Chapter Two Al-Khwarizmi Engineering Journal Al-Khwarizmi Engineering Journal,Vol. 12, No. 3, P.P. 80- 98 (2016) Experimental Study Using the Passive Solar Chimney for Evaporative Cooling With PCM and CFM as a Thermal Energy Storage Talib K. Murtadha* Hussien M. Salih** Ali D. Salman*** *Department of Mechanical Engineering/ University of Technology **,***Department of Electro- Mechanical Engineering/ University of Technology *Email: talib_km@yahoo.com ** Email: hussein_maj@yahoo.com *** Email: aligaphory@yahoo.com (Received 11 January 2016; accepted 17 April 2016) Abstract In this work, a test room was built in Baghdad city, with (2*1.5*1.5) m 3 in dimensions, while the solar chimneys (SC) were designed with aspect ratio (ar) bigger than 12. Test room was supplied by many solar collectors; vertical single side of air pass with ar equals 25, and tilted 45 o double side of air passes with ar equals 50 for each pass, both collectors consist of flat thermal energy storage box collector (TESB) that covered by transparent clear acrylic sheet, third type of collector is array of evacuated tubular collectors with thermosyphon in 45 o instelled in the bottom of TESB of vertical SC. The TESB was made from metallic iron sheets as a shell and fuelled by paraffin wax as phase change material (PCM). The PCM supported by copper foam matrix (CFM) to enhance thermal conductivity of wax. When heat is released from TESB to the air, a buoyancy force will be generated in chimney gaps. Then a difference in pressure between inside and outside test room leads to induce the air flow to test room through wet corrugated cellulose pad, where evaporative cooling (EC) occurs. Results of experimental work, that achieved in June, for 12 to24 hour in the test day, refer to effectiveness using EC to decrease the room temperature comparing. The system reduces test room temperature of up to 8.5~9.2 o C in 11:00 am to 3:00 pm and at highest effectiveness of EC, while minimum reduces in temperature of up to 3.5 o C in 8:00pm to 3:00 am. Also, the results showed the affectivity to using the TESB, during the night time for ventilation and EC, with lower effectiveness than from day time. The range of EC effectiveness equals 30.5-37.5 with a natural vent, while The maximum air change per hour (ACH) equals (3.8-6.187), and the maximum mass flow rate is equal to (36.651 kg.hr -1 ) at experimental evaluation of the system’s discharge coefficient value 0.371. Key words: Solar chimney , evacuated tubular collector, phase change material, copper foam matrix. 1. Introduction The energy consumed for space air conditioning, for heating or cooling and ventilation, depends on the latitude and altitude of the building. The consuming of energy dose not only lead to deplete energy source in our planet, but also lead to release more amount of CO2. So, that increases the globe worming potential and leads planet to creasy weather, beside increasing in temperature. Many sources are available and can be employed as renewable clean energy. And, solar of the sun is one of the important sources. So, many researches and studies have been employed to use the sun energy for cooling and ventilation, not for human comfort only, but in the industrial and agriculture. Maerefat [1] studied the SC and earth to air heat exchanger (EAHE) to decrease the indoor temperature. Results showed that the performance of the system depends on the solar radiation, outdoor air temperature , beside the configuration between SC and EAHE. With a taller SC in use, the number of required SCs decreases. Other side employed taller SCs lead to uncomfort. Same study was hinted for the optimum EAHE design for 0.5 meter in diameter and 20 meter in length. Maerefat [2] numerically studied for a combined system employing a SC with evaporative cooling cavity (ECC). Results revealed that the integrated system led to good conditions at daytime in test room, even mailto:talib_km@yahoo.com mailto:hussein_maj@yahoo.com Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 81 at high ambient air temperature about 40 o C, with low solar intensity of 200 W/m 2 , and relative humidity of 50%. Ventilation rate influenced by ambient temperature and solar intensity and configuration between both SC and ECC. Wasfy [3] work, a simulation performance of ventilation and evaporative cooling was studied in hot dry climate, for simulating test room in Baghdad city. Room was supplied by SC from one side, and wet pad from other. Results showed the ability to decrease the temperature inside the room to 10 degrees C, in hot dry climate, where the face of SC oriented to the west. Poshtiri [4] made comparison between two systems (SC-EAHE and SC-ECC). Numerical experiments showed that the SC-ECC system can prepare good indoor conditions, at low relative humidity of ambient air, and cooling demand of the room. Also, it depicted that the system can provide a good thermal condition after sun set. Other type SC-EAHE system results refer to that, at high ambient temperature and cooling load, system can provide a good indoor condition even at high air temperature and low solar intensity. Presented a comparison between two systems limited the ability to use the SC-EAHE for low insulation building, while the best choice for SC- ECC system is with high insulated building, especially in dry climates. Hassan [5] Showed results of a case study in Assiut City, for SC and evaporative cooling. Results showed the effect of air flow rate, by the relation between solar radiation, pressure coefficient with area of solar collector. Air flow rate increased when collector's temperature increased, the test room temperature decreased by 10-11.5 o C from the outdoor temperature, in the test day 21may-21 August. Mizanur [6] Presented an experimental work, applied a new design of passive solar chimney with a modern configuration of EC. Where the air induced through the SC leads the outside hot air to pass through the pipe that immersed in outdoor splash water pool. For manipulated air, the temperature decreased approximately 5 o C below the ambient temperature, and about 2-3 o C below the room temperature. Fazel [7] produced a new configuration of passive cooling system through ventilation mode. The system reduces test room temperature of up to 5 o C from the atmospheric temperature, with ability to decrease room temperature during night ventilation. 2. Experimental Set Up 2.1. Rig Set-Up The rig that used in this work consists of insulated test room, two types of solar chimneys (SC) that joint together in series configuration; a vertical fixed SC, and tilted one with 45 o in angle, both instilled at the south oriented wall. As well as evacuated tubular collectors with thermosyphos array are used. Good accuracy measurement instruments tools are used in different measuring, beside two types of data acquisition data logger DAQ. 2.1.1. Semi Full Scale Test Room and the Effective Dimensions of the System The test room with dimensions (2m length, 1.5 m width, 1.5 height), supported by SC’s in the south oriented wall, while paper fill (pad) inserted inside vent window and covered by wind protection in north oriented wall. The length of room is bigger than from width and height, to clarifying the behavior of temperature distribution inside room. The structure of test room consists of a wooden frame, walls are insulated by 4 cm of cork with 0.043 W/m. k in thermal conductivity, 2.5 cm thick with 0.05 W/m. k for glass wool. The outside walls are insulated by marmox with U=2.7 W/m 2 .C, while the roof and floor are insulated by marmox thermo-block with U=1.69 W/m 2 . o C. Fig.1, shows EC paper fill (pad), Fig.2. depicts room general details in ISO view, and Fig.3, shows the ETC with characteristics given in table.1. Fig.4. describes the schematic diagram for the test room in vent and EC-mode, that provided with two types of solar collectors instrumented with number of velocity and temperature sensors, table.1, defines all the symbols of Fig.2. 2.1.2. Evacuated Tubular Collectors (ETCTS) Ten pieces of ETC with Thermosyphon (ETCTS) are used to collect heat at an inclination angle of 45 o , and transfer heat to the bottom of the vertical SC. ETC 50 cm in length and 5.8 cm in diameter is shown in Fig.3. TS consists of the condenser which instilled inside the TESB, TS’s evaporator is inserted in the axial center of double glass ETC and covered by thin aluminum fin. expander tube with expander roll tools are used to make a good contact between TS’s condenser and (CFM) in TESB. Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 82 Fig.1. Vent open window covered by pape fill in Evaporative Cooling mode Fig. 2. Schematic diagram of insulated test room. Cellulose pad weather station (iso- view) θ C=12 cm Ac o L1 A=180cm *18 cm wind protection Inlet air wind protection L H W cw Aci Ac o Ari LO1 W1 Hade chimney protection 1Ɵ S1 d1 d2 Inclination angle Inlet air (vent air) Outlet air (exhaust air) SI Stack Height SI Cellulose pad Splash water ETCTS base Splash water path Cellulose pad Water tank Wind protraction Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 83 Table1, Description of symbols shown in Fig. 2 . Fig. 3. Evacuated Tubular collector with description notes. 0.75 meter in width. The box filled by copper foam matrix (CFM), and full refined paraffin wax, to form a thermal energy storage. Upper half of box is covered by double acrylic clear glass from outside, lower halve part is thermally insulated, and connected to ten evacuated tubular collectors, of 50 cm length tilted at 45 o . The upper side of TESB that exposed to the sun light is painted by a thermally matt black paint. The other side of the storage box (room side) is covered by a acrylic sheet, with 6.7 cm gap space and 14.92 in aspect ratio. Fig.5. shows steps for manufacture the vertical fixed solar chimney. imension description Symbol No Dimension Description Symbol No 6.7 (cm) Chimney gap CG 12 148 (cm) Width of the test room w 1 (thick=2.7cm* w=75cm*H=10 2cm) Thermal heat storage box THS-B 13 147 (cm) High of the test room H 2 (75m*11cm) Area inlet to the chimney Aci 14 200 (cm) Length of test room L 3 (75cm*8cm) Area outlet from chimney Aco 15 75 (cm) Chimney width (THSBW) CW 4 (148cm*16) Area inlet test room Ari 16 150 (cm) Second system chimney height L1 5 ( o C) Inside temperature TTHSB-i 17 91 (cm) Head Chimney protection width W1 6 ( o C) Surface temperature TTHSB-S 18 90 ( o ) Head chimney protection angle 1Ɵ 7 ( o C) Covered surface temperature TTHSB-SC 19 20 cm Head chimney protection side length S1 8 ( o C) Temperature air inlet chimney gap Tair-in-c 20 4.5 (cm) Head chimney distance between lower side corner and exit of moved chimney d1 9 ( o C) Temperature air outlet chimney gap Tair-out-c 21 18 (cm) Head chimney distance between top corner and exit of moved chimney d2 10 12 cm Wind protection space from window C 22 115 (cm) Height from Ari to the base LO1 11 1 Thermosyphon evaporator 4 Black Absorption inner layer 2 Thermosyphon condenser 5 Fin of evaporator 3 Vacuum insulation Tube 6 Centering Tube Stopper 3 5 6 4 2 1 Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 84 Fig. 4. Schematic diagram describing the test room in vent and evaporative cooling mode. 2.1.3.The Solar Chimney (SC) Two systems of solar chimneys are used, in ventilation with evaporative cooling mode: A-A vertical fixed solar chimney system Vertical built-in chimney for ventilation and EC mode. A one meter in height of galvanized iron box collector installed at the south oriented wall with 0.75 meter in width. The box filled by copper foam matrix (CFM), and full refined paraffin wax, to form a thermal energy storage. Upper half of box is covered by double acrylic clear glass from outside, lower halve part is thermally insulated, and connected to ten evacuated tubular collectors, of 50 cm length tilted at 45 o . The upper side of TESB that exposed to the sun light is painted by a thermally matt black paint. The other side of the storage box (room side) is covered by a acrylic sheet, with 6.7 cm gap space and 14.92 in aspect ratio. Fig.5. shows steps for manufacture the vertical fixed solar chimney. B-A tilt solar chimney system Inclined SC at 45 o is used by combining with the fixed vertical chimney system. tilted SC consists of a three TESB made from iron galvanized boxes that painted by a layer of matt black and filled with CFM and semi refined of paraffin wax as PCM. The three boxes are arranged in series configuration along the length of SC and construct a double side chimney gap, with 3 cm in each gap wedth. Evacuated solar collector Thermosyphon Evaporator of Thermosyphon condenser of thermosyphon N :north direction S :South direction EC mode series chimney working angle PCM 1- PCM 1- PCM 1- ? flat box collector consist from rectangular flat galvanized Iron boxes contain MF-PCM inside it. mid CMF-PCM collector -double parallel air flow channel up and down the MF-PCM in flat box collector - natural evaporative cooling ratio of length to the depth 2*(l/g=50) -high =length cos(theta) wind protection wind protection water tank glob valve splash water Paper Fill clear Acrylic cover  Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 85 CFM Flat plat box Constrict the TESB SC gap Array of ETC Collector of fixed chimney Acrylic wall TESB ETC base Step-1 Step-2 Step-3 Step-4 Step-5 Fig . 5 Stages to manufacture the vertical fixed SC and setup in the test room. Outline dimensions for tilted SC are 1.5 m in length and 0.75 m in width as shown in Fig .6,The schematic diagram is shown in Fig .7. SC’s boxes covered by 0.4 cm of acrylic clear sheet. Tilt chimney Test room TESBs Tilted chimney Chimney gap Solar collector ETCTS Cross section in tilted SC TC location transparent acrylic cover Vertical fixed SC Fig . 6 Setup the inclined SC in the test room Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 86 Induced air flows through a duple pass over flat thin TES box mid collector, with 50 in aspect ratio for each pass, and that bigger than the critical aspect ratio (arcr=12), to prevent back flow. 2.2. Solar Chimney Components 2.2.1. The solar chimney type and working angle in selective mode In this study, an experimental and theoretical examination are applied, to select the active working angle for tilted SC. Right angle means a good contact between air flow and SC collector without separation, but this angle conjugating simultaneously with low solar intensity. Experimental result, beside theoretical Fig.10 program simulation result refer to choice angle, at 45 o as selective working angle in this study. Also in this work, experimentally examining covers three types of inclined 45 o SCs; (flat plate, flat plate with double pass, flat thermal energy storage box with double pass). All testes applied for vent mode only. Results in Fig.11 refer to the ability of flat plat collector with double pass, to release heat to air, but with no effect in night time, so flat box collector with double pass is the active SC collector to employing in vent and EC mode. 2.2.2. The absorber One TESB are used as SC collector in vertical chimney, while Three TESBs are used to construct the tilted chimney collector. The emissivity of the painted layer of plate is ε=0.095. and the absorptivity αp=0.9, while the reflectivity ρplate=0.1. 2.2.3. Thermal energy storage material A combined of paraffin wax, as a phase change material, and copper foam matrix are used as a TESM. Where the paraffin wax is used to storage heat, in sensible and latent heat regions, while the CFM is used to enhance the thermal conductivity of thermal TESM . Air inlet to the first SC pass Air inlet to the second SC pass - Temperature Sensor Probe for air - Temperature Sensor probe on plate or built in material - Velocity Sensor Position th e ta flat plat collector with matt black paint 38 39 40 42 37 Acrylic sheet 4mm TC.probe Insulation (wall glass) 2 in, 24 kg/m3 in density serface TC probe inlet air temperature probe outlet air temperature probe temperature of acrylic sheet 25 cm 50 cm 50 cm 25 cm Iron galvanized 0.8mm z=1.2 cm z=1.8 cm z=2.4 cm z=3.6 cm z=4.2 cm z=4.8 cm z=5.4 cm z=6 cm z=3 cm z=0.6 cm 43 46 49 52 58 61 64 67 44 47 50 53 59 62 65 68 45 48 51 54 60 63 69 71 70 72 (P CM+CFM) (PCM+CFM) Iron galvanized matt paint Box (P CM+CFM) (P CM+CFM) 73 57 75 66 74 Distance between transparence sheet and TESB collectors was 3 cm, amd between TESB and the base of SC was 3cm. Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 87 Table2, n-Alkenes table No. n-Alkanes No of carbon Mol. weight Melting point (K) Latent heat of fusion (kJ/kg) Density at 20 o C (kg/m 3 ) Specific Heat Boiling Point (K) Solid (J/mol.K) at 298 K Liquid (J/mol.K) at 353 K 1 Heneicosane 21 296 313.35 213 788 (s) 570.7 a 698 a 629.7 2 Docosane 22 310 317.15 252 791(s) 598.1 a 739.0 641.8 3 Tricosane 23 324 320.65 234 793(s) 625.0 a 772.0 653.4 4 Tetracosane 24 338 323.75 255 796(s) 651.4 a 805.0 664.5 5 Pentacosane 25 352 326.65 238 798(s) 670.4 a 815.9 675.1 6 Hexacosane 26 366 329.45 250 800(s) 677.8 a 870.0 685.4 7 Heptacosane 27 380 331.95 235 802(s) 728.1 a 928 a 695.3 8 Octacosane 28 394 334.35 254 803(s) 752.8 a 937.0 704.8 9 Nonacosane 29 408 336.35 239 805(s) 777.2 a 1001 a 714.0 a:estimated values-experimental data not avilible time (sec) T e m p e ra tu re (C ) 0 100 200 300 400 500 600 700 56 57 58 59 60 61 62 63 64 65 time (sec) T e m p e ra tu re (C ) 0 200 400 600 800 1000 1200 1400 1600 44 46 48 50 52 54 56 58 60 62 64 66 2.2.4. Phase change material (PCM) Many types of paraffin and microcrystalline wax are examined to find the suitable wax. So two types of paraffin wax are selected as working PCM; -First type a full refined paraffin wax PW-600, used as a TESM with a CFM. This type is used in the fixed vertical SC. -Second wax type is a semi refined paraffin wax, used with the CFM as a TESM in the TESB for the second inclined chimney. To define the thermo physical properties of each wax, by limiting the melting point for each experimentally from (temp-time) diagram Fig.8. Then by using empirical relations that dependent on the number of carbons. Where from the melting temperature and from table-2 [8], can be select the suitable wax, then calculated the properties for solid, liquid single zone and mushy zone. The formula defined n-Alkanes structure is , n means the number of carbons. Fig. 8. Experimental results show behavior of wax in different temperature a, full refined PW b, semi-refined PW Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 88 Fig. 9. Copper foam matrix a-with PW, b-without PW. 2.2.5. Copper Foam Matrix (CFM) The combined of FM-PCM means higher thermal conductivity, with same latent heat of fusion, and same solidification and melting temperature. So, a copper foam matrix CFM is used to enhance the heat transfer, because the thermal conductivity of PCM is not enough to receive or release heat in selective heat transfer duration time. Fig .9, refers to the CFM with and without PCM. CFM used with 95% porosity and 30 porous per inch (30 ppi). 2.2.6. The transparent cover Nontraditional transparent cover, 4 and 6 mm from clear acrylic sheets are used with vertical and tilted 45 o SCs. The special properties for these material are the; flexibility, light weight, anti crash, beside other properties that in common with BK-7. All important properties for acrylic and BK-7 except thermal conductivity of BK-7, are calculated for three selective angles and listing in Table.3, that showing a comparison between commercial glass sheet (BK-7) and clear acrylic sheet. 2.3. Measurement and instrument tools The following measurement and instrument devices are used in this project beside data logger, data acquisition (DAQ), to measuring the depended and independent variables; 2.3.1. Temperature Three types of temperature sensors are used in different positions. With 290 meter of type-K thermocouple (TC) are used to cover all the temperature that must be measured in the SC’s and test room beside the SC’s gap. A 3D mesh grid of temperature sensors are distributed inside Table 3, physical properties for Acrylic and commercial window glass( Bk7). Angle (degree) n ƘL K (w/m. o C) Glass BK7 30 1.526 0.799 0.072 0.125 32*L at 4mm 0.92 0.81 45 0.782 0.0875 0.133 60 0.729 0.14 0.141 Clear Acrylic 30 1.491 0.885 0.0741 0.0414 0.04 0.94 0.7 45 0.872 0.0868 0.0443 60 0.82 0.143 0.0477 L: cover thickness in mater. n: Average refractive index in solar spectrum of cover materials. Ƙ: extinction coefficient + + =1 = transmitivity, ρ=reflectivity = absorbtivity, = emissivity (a) (b) 40 -x 40 -x Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 89 the test room. 36 semiconductors type LM-35dz, with 36 thermocouple probes are distributed inside the room in three horizontal layers (3*4) node. The probes are connected to two types of Data Acquisition (DAQ) from labJack U6-PRO and UT-7, also two types of digital thermometer are used - DM6801A+ digital thermometer with 0.1 o C in resolution and -50 to 199 o C in range, with +/- (0.2%+1 o C) value in accuracy. - DM6803A+ digital thermometer with 0.1 o C in resolution , 0 to 800 o C in range, and accuracy with +/- (0.3%+1 o C). Both thermometers are connecting to the selector switch. As well as, array of thermocouple probes are distributed and connected to the vertical and tilted SC’s gab. TC’s probes connected to the collector plate, TESB, ETC and glass cover. Fig .7 shows The positions array of thermocouple probe sensors in tilted SC. 2.3.2. Air Velocity Two types of a thermal digital anemometer with high resolution are used to measure the air velocity in the two systems of chimney gap, beside room. -TSI AVM410 thermal anemometer with 0.01 m/s in resolution, and same value in threshold. Velocity range (0 to 20 m/s), and reading temperature range (-18 to 93 o C). -Testo 405-V1 Thermal anemometer with 0.01 m/s in resolution and threshold, while velocity range (0 to 5 m/s) at (-20 to 0 o C) and (0 to 10) when temperature range (0 to 50 o C). - AM-4838 digital fan anemometer is used primary to limit the direction of air flow inlet to or outlet from the solar chimney beside smoke generator. The specification of this digital anemometer : 0.1 m/s in resolution, 0.4-30 m/s in range and threshold equals 0.4 m/s. Positions of the measured velocity are showed in Fig.7, where a three-hole port to measure the velocity from upper side air pass, and two from lower side are pass . 2.3.3. Solar radiation intensity Two types of solar intensity meter are used in the experimental work. TES- 1333 model is fixed at tilted SC, with specification: 1 W/m 2 in resolution, 0-2000 W/m 2 in range. Other Type TES-132 with a data logger and interface connection to PC. Its specification: 0.1W/m 2 in resolution and measuring range 0-2000 W/m 2 . This type Is used to measure the solar intensity before and after the acrylic cover to calculate the transmitivity value. Beside recording solar intensity on surface of ETC and fixed SC. Average solar intensity recorded by WS. 2.3.4. Weather station system A modern weather station model WS-1000- WiFi with 915 MHz in Frequency, outdoor and indoor instrument collection, transmitted the data every 16 second to the analyzer data logger data screen, with built in memory, and external data storage. Data logger records the data transmitted at interval time, that recognized by user to record data each 60 seconds for 24 hour. The following important data can be recorded by the WS-1000- WiFi :  Indoor average temperature  Indoor relative humidity  Real and absolute pressure  Outdoor average temperature  Outdoor relative humidity  Solar radiation intensity (horizontally)  Wind speed  Gust speed  Wind direction 2.4. Experimental Test Procedure The experimental work, is achieved in June, 2015, where data are logging for the dependent variables along 12 hours. All measurement and instruments tools are used as mentioned previously to measure and record the dependent variable, for each 2 hours as test interval, and average value for general variables that measured and recorded by WS data logger along 24 hours, with 20 minutes as test interval The depended variables including each of - Measuring temperature in; chimneys gap, test room space, TESB, outdoor temperature, - velocity in chimney gap beside inlet and outlet SC - solar intensity. While the general depended variable including each variables that measuring by WS. Many conditions are Applied, to select test day such as; clarity (not dusty), acceptable wind speed without gust, the clouds absence or partial cloudy day. Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 90 2.5. Theoretical Consideration and Calculation In this study assuming there is no heat losses directly from test room to the surround, or from the insulated parts of SC’s. Therefore, SC that exposure to the sun solar, absorbed all heat with respect to the value of collector absorbtivity, reflectivity and emissivity, beside the acrylic cover’s transmitivity, absorbtivity, reflectivity and refractivity value. So, according to the heat balance, heat absorbed by collector must be equal to heat released to the working air that passes through the chimney gap. 2.5.1. Calculated heat storage (TESB) In experimental test, results are shown in Fig.8, to find melting point range, then from n-Alkenes table-2 [8], to define the latent heat of fusion vale in mushy zone. So for material which has a symmetrical distribution of the specific heat for the melting region[9], ...(1) ...(2) ρ ρ ( ) ( ) ...(3) . / . | | / , - ...(4) ρ ( ( ))) ( ) as defined before, for materials which show a symmetrical distribution of the specific heat for the melting region. . ..(6) ( ) 2 0 ( )13 ( ) ...(7) ( ) 0 ( )1 ...(8) ( ) ( ) ( ) ( ) ..(9) to calculate heat transfer in evaporative cooling procedure [10]. Cooling and humidification (removed heat (sensible) with the addition of moisture (latent)) are: ..(10) ̇ { ( ) ( )} ..(11) 2.5.2. Heat transfer to the humid Air The inside solar chimney heat transfer from TESB to the moist air by simple equation is illustrated below [10]. ( ) ..(12 ) For the sensible heat transfer to the dry air, ( ( )) ..(13) Or by employing the equation of state for moist air [10]. 2.5.4. Simultaneous efficiency To compute the simultaneous efficiency at duration time of heat charge, it must compute the rate of heat storage in TESB during its exposure to the solar radiation which can be calculated from eqn. below [8] = ( ) m= mass for wax and copper foam matrix t= duration time to charge TESB by heat (q) so, the heat storage in duration time t can be found from eqn. (15) ..(15) To compute heat storage during duration charge for N time , by algebraic summation of eqn. 14 to get ∑ * + ..(16) Its mean the rate between heat storage to the heat absorbed by TESB. , - [ ] 0 ⁄ 1 , - , - Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 91 = * + ..(17) 2.5.5.Ventilation air change per hour (ACH) To calculate the mass flow rate through the solar chimney only, or through the solar chimney and room. [11],[12]. √ ( ⁄ ) √ 0 1 ..(18) Where, is the system’s discharge coefficient, is defined as the ratio of the cross- section area at the vena-contract to the actual opening area. It is taken as 0.57 due to the sharp edge inlet, or calculated as shown later . is the mean temperature of air in the channel (Kelvin), which is described by the equation below [13]. ( ) ..(19) Where, is meant for the mean temperature approximation which depends on the inlet and outlet air temperature . , are equal temperature of air inlet and outlet solar chimney; room temperature; ⁄ [14] glass side ...(20-a ) absorber side ...(20-b) ...(21) To calculate the system’s discharge coefficient [15]: | | ...(22) ( ); ( ) ( ) ( ) ( ) ; To calculate ACH; air change per hour [14] is ̇ ( ) 3. Result and Discussion Experimental results showed, the effect of EC system by using induced air through solar chimney. Fig.12. shows that there is a decreasing in indoor temperature along test time comparing with outdoor temperature. Maximum difference in temperature 8.5-9.2 o C occurred at maximum solar radiation with increasing in relative humidity. Fig.13. shows the vent-mode only where indoor temperature is almost higher than outdoor temperature with low RH%, especially in noon time at high solar radiation. Fig.14. appears the effect of induced air through solar chimney, and the evaporative cooling effectiveness (ECE) value, where the high value of effectiveness occurs approximately at high value of solar radiation. That means a high velocity of air through SC (through test room) at noon time. Temperature distributions in vertical mid layers along test room are shown in Fig.15-(a-i). Fig.15-d. shows 3D test room in three layers : east , mid and west layer along the test room and after 2.pm, the sun direction effect is shown in the west layer, where increasing in temperature more than the temperature of east layer. After sunset starts, Fig.15-f. shows the starting decrease in room temperature. Other Fig.15.(g-i) represents the distribution of temperature in test room along day time and night time, where temperature increasing in the roof and near the solar chimney, while it decreases on other zone especially near the wet pad. In Fig.16, The experimental and theoretical value of air change per hour (ACH) in EC-mode depends on discharge coefficient of system 0.371, that calculated for the present test room. Low Cd value caused by the effect of fill pad air flow resistance. In experimental work, ACH was determined, depending on the tilt SC collector temperature and air velocity, so it measured in mid way in chimney gap, and before the end way of chimney gap. The fluctuation appeared in ACH value because of the turbulent in air flow, while the value of theoretical ACH was determined depending on the variables in Eq.23. The variables change smoothly especially temperature of room and collector, while the calculation of mass flow rate of air depends on upper and lower collector temperature and density. So the air mass flow rate was experimentally estimated in upper and lower chimney gap way (mid ,before end), Fig.17. Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 92 Fig. 10. Optimal solar chimney angle, for different seasons in Baghdad city. Fig.11. comparison between three different types of tilted solar chimney's collector with selective working angle. Fig. 12. Average temperature for indoor and outdoor through test day with Vent and EC effect. Jan Feb M ar Apr M ay Jun Ju l Aug Sep O ct Nov Dec fivtenth of month along the year -30 -20 -10 0 10 20 30 40 50 60 70 80 90 100 A n g le ( d e g re e ) Solar declination angle Solar altitude Optimum tilt collector angle 8:00 10:00 12:00 14:00 16:00 18:00 20:00 22:00 0:00 Day time (hh) 24 30 36 42 48 54 60 66 72 78 84 90 96 co lle ct or s ur fa ce te m pe ra tu re ( C ) collector up surface temperature single pass flat plate collector double pass flat plate collector double pass flat storge box collector selective angle for tilted chimney (theta=45 degree) 0:0 0 1:4 0 3:2 0 5:0 0 6:4 0 8:2 0 10:0 0 11:4 0 13:2 0 15:0 0 16:4 0 18:2 0 20:0 0 21:4 0 23:2 0 1:0 0 Day time (hh:mm) 26 28 30 32 34 36 38 40 42 44 ai r t em pe ra tu re d eg re e (C ) 12 16 20 24 28 32 36 40 44 48 R el at iv e H um id ity (% ) 11-6-2015 evaporative cooling with splash water 0 100 200 300 400 500 600 700 800 900 h or iz on ta l S ol ar In te ns ity ( w /m ^2 ) 3 4 5 6 7 8 9 10 (T ou t-T in ) d eg re e (C ) Indoor Temp. Outdoor Temp. Indoor RH% Outdoor RH% h Solar Intensity Tout-Tin Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 93 0:0 0 1:4 0 3:2 0 5:0 0 6:4 0 8:2 0 10:0 0 11:4 0 13:2 0 15:0 0 16:4 0 18:2 0 20:0 0 21:4 0 23:2 0 1:0 0 Day time (hh:mm) 26 28 30 32 34 36 38 40 42 44 ai r t em pe ra tu re d eg re e (C ) 12 16 20 24 28 32 36 40 44 48 R el at iv e H um id ity (% ) 11-6-2015 evaporative cooling - effectivness EC by splash water 0 100 200 300 400 500 600 700 800 900 h or iz on ta l S ol ar In te ns ity ( w /m ^2 ) 0.28 0.32 0.36 0.40 0.44 0.48 0.52 E va po ra tiv e C oo lin g Ef ec tiv ne ss % Indoor Temp. Outdoor Temp Indoor RH% Outdoor RH% EC effectivness 40 50 60 70 80 90 100 110 120 130 140 150 160 Length's Part From Test Room To Measure Temperature (cm) 40 50 60 70 80 90 100 110 H e ig h t' s P a rt F ro m T e s t R o o m , T o M e a s u re T e m p e ra tu re ( c m ) 28.3 28.4 28.5 28.6 28.7 28.8 28.9 29.0 29.1 29.2 29.3 29.4 North Side 11/6/2015 -10:00 pm Data- EC-V-L2 Fig. 15-a. Effect of evaporative cooling on the temperature Distribution in mid layer test room (08:00 am). Fig. 15-b. Effect of evaporative cooling on the temperature Distribution in mid layer test room (10:00 am). 0:00 1:40 3:20 5:00 6:40 8:20 10:00 11:40 13:20 15:00 16:40 18:20 20:00 21:40 23:20 Day time (hh:mm) 30 32 34 36 38 40 42 44 46 48 ai r t em pe ra tu re d eg re e (C ) 0 2 4 6 8 10 12 14 16 18 20 Re la tiv e Hu m id ity % 0 100 200 300 400 500 600 700 800 900 ho riz on ta l s ol ar in te ns ity ( w/ m ^2 ) 4-6-2015- Data ventilation only -6 -4 -2 0 2 4 6 (T ou t-T in ) d eg re e (C ) Indoor temp. Outdoor temp. Indoor RH% Outdoor RH% h solar intensity Tout-Tin 40 50 60 70 80 90 100 110 120 130 140 150 160 Length's Part From Test Room To Measure Temperature (cm) 40 50 60 70 80 90 100 110 H e ig h t' s P a rt F ro m T e s t R o o m , T o M e a s u re T e m p e ra tu re ( c m ) 30.8 30.9 31.0 31.1 31.2 31.3 31.4 31.5 31.6 31.7 31.8 31.9 32.0 32.1 32.2 North Side 11/6/2015 -08:00 am Data- EC-V-L2 Fig.13 average temperature for indoor and outdoor through test day for Vent only. Fig.14. Evaporative Cooling effectiveness through test day. oC oC Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 94 Fig. 15-c. Effect of evaporative cooling on the temperature Distribution in mid layer test room (12:00 pm ). Fig. 15-d. Effect of evaporative cooling on the temperature Distribution in 3D test room (02:00 pm). Fig. 15-e. Effect of evaporative cooling on the temperature Distribution in mid layer test room (04:00 pm). Fig. 15-f. Effect of evaporative cooling on the temperature Distribution in mid layer test room (06:00 pm) Fig. 15-g. Effect of evaporative cooling on the temperature Distribution in mid layer test room (08:00 pm). 40 50 60 70 80 90 100 110 120 130 140 150 160 Length Part From Test Room To Measure Temperature (cm) 40 50 60 70 80 90 100 110 H ig h P a rt F ro m T e s t R o o m T o M e a s u re T e m p e ra tu re ( c m ) 30.2 30.4 30.6 30.8 31.0 31.2 31.4 31.6 31.8 32.0 32.2 32.4 32.6 North Side 11/6/2015 -12:01 pm Data- EC-V-L2 40 50 60 70 80 90 100 110 120 130 140 150 160 Length's Part From Test Room To Measure Temperature (cm) 40 50 60 70 80 90 100 110 H e ig h t' s P a rt F ro m T e s t R o o m , T o M e a s u re T e m p e ra tu re ( c m ) 33.2 33.3 33.4 33.5 33.6 33.7 33.8 33.9 34.0 34.1 34.2 34.3 34.4 34.5 34.6 34.7 North Side 11/6/2015 -02:00 pm Data- EC-V-L1 40 50 60 70 80 90 100 110 120 130 140 150 160 Length's Part From Test Room To Measure Temperature (cm) 40 50 60 70 80 90 100 110 H e ig h t' s P a rt F ro m T e s t R o o m , T o M e a s u re T e m p e ra tu re ( c m ) 33.0 33.2 33.4 33.6 33.8 34.0 34.2 34.4 34.6 34.8 35.0 35.2 35.4 35.6 North Side 11/6/2015 -02:00 pm Data- EC-V-L2 40 50 60 70 80 90 100 110 120 130 140 150 160 Length's Part From Test Room To Measure Temperature (cm) 40 50 60 70 80 90 100 110 H e ig h t' s P a rt F ro m T e s t R o o m , T o M e a s u re T e m p e ra tu re ( c m ) 33.4 33.6 33.8 34.0 34.2 34.4 34.6 34.8 35.0 35.2 35.4 35.6 35.8 North Side 11/6/2015 -02:00 pm Data- EC-V-L3 40 50 60 70 80 90 100 110 120 130 140 150 160 Length's Part From Test Room To Measure Temperature (cm) 40 50 60 70 80 90 100 110 H e ig h t' s P a rt F ro m T e s t R o o m , T o M e a s u re T e m p e ra tu re ( c m ) 34.4 34.6 34.8 35.0 35.2 35.4 35.6 35.8 36.0 36.2 36.4 36.6 11/6/2015 -04:00 pm Data- EC-V-L2 North Side 40 50 60 70 80 90 100 110 120 130 140 150 160 Length Part From Test Room To Measure Temperature (cm) 40 50 60 70 80 90 100 110 H ig h P a rt F ro m T e s t R o o m T o M e a s u re T e m p e ra tu re ( c m ) 33.6 33.7 33.8 33.9 34.0 34.1 34.2 34.3 34.4 34.5 34.6 34.7 34.8 34.9 35.0 35.1 35.2 11/6/2015 -06:00 pm Data-EC-V-L2 40 50 60 70 80 90 100 110 120 130 140 150 160 Length's Part From Test Room To Measure Temperature (cm) 40 50 60 70 80 90 100 110 H e ig h t' s P a rt F ro m T e s t R o o m , T o M e a s u re T e m p e ra tu re ( c m ) 30.3 30.4 30.5 30.6 30.7 30.8 30.9 31.0 31.1 31.2 31.3 31.4 31.5 31.6 31.7 31.8 31.9 32.0 11/6/2015 -08:00 pm Data- EC-V-L2 North Side oC oC oC oC oC oC Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 95 8.00 10.00 12.00 14.00 16.00 18.00 20.00 22.00 24.00 Day time (hh:mm) 6 8 10 12 14 16 18 20 22 24 m as s fl o w r at e o f ai r in c h im n ey g ap ( kg /h r) mass flow rate in chimney gap mid way up chimney gap mid way down chimney gap before outlet up chimney gap before outlet down chimney gam Fig. 15-h. Effect of evaporative cooling on the temperature Distribution in mid layer test room (10:00 pm). Fig. 15-i. Effect of evaporative cooling on the temperature Distribution in mid layer test room (12:00 am). Fig. 16. Air change per hour in evaporative cooling mode. So, the mass flow rate through the test room is equals to the mass flow rate through the chimney with respect to the synchronous change in value for volume flow rate and density. Maximum of mass flow rate of air through test room approximately 1.6.61 kg.hr -1 in value. Air gap temperature in vertical fixed chimney shown in Fig.18, the air temperature are measured in three positions in chimney gap, after inlet, in the mid way, and before outlet of chimney gap. Results refer to increase in air temperature along the way of chimney length, and the heights of air temperature in same level are near the TESB. Fig.19. shows the heat storage efficiency (HSE) with maximum value in 10:00 am, because the higher difference in temperature between inside TESB, and it’s up-surface collector (0.75*1.5) m 2 accrues at that time. HSE equals the summation of change of energy storage through time to the summation of solar energy through same time. 4. Conclusions From the experimental results, the following conclusions can be drawn: - Employing the evaporative cooling effect, made more successfully comfortable zone ,and more suitable for human live mode, and that done by decreasing the room air temperature with respect to the increasing of relative humidity. Fig. 17. Experimental value of mass flow rate. - Comfort condition does not cover the day time only but also the night time by using the thermal energy storage material. - Accomplished double pass solar chimney collector ensures a good aspect ratio between 40 50 60 70 80 90 100 110 120 130 140 150 160 Length's Part From Test Room To Measure Temperature (cm) 40 50 60 70 80 90 100 110 H e ig h t' s P a rt F ro m T e s t R o o m , T o M e a s u re T e m p e ra tu re ( c m ) 28.3 28.4 28.5 28.6 28.7 28.8 28.9 29.0 29.1 29.2 29.3 29.4 North Side 11/6/2015 -10:00 pm Data- EC-V-L2 40 50 60 70 80 90 100 110 120 130 140 150 160 Length's Part From Test Room To Measure Temperature (cm) 40 50 60 70 80 90 100 110 H e ig h t' s P a rt F ro m T e s t R o o m , T o M e a s u re T e m p e ra tu re ( c m ) 27.0 27.1 27.2 27.3 27.4 27.5 27.6 27.7 27.8 27.9 28.0 28.1 28.2 North Side 12/6/2015 -00:01 am Data- EC-V-L2 8.00 10.00 12.00 14.00 16.00 18.00 20.00 22.00 24.00 Day time (hh:mm) 3.6 4.0 4.4 4.8 5.2 5.6 6.0 6.4 6.8 7.2 7.6 A C H experimental value ACH depend on mid way of tilt chimney gap experimental value ACH depend on end way of tilt chimney gap theoretical calculation oC oC Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 96 chimney length and the gap thickness, the ratio is bigger than 12, make a chance to prevent reverse air flow in chimney gap. Fig.18. Vertical SC air gap temperature. Fig. 19. Solar Radiation, Energy Summation and heat storage efficiency. Nomenclature A area ACH Air chinge per hour Cd Discharge coefficient Cp Specific heat EC Evaporative cooling ECE Evaporative cooling efficiency ETC Evacuated tubular collector g gravitational acceleration H enthalpy , height HSE eat storage efficiency I-beam beam solar radiation Lc characteristic length m mass m o mass flow rate P Pressure PW Paraffin wax Q heat SC Solar chimney T , t Temperature, time TESB,M Thermal energy storage-box, material u velocity V o Volumetric flow rate w Moisture contain Greek letters Inclination Density Width of melting zone Sun altitude angle Latitude angle Hour angle Declination angle Solar radiation angle, 8.00 10.00 12.00 14.00 16.00 18.00 20.00 22.00 24.00 day time (hh:mm) 26 27 28 29 30 31 32 33 34 35 a ir t e m p e ra tu re i n in le t v e rt ic a l c h im n e y -g a p ( c ) distance from TESB 0.25 cm 1.75 cm 3.25 cm 4.75 cm 6.25 cm 8.00 10.00 12.00 14.00 16.00 18.00 20.00 22.00 24.00 Day time (hh:mm) 28 29 30 31 32 33 34 35 36 37 38 39 40 41 a ir t e m p e ra tu re i n m id h e ig h t v e rt ic a l c h im n e y -g a p ( c ) distance from TESB 0.25 cm 1.75 cm 3.25 cm 4.75 cm 6.25 8.00 10.00 12.00 14.00 16.00 18.00 20.00 22.00 24.00 Day time (hh:mm) 28 29 30 31 32 33 34 35 36 37 38 39 40 41 a ir t e m p e ra tu re i n o u tl e t v e rt ic a l c h im n e y - g a p ( c ) distance from TESB 0.25 cm 1.75 cm 3.25 cm 4.75 cm 6.25 cm 8.00 10.00 12.00 14.00 16.00 18.00 20.00 Day time (hh:mm) 0 100 200 300 400 500 600 700 800 900 1000 S o la r R a d ia ti o n R a te b e h in d A c r y li c , 4 5 d e g r e e a n g le 2000 4000 6000 8000 10000 12000 14000 16000 18000 20000 E n e r g y S u m m a ti o n T h r o u g h D u r a ti o n C h a rg e T im e (k J ) 0.00 0.10 0.20 0.30 0.40 0.50 0.60 0.70 0.80 0.90 H e a t S to r a g e E ff ic ie n c y % 11/6/2015 solar radiation energy summation heat storage effeciency Talib K. Murtadha Al-Khwarizmi Engineering Journal, Vol. 12, No. 3, P.P. 80- 98 (2016) 97 Solar chimney tilt angle Heat Storage Effeciency Subscripts a air c Copper g gas I inlet l liquid m melting o outlet s Solid Sl Latent heat of fusion 5. References [1] M. Maerefat, A.P. Haghighi , “ Passive cooling of building by using integrated earth to air heat exchanger and solar chimney”, Renewable Energy 35, PP. 2316-2324, 2010. [2] M. Maerefat, A.P. Haghighi ,“ Natural cooling of stand-alone houses using solar chimney and evaporative cooling avity”, Renewable Energy 35, PP. 2040-2052, 2010. [3] Usama Mustafa , “Using Solar Chimney to Suck Air Through a Wet Ped”, Journal of Engineering and Development, Vol. 15, No.2, PP. 205-213,June-2011. [4] Amin H. Poshtiri, Neda G., “ Comparative survey on using two passive cooling systems, solar chimney- earth to air heat exchanger and solar chimney-evaporative cooling cavity”, World Renewable Congress, PP. 2102-2109, 2011, Sweden. [5] Amr S., Hiroshi Y., Tomonobu G., “Integration of Evaporative Cooling Technique With Solar Chimney to Improve Indoor Thermal Environment in the New Assiut City, Egypt”, International Journal of Energy and Environment Engineering, PP. 1- 15, 2013. [6] MD. M. Rahman, Muhammad M.,” A passive cooling system of residential and commercial buildings in summer or hot season”, Recent Advances in Renewable Energy Source, PP.100-105. [7] Md. F. Rabbi, Mrittunjoy Sarker, “Alternative Room Cooling System”, American Journal of Engineering Research (AJER), Vol. 4, Issue-6, PP. 215-218, 2015. [8] Arkan U.Meko, ”Energy Storage by phase change by using paraffin wax”, MSc, thesis, Machines and Equipment, University of Technology, Baghdad, Iraq, 2004. (Arabic) [9] Helmut E. Feustel , Corina Stetiu,”Thermal Performance of Phase Change Wallboard for Residential Cooling Application”, Environmental Energy Technologies Division, Ernest Orlando Lawrence Berkeley Nationalla Boratory, University of California Berkeley, CA 94720, USA,1997. [10] S. Salam, et al., “Psychometric Analysis for arbitrary dry-gas mixtures and pressres using microcomputer”, ASHRAE Transaction, Part-1,Vol. 92, 1986. [11] Hussain H. Al-Kayiem, Ahmed K. Hussein, Toh Seng Peow, “Investigations of Natural Convective Heat Transfer in Rectangular Thermal Passages“, International Journal of Mechanical, Aerospace, Industrial and Mechatronics Engineering Vol.7, No. 3, PP 159-164,2013. [12] Salah Larbia, Adel El Hella,“Thermo-fluid aspect analysis of passive cooling system case using solar chimney in the south regions of Algeria”, Energy Procedia 36 PP. 628 – 637, 2013. [13] J. Mathur, et al. “ Summer-performance of inclined roof solar chimney for natural ventilation”, Energy and Building 38, PP. 1156-1163, 2006. [14] B. Belfuguais, S. Larbi,“Passive Ventilation System Analysis using Solar Chimney in South of Algeria” World Academy of Science, Engineering and Technology Vol. 58, PP. 26-30, 2011. [15] C. Seytier,et al., “Combined Convective- Radiative Thermal Analysis of an Inclined Rooftop Solar Chimney” Journal of Solar Energy Engineering, Vol. 135 Feb. , 2013. (2016) 80- 98، صفحة 3، العذد12ذجلة الخىارزمً الهنذسٍة المجلمطالب كشاش مرتضى مع مادة ثنائٍة الطىر رٌذ ألخيخٍرسخخذا المذننة الشميٍة اليليٍة يً الخيالدراسة عملٍة ومصفىية رغىة النحاش كخسان حراري طالب كشاش مرتضى * صالححيٍه مجٍذ ** علً داود سلمان*** انجبيؼخ انزكُىنىجُخ / *لسى انهُذسخ انًُكبَُكُخ انجبيؼخ انزكُىنىجُخ خ /*لسى انهُذسخ انكهشويُكبَُكُ*،** * talib_km@yahoo.comانجشَذ االنكزشوٍَ: * hussein_maj@yahoo.comانجشَذ* االنكزشوٍَ: aligaphory@yahoo.comانجشَذ*** االنكزشوٍَ: الخالصة فٍ يذَُخ ثغذاد نكم يٍ انطىل وانؼشض واسرفبع انغشفخ انًجُُخ فٍ ( يزش 1.5*1.5*2خالل هزِ انذساسخ انؼًهُخ، رى ثُبء غشفخ اخزجبس يؼضونخ ثذجى ) أَىاع يٍ ثؼذح جهضد غشفخ االخزجبس 126ثًُُب صًى كال انًذاخٍ انشًسُخ ظًٍ َسجخ غىل انً ػشض انفجىح انهىائُخ ثًمذاس اكجش يٍ انمًُخ انذشجخ 6 نهعىء وػبصلفهُبنك انًذخُخ انؼًىدَخ انضبثزخ راد انخضاٌ انذشاسٌ انًسطخ وانًذهىٌ ثذهبٌ اسىد غُش نًبع ويغهفخ ثسطخ َفبر انًجًؼبد انشًسُخ، ورذسٍُ رىنُذ لىح انطفى، فٍ هزِ وانًىصىنخ ثبنزىانٍ يغ انًذخُخ انضبثزخ نضَبدح اسرفبع انًذخُخ انكهٍ دسجخ 45وهُبنك انًذخُخ انًبئهخ ثضاوَخ دشاسَب، االصيخ ػٍ انًذخُخ صالصخ خضاَبد دشاسَخ ػهً غىل انًذخُخ يغ وجىد فجىرٍ هىاء ػهً غشفٍ انًجًغ نجشَبٌ انهىاء خالنهًب يٍ خالل رىنُذ لىح انطفى خ يٍ االَبثُت انضجبجُخ انًضدوجخ وانًفشغخ يٍ غشَك صَبدح اَزمبل انذشاسح انً انهىاء يغ ربيٍُ يُغ دذوس جشَبٌ هىاء خهف6ٍ كًب رى صساػخ يجًىػ 45انهىاء وانزٍ فٍ داخم كم وادذِ يُهب اَجىة دشاسٌ وثذوٌ دشىح )صشيىسبَفىٌ( دُش رىصم هزِ االَبثُت انًًُهخ ثضاوَخ o انً انُصف انسفهٍ يٍ رذزىٌ ػهً يؼذَُخ يغهىَخ خضاَبد فٍ انًذخُخ انشًسُخ ثبسزخذاو خضٌ دشاسح اإلشؼبع انشًسٍ رى انخضاٌ انذشاسٌ نهًذخُخ انشًسُخ انؼًىدَخ انضبثزخ6 خ نزىنُذ لىح يىاد يزغُشح انطىس نهب لبثهُخ ػهً خضٌ انذشاسح ويذػًخ ثشغىح يؼذَُخ نزذسٍُ انًىصهُخ انذشاسَخ نًبدح انخض6ٌ رسزخذو انذشاسح انًخضوَ داخم انغشفخ، نهسًبح نههىاء انخبسجٍ انُمٍ ثبنذخىل ػجش فزذبد رذزىٌ ػهً دشىِ انطفى ويٍ صى دش انهىاء خالل انًذخُخ انشًسُخ وػًم رخهم ظغػ انزجشَذ أنزجخُش6ٌ أظهشد انُزبئج انؼًهُخ وانزٍ رى وثًشوس انهىاء فىق سطخ انذشىح انًجزهخ يًب َؤدٌ إنً دذوس سهُهىصَخ نهب انمبثهُخ ػهً ايزصبص انًبء، سبػخ يزىاصهخ، دُش إٌ الم فشق دسجخ 24إجشائهب فٍ ثذاَخ ويُزصف انشهش انسبدط، إنً إيكبَُخ خفط دسجخ دشاسح دُض االخزجبس ظًٍ فزشح اخزجبس يسبءا وكزنك ثفشق يًبصم َذذس ػُذ انسبػخ 20:00انسبػخ دسجخ يئىَخ ػُذ 3.5دشاسح ثٍُ دُض االخزجبس وظشف انهىاء انخبسجٍ كبَذ يب َمبسة كًب أظهشد انُزبئج .يٍ ػًش فزشح االخزجبس 15:00 -11:00دسجخ يئىَخ وَذذس خالل 8.5-9.2 صجبدب، ايب اػهً فشق فٍ دسجخ انذشاسح ثًمذاس 03:00 -30.5فؼبنُخ انزجشَذ انزجخُشٌ يذيثهغذ ، فبض فٍ فؼبنُخ انزجشَذ انزجخُشٌفؼبنُخ اسزخذاو انخضٌ انذشاسٌ انشًسٍ، نفزشح يب ثؼذ انًغُت يغ يالدظخ اَخ اكجش يؼذل و، 0.371ظًٍ يؼبيم رذفك خالل انًُظىيخ ( خالل انسبػخ6.187-3.8) ذلؼ، ايب رهىَخ انذُض فكبٌ ثًظًٍ جشَبٌ انهىاء انطجُؼٍ 37.5 kg.hr 36.651).رذفك كزهٍ نههىاء فكبٌ ثًمذاس -1 ) mailto:talib_km@yahoo.comالبريد mailto:hussein_maj@yahoo.com*البريد mailto:aligaphory@yahoo.com***البريد