering to the tank would be directed towards to cold water exit channel (T1) from the tank. At the end, the cold water can not produce a lot of vortex inside the tank and destroying effects into thermal stratification inside the tank would be decreased. The hot water exit channel (T3) is generally located at the top of the tank. So, the hot water can be supplied as long as possible because of the positions of the hot water exit channel.

NUMERICAL ANALYSIS OF THE EFFECT OF USING SOME. OBSTACLES INTO THERMAL STRATIFICATION IN HOT. WATER TANK WITH NATURAL CONVECTION

Necdet ALTUNTOP1, Mevlut ARSLAN1, Veysel OZCEYHAN1,

1 Dept. of Mechanical Engineering, Erciyes University, 38039 Kayseri, Turkey

Abstract

In this work, the numerical analysis of the effects of using different obstacles into the thermal stratifications in the cylindrical hot water storage tank has been presented. This kind of storage tank is widely used in heating systems by solar energy. The heat transfer is carried out by natural convections in the tank. The water is used as fluid. The Optimal shape and angle of the obstacle has been found to obtain higher thermal stratification as possible as between cold and hot water between 30 different obstacles. The natural convection effect into the temperature distribution inside the tank has also obtained for different obstacle types and angles. The temperatures of the water entering to the collector and from the collector and water exiting form the tank to usage have been presented into the graph. The temperature differences of these waters have also presented to determine thermal stratification according to the obstacle types and angles. The temperature distributions in the tank between with and without obstacle have been analyzed to compare to get high thermal stratification. At the conclusion, It is found that the obstacle type 11 has supplied the highest thermal stratification between all investigated cases.

Conclusions

The temperature distributions of the heat storage tank with different obstacles are calculated numerically and presented in z-r plane. Temperature distribution of the smooth tank is also presented. The results as follows;

Using the obstacles are improving the thermal stratification inside the tank compared to the smooth tank.

It can be observed that, the obstacle types have gap in the center, have better thermal stratification than obstacle types that have gap near the tank wall.

Obstacle types 7 and 11 have supplied hot water with higher degree to usage rather than other obstacles type and also rather than smooth tank. This is desirable case for thermal stratifications. Other obstacle types have little effect into the thermal stratifications in the tank. The smooth tank has also little thermal stratifications.

While the operation periods of time, the tank has obstacle type 11 has lower average value of temperature in the z=0.2 plane in radial direction than the tank has 7 type of obstacle. The reason of this case is that tank model has obstacle type 11 has cylindrical shaped obstacle in z=0.2. This obstacle prevents the destroying effect of the cold water into the thermal stratifications while the operation period of time increases. So, in tank 11, the temperature of the water going to the heater would decrease while the time period increases. This is also desired situation for heat storage tank in solar energy systems.

T3 has increased in tank 11 and T1 has decreased during the operation times. So, the difference between T3 and T1 would also increase. This is also desired criteria for thermal stratifications. With respect to these arguments, the tank has obstacle type 11 has best thermal stratification between all investigated cases.

The tank has obstacle has improved the solar collector efficiency as well as thermal stratifications. Because, T1 (water return to the solar collector) would decrease when the obstacle is used. So, the increase of the solar collector efficiency can be achieved.

Acknowledgement

The authors thank to the Erciyes University for FLUENT 6.1.22 code.

Theoretical Model

The cross-sectional view of the used model for numerical analysis is shown in Fig. 1.

Boundary layer equations were used to determine the temperature and velocity distributions in the flow field. The analysis was based on the unsteady, three-dimensional continuity, momentum and energy equations.

The assumptions are used as:

— The flow is unsteady, turbulent and three-dimensional,

— The thermal conductivity of the tube sheet material does not change with temperature

— The tube material is homogeneous and isotropic.

Three dimensional continuity, momentum and energy equations are solved numerically. The upwind and central difference method used for convections and diffusions, respectively [9].

The aim of using the obstacle is supplying hot water as long as possible in the upper part of the tank to usage. So, high thermal stratification would be achieved by using these obstacles to obtain higher degree of hot water from the tank. The obstacle’s schematic view is shown in figure 2. The details of these obstacle geometries are shown in figure 3. Table 1 indicates that the matches between obstacle type and tank.

d =0.02 m f1 = 0.04 m Vk=0.2 m/s

D= 1 m g = 0.2 m

f = 0.2 m Si = 0.2 m

The hot water entrance velocity is assumed as 0.2 as forced convective regions. The water temperatures are assumed 333, 320 and 285 K for water exit from the tank to usage, water in the tank and water coming from the main lines, respectively.

dl

1

T4

V

Figure 1 Cross-sectional view of the used tank model

Table 1 Obstacle types and tanks matches

Obstacle types

The obstacle placed tank models.

1

7,8

2

9,10

3

12

4

11

5

12

6

1,2,3,4,5,6

The dimensions of the obstacles in figure 3 are shown in Table 2.

Table 2 The dimensions of the obstacles

Obstacles number

a

S (m)

t (m)

r1 (m)

r2(m)

r3(m)

r4(m)

l (m)

r5

1

0.8

0.02

0.96

0.2

2

0.8

0.2

0.96

0.0

3

0.2

1.0

4

0.2

1.0

0.2

5

0.2

0.8

6

20o

0.02

0.8

2.1 Physical properties of fluid and boundary conditions

The thermodynamic properties of the water are considered in this study. The velocity and is assumed to be zero at the beginning. The operation pressure in the tank is taken1 atmosphere and the hot water temperature is assumed to be 320 K when the water usage started. The time between the water is started to be used and the water usage was finished is assumed as

calculation region. This time is taken as 30 minutes and the problem solved as unsteady.

Figure 3 The details of the obstacles in the tank.

INVESTIGATIONS OF THE SOLVIS STRATIFICATION. INLET PIPE FOR SOLAR TANKS

E. ANDERSEN, U. JORDAN, L. J. SHAH, S. FURBO Department of Civil Engineering, Technical University of Denmark Building 118, DK-2800 Kgs. Lyngby, Denmark Tel.: +45 4525 1901, Fax: +45 4593 1755, ean@byg. dtu. dk, uj@byg. dtu. dk, ljs@byg. dtu. dk, sf@byg. dtu. dk

Introduction

Since the 1960’ties the influence of the thermal stratification in hot water tanks on the thermal performance of solar heating systems has been studied intensively. It was found, that the thermal performance of a solar heating system is increasing for increasing thermal stratification in the hot water tank.

The temperature of the storage water heated by the solar collector loop usually varies strongly during the day. In order to reach a good thermal stratification in the tank, different types of pipes, plates, diffusers and other devices have been investigated in the past (e. g. Loehrke, 1979). The aim pursued was to transport the heated water into the tank level of corresponding temperature.

Flexible stratification pipes (manifolds) have been further developed for example by (Gari et al., 1982). Furthermore, a wide variety of non flexible tubes with either open holes and perforated vertical plates inside the pipes (Davidson, 1992) or openings in form of balls (e. g. Leibfried, 2000) or flaps (e. g. described in Krause, 2001) have entered the market during the recent years.

In this paper an investigation of a stratification pipe with openings covered with flaps according to (Krause, 2001) is presented. The flaps are constructed with a soft material which allows the flap to close and open depending on the temperature and pressure differences inside and outside the pipe. Figure 1 shows schematic

illustrations of the pipe. The total height of the pipe is 328 mm, the outer diameter 60 mm, and the flaps are located with a distance of 292 mm in vertical direction (distance between the centre of each opening).

Preliminary laboratory tests by (Shah, 2002) with the same stratification pipe containing 5 openings showed that thermal stratification was well built up for a volume flow rate smaller than 8 l/min and larger than 4 l/min, regardless of the inlet temperature, the temperature level in the tank, and the thermal stratification in the tank. For volume flow rates larger than 8 l/min, however, the number of open flaps increased, so that
water entered the tank at different levels instantaneously. For volume flow rates smaller than 4 l/min laboratory tests indicated that cold water could be sucked in through an opening in a low level due to low pressure differences. The cold water that entered the pipe through these openings from the bottom of the store mixed with the heated water that flew through the pipe and thereby induced mixing in the tank during charging.

More detailed investigations of the flow structure close to the flaps of the stratification pipe are presented in the following for one set of operating conditions. Temperature measurements were carried out and an optical method called Particle Image Velocimetry (PIV) was used to visualize the flow around the flaps.

Experiments

Experimental Set-up

The experimental set-up is shown in Fig. 2. The set-up consists of a rectangular glass tank with side lengths of 400 x 400 x 900 mm3, a heating and a cooling unit, and standard PIV equipment (Dantec Dynamics). The PIV equipment consists of a laser, a camera and a processing system for analysing the pictures taken by the camera. Information about the PIV equipment is given in Table 1.

Table 1. PIV equipment.

laser

type

energy/pulses

wavewlength

Nd:YAG, NewWave Solo (Neodym-Yttrium-Aluminium — Granat)

100 mJ/pulse

532 nm (frequency doubled)

CCD

type

HiSense 12 bit

camera

resolution

1280 x 1024 pixel (64 x 64 pixel interrogation area)

particles

Polyamid, 5pm (PSP-5)

software

Flowmanager, Dantec Dynamics

The camera is placed perpendicular to the laser that illuminates a thin slide in the flow.

The inlet consisting of three compound stratification inlet pipes placed in the centre of the tank. The inlet pipe is closed at the top. The outlet is placed in the bottom of the tank in the corner behind the inlet pipe. The temperature is measured in the middle of the pipe below each inlet and in 13 uniformly distributed levels in the tank. Also the in — and outlet temperatures are measured as well as the volume flow rate. The temperatures are measured with thermocouples type TT with an accuracy of 0.5 K. The volume flow rate is measured with an electro magnetic inductive flow meter, type HGQ1 from Brunata HG a/s. The flow meter has an accuracy of about ± 1 %.

The numerical method

CFD code is used to obtain velocity and temperature distributions inside the tank. Three dimensional unsteady solutions are taken by using implicit method in segregated solver. The discretization is achieved by using standard method for pressure and by using first upwind method for momentum, energy, turbulent kinetic energy and turbulent dissipation rate equations. The SIMPLE (semi-implicit method for pressure-linked equations) algorithm was used for flow calculations [10].

Te under-relaxation factors are assumed as 0.3, 0.7, 1, 0.8, 0.8 and 1 for pressure, momentum, energy equations, turbulent kinetic energy (k), turbulent dissipation rate (s) and turbulent viscosity (pt) as, respectively. This factor has assumed as 1 for body force and density.

The convergence factors are used as 10-3 for continuity, momentum, turbulent kinetic energy and turbulent dissipation rate equations. This value is taken 10-6 for energy equations [10].

Temperature distributions inside different the tank models

The best obstacle type and angle for supplying higher thermal stratification has been found numerically between all investigated cases. The aim is supply hot water as long as possible with high thermal stratification between the temperatures T4 (cold water enter to the tank from main lines) and T2 (hot water supplied by solar collector). In order to obtain this higher stratification, different kind of obstacles as cylindrical, semi-cylindrical and conic are inserted to the tank. These obstacles are placed in the tank with suitable angles and coordinates to decrease contact area between cold and hot water in the tank. T4 flow fibers don’t have to destroy hot water gradient. However, the hot water entering the tank (T2) would destroy the stratification. Therefore, hot water velocity is taken as 0.02 m/s for natural circulation. The flow rate of the hot water from tank to usage would be equal to the cold water entering to the tank from the main lines. The cold water velocity from the main lines is assumed as 1 m/s.

There would be vortexes in the tank. Because two different fluids are mixed in the tank and they are hitting each other towards to the wall and obstacle surfaces. Therefore, calculations are carried out by using wall functions method and standard k-s turbulent models with FLUENT [10].

Higher percentage of the cold water entering to the tank would be directed towards to cold water exit channel (T1) from the tank. Because the cold water enters and exit pipes in radial direction are in the same axis as symmetrical condition. So, the cold water can not produce a lot of vortex inside the tank and destroying effects into thermal stratification inside the tank would be decreased. The water is wanted to be hot as possible as for usage. In order to achieve this, the hot water exit channel (T3) is generally located at the top of the tank.

Discussion

The numerical analysis of the effect of the different type of obstacles into the thermal stratifications in the hot water storage tank in solar energy system has presented. The geometrical details of the obstacle types are defined under the theoretical model caption. The present study is initial works that aimed to find the best obstacle type between all investigated cases to analyze in experimental setup later.

Nearly 30 different types of obstacles are considered in this work but, 12 of them is present here. The temperature difference distributions of the tank with and without obstacle, which is given in figure 3 and 4, are presented in figure 5.

Smooth tank is considered firstly to compare the thermal stratification inside the tank with obstacles. There is a little thermal stratification at the top of the smooth tank. So, the temperature difference between thermal stratifications is far from desired values in smooth tank. The temperature distribution of the smooth tank case is depicted in figure 4-13. The hot water (T2) and cold water (T4) has contact in all axial cross-sectional area when they enter the tank. The rotations of the hot and cold water velocity vectors occur. Because they hit each other towards to the tank wall. The hot water stratification has been destroyed by cold water in this condition. In order to keep higher thermal stratification, the axial contact area between cold and hot water must be decreased and cold water mustn’t be directed towards upper part of the tank. Therefore, the obstacles in different shapes as cylindrical, semi-cylindrical and conic are placed in the tank to get minimum axial contact area.

The thermal stratification area and thickness are higher in tank with obstacles rather than tank without obstacles. The thermal stratifications are shown in figure 4 for storage tank with 12 different type of obstacle and 1 smooth tank. Figure 5 represent the temperature difference according to the tank numbers to determine the best tank models in order to obtain higher thermal stratification. T3-T4 and ((T2-T1HT3 — T1)) must have higher and ((T2-T3) and (T1-T4)) must have lower value to obtain good thermal stratifications. With respect to all these argument, obstacle type 7 and 11 has supplied higher thermal stratification.

T3 and T1 temperature distributions according to the tank model are illustrated in figure 6. T3-T1 (temperature difference between water exit to the usage and water going to the storage tank) must be considered for choosing the tank model has better performance of thermal stratification. This temperature difference must be higher to obtain higher thermal stratification. Obstacle type 11 has higher value of T3-T1. It can be said that obstacle type 11 can supply highest thermal stratification between all investigated cases. The best indicators to evaluate the effect of the obstacles into the thermal stratifications are T3 and T1. T3 and T1 must be higher and lower as soon as possible, respectively. T3 and T1 values are very close in smooth tank.

1-052 EuroSun2004

Figure 4-3

1.5 ■

1.4 ■

1.3
1.2
1.1
1

0.9

0.8

0.7

0.6

°.5

0.4

0.3

0.2

0.1

0

1.5
1.4
1.3
1.2
a 1.1
1

0.9

0.8

0.7

0.6

0.5

0.4

0.3

0.2

0.1

0

SHAPE * MERGEFORMAT

Temperature distributions of obstacle type 11 and 7 for operation periods of 5, 10, 15, 20, 25 and 30 minutes are shown in figure 7 and 8 in z plane, respectively. These two different obstacles have different temperature for z=0.0, 0.1, 0.2 and 0.3 m during the 30 minutes operation period. Obstacle type 11 reach the maximum temperature in z=0.3 m for all operation period but, obstacle 7 can reach the maximum temperature in z= 0.6. The temperature values are nearly the same in between z=0.4 and z=1.5 as in figure 7 and 8. So, these two obstacle type nearly has the same temperature inside the tank in all points.

Figure 9 represent the T3 and T1 distributions in z plane versus operation time for obstacle types 11 and 7. These temperature presented here for 6 different time periods as t=5, 10, 15,

20, 25 a 30 minute as seen in figure 9. T3 values are nearly the same for these two obstacle type but, T-i has lower value in obstacle type 11 after the 10 minute of operation period. So, type 11 has higher temperature difference between T3 and T1 after 10 minute in obstacle typell rather than obstacle type 7. The case is desired for higher thermal stratification. In the

light of these parameters, obstacle type 11 has supplied the best thermal stratification for system has natural circulation inside between all investigated obstacles.

1. Conclusions

The numerical analysis of the effect of the using different kind of obstacles in the heat storage tank to obtain higher thermal stratification has been presented. The temperature distributions in the heat storage tank with different obstacles are also presented in z-r plane. Temperature distribution of the smooth tank is also presented.

The results from these analyses as;

The tank with obstacles has better thermal stratifications rather than smooth tank.

The obstacle types have gap in the center, have better thermal stratification than obstacle types that have gap near the tank wall.

Tank models 7 and 11 have higher thermal stratification. So, these obstacles have supplied hot water in higher degree to use and also have water to the heater tank in lower degree. This is desirable case for thermal stratifications. It is seen that other obstacle have little effect into the thermal stratifications.

In z=0.2 plane, the average temperature values in radial direction is being lower in obstacle type 11 compared to the obstacle type 7 while the time period increases. Because tank model 11 has cylindrical shaped obstacle in z=0.2. This obstacle prevents the destroying effect of the cold water into the thermal stratification while the operation period of time. So, the temperature of the water going to the heater would decrease while the time period increases in tank 11. This is also desirable condition for heat storage tank.

T3 (water temperature for usage) has increased in tank 11 and T1 (water is going to the heater) has decreased while the increase of operation times. So, obstacle type 11 has the highest temperature difference between T3 and T1. This is the desired criteria for thermal stratifications. In the light of all these considerations, the tank, has obstacle type 11, is the best tank type for thermal stratification in between investigated cases.

Using obstacle has improved the solar collector efficiency as well as thermal stratifications. Because, T1 (water return to the solar collector) would decrease when the obstacle is used. So,

the solar collector efficiency would also increase.

Acknowledgement

The authors thank to the Erciyes University for FLUENT 6.1.22 code. References

1. Alizadeh S., An Experimental and Numerical Study of Thermal Stratification in a Horizontal Cylindrical Solar Storage Tank, Solar Energy, Vol.66, No.6, pp.409-421, 1999.

2. Al-Nimr M. A., Temperature Distribution inside Electrical Hot Water Storage Tanks, Applied Energy, Vol.48, pp.353-362, 1994.

3. Misra R. S., Thermal Stratification with Thermo siphon Effects in Solar Water Heating Systems, Energy Conversion Management, Vol.35, No.3, pp.193-203, 1994.

4. Helwa N. H., Mobarak A. M., Effect of Hot Water Consumption on Temperature Distribution in a Horizontal Solar Water Storage Tank, Applied Energy, Vol.52, pp.185-194, 1995.

5. Hariharan K., Badrinarayana K., Temperature Stratification in Hot Water Storage Tanks, Energy, Vol.16, No.7, pp.977-982, 1991.

6. Hahne E., Chen Y., Numerical Study of Flow and Heat Transfer Characteristics in Hot Water Stores, Solar Energy, Vol.64, No.1-3, pp.9-18, 1998.

7. Mo Y., Miyatake O., Numerical Analysis of the Transient Turbulent Flow Field in a Thermally Stratified Thermal Storage Water Tank, Numerical Heat Transfer, Part A, Vol.30, pp.649­667, 1996.

8. Eames P. C., Norton B., The Effect of Tank Geometry on Thermally Stratified Sensible Heat Storage Subject to Low Reynolds Number Flows, Int. J. of Heat Transfer, Vol.41, No.14, pp.2131-2142, 1998

9. P. V. Suhas, Numerical Heat Transfer and Fluid Flow, pp. 79-109, Hemisphere Pub. Co., New York, 1980.

10. FLUENT 6.1.22 user’s guide. Fluent Incorporated, Centerra Resource Park, 10, Cavendish Court, Lebanon, NH 03766, USA, 2001.

Nomenclatures

Vk Hot water velocity from tank to tank

V§ Cold water velocity from mainlines to tank

D Tank diameter

H Tank height

f1 The distances between cold water enter and exit point and bottom of the tank

d Pipe diameter

Si The distance between the point hot water enter and tank ceiling

d1 The gap diameter in the center of the obstacle

l Channel length

T Temperature

T3 Usage water temperature

T 1 Temperature of the water going to the heater

T 2 Temperature of the water coming from the heater

T4 Temperature of the water coming from the mainlines.

t Time

THE EFFECT OF THE WATER FLOW RATE INTO THERMAL. STRATIFICATION IN HOT WATER STORAGE TANKS

Necdet ALTUNTOP1, Mevlut ARSLAN1, Veysel OZCEYHAN1,

1 Dept. of Mechanical Engineering, Erciyes University, 38039 Kayseri, Turkey

Abstract: The numerical analysis of the effects of water flow rate into the thermal stratifications in the cylindrical hot water storage tank has been presented. The obstacle, has dimensions f/H=0.133 and g/D=0,2 and has a gap at the center of, has also replaced in the tank. This obstacle has supplied the thermal stratification between cold (at the bottom) and hot (at the top) water. Because it prevents mixing of two fluids. The flow rate has changed for both tanks with and without obstacles in order to analyze the effect of the volume flow rate. The temperature distributions are also presented for both types. The temperature distributions of the cold water in, hot water out and the temperature differences of the water going to and coming from the collector have been presented into the graph. The temperature distributions of both tank types have been compared to supply as high as possible hot water to usage and as low as possible to heater. At result, The best thermal stratification has obtained with Vk=0,8 m/s. The tank type has obstacle has better performance into thermal stratification compared to the smooth tank.

1. Introduction

Water has widely used in domestic and international area fro solar energy storage as sensible heat. In storage units, when the hot water is being used, the cold water comes instead of the hot water from the main lines and these two waters would be mixed in the tank and the water temperature would decrease drastically. In this study, the obstacle has placed to prevent this disadvantages and the effect of the volume flow arte into the thermal stratification has also investigated.

There is some previous analysis about these subjects as; ALIZADEH, has investigated the thermal behavior of a horizontal cylindrical storage tank both experimentally and numerically. He used one dimensional the Turbulent Mixing Model and Displacement Mixing Model in numerical calculations. He has used some models to prevent unsteady behavior of the vertical temperature distributions [1].

AL-NIMR has solved and presented some mathematical models to determine the effect of the different design parameters on the thermal stratification within the tank and the time required by tank to supply water within a specified outlet temperature [2].

MISRA has analyzed the thermal stratification both theoretically and experimentally in hot water storage tank for the thermo siphon effect in solar water heating systems. He has given the analytical expressions to obtain temperature distributions in the tank. He has also given the diagrams depends on the time to present conductive heat transfer between the layers in the storage tank [3].

HELVA ad MOBARAK have investigated the effect of the amount of the hot water using into the temperature distribution in solar water heating storage tank [4].

HARIHARAN and BADRINARAYANA have analyzed the thermal stratifications numerically
and experimentally in the hot water storage tank. They have studied the effect of surrounding and operating conditions into the thermal stratifications. They have observed that stratification improves with increasing AT and water flow rates [5].

HAHNE and CHEN have studied numerically about the flow and heat transfer characteristics in a cylindrical hot water store. They have used the storage efficiency to obtain thermal stratification. They have found that the increase of the Richardson and Peclect number has an effect that increases the storage efficiency [6].

Mo and MIYATAKE have carried out the transient numerical analysis for the thermal stratifications in the storage tanks. They have used turbulence model (k-s model). They have presented the effect of exchange cold water with hot water into the thermal stratifications [7].

EAMES and NORTON have investigated the effect of the tank geometry into the thermal stratification for sensible heat storage for low Reynolds number. They have presented the effect of inlet and outlet port locations on store performance [8].

In this study, the effect of the using different volume flow rate of the water for obtaining higher thermal stratifications has been analyzed numerically. One obstacle is placed in the cylindrical tank to get the best performance for thermal stratifications inside the tank between all investigated volume flow rates. The water has been used as fluid. The flow type has assumed as turbulent. There would be vortexes in the tank. Because two different fluids are mixed in the tank and they are hitting each other towards to the wall and obstacle surfaces. Therefore, calculations are carried out by using wall functions method and standard k-s turbulent model.

The main difference of this work is that the thermal stratification is supplied by using the obstacle. This obstacle has prevented to mixing of two different fluids to supply higher thermal stratification. The used obstacle has hole at the center. The different volume flow rate is used to analyze the effect of using this obstacle. The previous works has two dimensional calculations but, this present study has carried out by three dimensional.