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International Journal on Power Engineering and Energy (IJPEE) ISSN Print (2314 – 7318) and Online (2314 – 730X) Vol. (5) – No. (4) October 2014 Design and Sizing of Solar Thermal Power Plant (STPP) in Egypt Faten Hosney Fahmy, Hanaa Mohamed Farghally, Ninet Mohamed Ahmed Electronics Research Institute, Giza, Egypt. [email protected], [email protected], [email protected] Abstract - Solar thermal power is a prime choice in developing an affordable, feasible, global energy source that is able to substitute for fossil fuels in the sunbelts around the world. Solar thermal technologies, especially parabolic trough concentrators (PTC) are more convenient for concentrating power station. This paper presents the design and sizing of a parabolic trough solar thermal electric power plant with a net capacity of 1 MW using direct steam generation in one of Suez Suburbs in Egypt. 1 MW electric power generated during the day sunny periods is used to feed a small local grid in a suburb of Suez. A EUROTROUGH solar collector is used, it is found that, the solar field is constituted of 40 collectors grouped in 10 loops, and the estimated solar field area is 22680 m2. Also, this study includes a thermodynamic analysis of a vapor power plant and the Rankine cycle of 1 MW steam power plant is modeled and analyzed. The oil and steam mass flow rates are found to be 2.252 kg/s and 1.4 kg/s respectively. The thermal efficiency of the parabolic trough solar collector (PTSC) is found to be 71% and the total plant efficiency is 28. 3%. Keywords- solar energy, parabolic trough collector, power plant, Rankine cycle. 1. INTRODUCTION Pollution and increasing fuel prices are the main focus for governments today. Therefore, the world must move swiftly towards the clean and economical natural energy sources. Renewable power generation can help countries to meet their sustainable development goals through provision of access to clean, secure, reliable and affordable energy. A new strategy should be applied in the coming decades based on the integration of existing power plants with renewable energy sources, such as solar and wind energy. Reference Number: JO-P-0056 The benefits of solar power are compelling: environmental protection, economic growth, job creation, diversity of fuel supply and rapid deployment, as well as the global potential for technology transfer and innovation [1-3]. The underlying advantages of solar energy are that the fuel is free, abundant and inexhaustible. The total amount of energy irradiated from the sun to the earth’s surface is enough to provide for annual global energy consumption 10,000 times over [4-6]. The main cause of pollution is existing electricity power plants that use huge quantities of fossil fuel. Solar thermal energy (STE) is a technology for harnessing solar energy for thermal energy (heat). Solar thermal collectors are classified by the United States Energy Information Administration as low, medium and high temperature collectors. Low-temperature collectors are flat plates generally used to heat swimming pools. Medium-temperature collectors are also usually flat plates but are used for heating water or air for residential and commercial use. High-temperature collectors concentrate sunlight using mirrors or lenses are generally used for electric power production [68]. Concentrating solar thermal power is a global scale technology that has the capacity to satisfy the energy and development needs of the world without destroying it. Solar thermal power uses direct sunlight, so it must be sited in regions with high direct solar radiation. Among the most promising areas of the world are the SouthWestern United States, Central and South America, Africa, the Middle East, the Mediterranean countries of Europe, Iran, Pakistan and the desert regions of India, the former Soviet Union, China and Australia [9-12]. Concentrated Solar Power (CSP) technologies are usually categorized in three different concepts: Troughs, Towers and Dishes. Among them Parabolic Trough Solar Collector (PTSC) is currently the most proven solar thermal electric 500 International Journal on Power Engineering and Energy (IJPEE) ISSN Print (2314 – 7318) and Online (2314 – 730X) technology. This paper presents the design and sizing of a parabolic trough solar power plant with a net capacity of 1 MW using direct steam generation in Suez Suburb, Suez city in Egypt. Also, the Rankin cycle of 1 MW steam power plant is analyzed and modeled. II. LOCATION DATA One of the Suez Suburbs is selected as the site under consideration; Suez Suburbs are characterized by a rich solar radiation and moderate wind speed. Suez Suburbs are a seaport Suburbs in north-eastern Egypt, located on the north coast of the Gulf of Suez near the southern terminus of the Suez Canal. Its elevation, longitude and latitude are 6 m, 29°58′ N and 32°33′ E respectively. Its low and high temperature is shown in Figure (1). It is observed that, the monthly average low temperature ranged between 8oC and 23oC, and the monthly average high temperature ranged between 19 oC and 36 oC [13]. Suez enjoys sunshine all year, with direct solar radiation which reaches 6 KWh/m2/day. Also, the average wind speed is around 5.5 m/s [14]. Figure (1): Monthly average high and low ambient temperatures for Suez Suburbs. III SYSTEM DESCRIPTION There is a striking resemblance between conventional fossil-fuel power plant and Solar Thermal Power Plant (STPP), the difference lies in the mode of heat generation. While conventional power generation derives its heat source from the burning of fossil fuels, STPP uses radiant energy from the sun. A description of STPP is illustrated in Figure (2). The main elements of the plant are: the solar field (parabolic trough solar collectors), power block which includes heat exchanger (as solar boiler), turbine, condenser, pump and generator. A heat transfer fluid (HTF) is heated as it circulates through the receiver and returns to a series of heat exchangers in the power block where the Reference Number: JO-P-0056 Vol. (5) – No. (4) October 2014 fluid is used to generate high-pressure steam. The steam is then fed to turbine/generator to produce electricity. The spent steam from the turbine is condensed in a standard condenser and returned to the heat exchangers via condensate and feedwater pumps to be transformed back into steam. Condenser cooling is provided by mechanical draft wet cooling tower. Figure (2): Description of solar thermal power plant (STPP). A. Solar Field The solar field is the heat-collecting portion of the plant. The major component of any solar system is the parabolic trough solar collector. It consists of one or more loops of solar collector assemblies (SCA’s), with each loop laid out in parallel. Solar energy collectors are special kinds of heat exchangers that transform solar radiation energy to internal energy of the transport medium. They absorb the incoming solar radiation, convert it into heat, and transfer the heat to a fluid (oil) flowing through the collector. In this study, the solar field is used as a heat source for power plant to generate 1 MW electric power during the day sunny periods to feed a small local grid in a suburb of Suez. PTSC is currently the most proven solar thermal electric technology widely used in generating power for Rankine cycle to produce power for electric generation. Parabolic-trough collectors (PTC) are frequently employed for solar steam-generation because temperature of about 200-300oC can be obtained without any serious degradation in the collector's efficiency. A Parabolic trough collector as shown in Figure (3) consists of a reflecting surface mounted on a reflector support structure having the profile of a parabola. A receiver assembly, comprising a circular 501 International Journal on Power Engineering and Energy (IJPEE) ISSN Print (2314 – 7318) and Online (2314 – 730X) Vol. (5) – No. (4) October 2014 absorber tube with suitable selective coating and enclosed in a concentric glass envelope, is centered along the reflector focal line [15]. Figure (4): Shell and tube heat exchanger configuration Figure (3): Parabolic trough solar collector. B. Heat Exchanger (as solar boiler) A shell and tube heat exchanger is the most common type of heat exchanger in oil refineries and other large chemical processes, and is suited for higher-pressure applications. As its name implies, this type of heat exchanger consists of a shell (a large pressure vessel) with a bundle of tubes inside it. One fluid runs through the tubes, and another fluid flows over the tubes (through the shell) to transfer heat between the two fluids. The set of tubes is called a tube bundle, and may be composed of several types of tubes: plain, longitudinally finned, etc. Two fluids, of different starting temperatures, flow through the heat exchanger. One flows through the tubes (the tube side) and the other flows outside the tubes but inside the shell (the shell side). In this study, oil is used as a heat transfer fluid (HTF) is flows inside the shell, while the saturated steam which is the working fluid is flows through the tubes. . Figure (4) illustrates the composition of a shell and tube heat exchanger. Heat is transferred from one fluid to the other through the tube walls, either from tube side to shell side or vice versa [16]. Reference Number: JO-P-0056 A counter flow heat exchanger is the most efficient flow pattern. It leads to the lowest required heat exchanger surface area because the log mean temperature drop is the highest for a counter flow heat exchanger. Figure (5) illustrates the inlet and outlet temperatures of the two fluids (oil and steam) in a counter flow heat exchanger. Figure (5): The terminal temperature of oil and steam fluids in a counter flow heat exchanger. a. Selection of Heat Transfer Fluid Parabolic trough solar collectors utilize an HTF that flows through the receiver to collect the solar thermal energy and transport it to the power block. The type of HTF used determines the operational temperature range of the solar field and thus the maximum power cycle efficiency that can be obtained. Table 1 shows the available HTF options. Synthetic oil such as a mixture of biphenyl and diphenyl oxide (Therminol VP-1) is selected one. It is pumped through each heat collection element (HCE) tube. The heated HTF is pumped back to the power plant, where it becomes the 502 International Journal on Power Engineering and Energy (IJPEE) ISSN Print (2314 – 7318) and Online (2314 – 730X) thermal resource for steam generation in the power cycle. Within the power cycle portion of the plant, the hot HTF is piped through a series of counter flow heat exchangers that transfer the thermal energy from the HTF to a feedwater stream to produce steam. This steam serves as the working fluid in a conventional Rankine power cycle [11]. Table 1 Heat transfer fluids with application in solar parabolic trough fields [17] b. Selection of the Working Fluid The selection of the optimum working fluid that can be used with the solar operated Rankine cycle depends on of staging many criteria and the most important of which is the maximum temperature of the cycle. Other criteria include the following [18-19]: 1. High molecular weight to reduce the nozzle velocity and thus enable the use of a low speed turbine without the necessity of the expander (the nozzle velocity is inversely proportional to the square root of the molecular weight). 2. Reasonable pressure corresponding to the boiling temperature of the fluid. High pressure requires careful sealing to avoid leakage. 3. Dry expansion, i. e positive slope of the vapour saturation curve on the T-S diagram, to assure that all the expansion states in the turbine exist on the superheat region. 4. High latent heat to give high specific consumption of the working fluid and therefore reduce the size of the plant for a given power output. 5. Fluid compatible with the seals, lubricant oil, and materials of the various components. 6. Thermal and chemical stability at the temperature range of operation. Reference Number: JO-P-0056 Vol. (5) – No. (4) October 2014 7. Inexpensive, non-corrosive, non- flammable, and non-toxic fluid. 8. Thermodynamic properties that lead to the highest possible efficiency of the system at the selected temperature range of the cycle. 9. Reasonable pressure at the condensing temperature (usually about 50 oC). Very low pressure in the condenser requires special case of sealing. Table 2 compares the properties of some suggested working fluids for the Rankine cycle. In this study, we chose water as a working fluid. Water as working fluid is very convenient compared to organic fluids. It is inexpensive, non-toxic, nonflammable, has low global warming potential and zero ozone depleting potential, chemically stable and low viscosity (and thus lower friction losses and higher heat exchange coefficients). However, a watertreatment and a deaerator must be integrated with the power plant to feed the cycle with highpurity deionized, oxygen free water. Organic fluids may be relatively toxic and is more expensive than water (excluding cost of pretreatment). Table 2 Some suggested working fluids for the Rankine cycle [11]. C. Turbine Steam enters the turbine at a high temperature and high pressure state. The expansion of the steam as it moves from high pressure to lower pressure converts the potential energy (in the form of pressure) to kinetic energy by imparting its momentum to the turbine blades, thereby causing the connected shaft to rotate. The mechanical work created by the rotating shaft is converted to electrical energy through a generator. 503 International Journal on Power Engineering and Energy (IJPEE) ISSN Print (2314 – 7318) and Online (2314 – 730X) D. Electromechanical Energy Transfer (Generator) The steam turbine drives a generator, to convert the mechanical energy into electrical energy. Typically this will be a rotating field synchronous machine. E. Condenser The exhaust steam from the low pressure turbine is condensed to water in the condenser which extracts the latent heat of vaporization from the steam reducing the pressure dramatically to near vacuum conditions thus increasing the pressure drop across the turbine enabling the maximum amount of energy to be extracted from the steam. The condensate is then pumped back into the heat exchanger as feedwater to be used again. It goes without saying that condenser systems need a constant, of cooling water and this is supplied in a separate circuit from the cooling tower which cools the condenser cooling water by direct contact with the air and evaporation of a portion of the cooling water in an open tower. F. Pump The pump being a component in a Rankine cycle which is needed to raise the pressure of the liquid leaving the condenser to the pressure of the steam generator. Since pump work is inversely proportional to the fluid density, less work is required to pressurize a liquid than a vapour or gas. The ideal pump raises the pressure of a liquid in an adiabatic, reversible process. IV. RANKINE CYCLE OF PARABOLIC TROUGH SOLAR THERMAL POWER PLANT The Rankine cycle is the fundamental operating cycle of all power plants where an operating fluid is continuously evaporated and condensed. The selection of operating fluid depends mainly on the available temperature range. Rankine cycle used in thermal power plants deals on heating up water in constant pressure while changing its phase. The thermodynamic analysis of a Rankine cycle for the steam power plants based on the first and second laws of thermodynamic. All four components (turbine, condenser, pump and heat exchanger) that make up ideal Rankine cycle are steady-flow devices, and thus all four processes that make up the Rankine cycle can be analyzed as steady-flow processes. The kinetic and potential energy changes of water are small relative to the heat Reference Number: JO-P-0056 Vol. (5) – No. (4) October 2014 and work terms, are thus neglected [20]. Schematic representation of an ideal Rankine cycle and the temperature – specific entropy (T– s) diagram for the thermodynamic processes of a standard irreversible Rankine cycle is shown in Figure (6) [21]. The working fluid undergoes the following series of internally reversible processes: Process 1–2: Isentropic expansion of the working fluid through the turbine from saturated vapor at state 1 to the condenser pressure. Process 2–3: Heat transfer from the working fluid as it flows at constant pressure through the condenser with saturated liquid at state 3. Process 3–4: Isentropic compression in the pump to state 4 in the compressed liquid region. Process 4–1: Heat transfer to the working fluid as it flows at constant pressure through the heat exchanger to complete the cycle. Figure (6a): Schematic representation of an ideal Rankine cycle. Figure (6b): T-S diagram of an ideal Rankine cycle. The net power delivered by the Rankine cycle is the difference between the turbine power and the magnitude of the pump power. One of the significant advantages of the Rankine cycle is that the pump power is usually quite small compared with the turbine power. This is indicated by the work ratio, wt / wp, which is large compared with one for Rankine cycle. As a result, the pumping power is sometimes neglected in approximating the Rankine cycle net power output. 504 International Journal on Power Engineering and Energy (IJPEE) ISSN Print (2314 – 7318) and Online (2314 – 730X) V. MODELING OF SOLAR THERMAL POWER PLANT (STPP) In this section we will introduce the model of solar field; heat exchanger and power block Rankine cycle . A. Solar field modeling The design of a solar field is influenced by the industrial process, the technical characteristics of the selected collectors, the location of the plant and the climate data. The solar field consists of a number of parabolic trough collector loops connected in parallel to each other. Each loop consists of several solar collector assemblies (SCA) in series, in one or several rows. The solar collector efficiency can be determined from its characteristic using the solar irradiance. The solar collection efficiency (ηth) is defined as the ratio of the rate of useful thermal energy leaving the collector, to the useable solar irradiance falling on its aperture area. Simply stated collector efficiency and is calculated as follows [22-25]: th = oilCp (Tout −Tin) Qu Qu m = = Qi Ib Aa Ib Aa Q abs = A a η opt I dn (2) The nominal temperature increase in a collector of the EUROTROUGH type is calculated using the following equation. Q t − Q p Q (3) oil =C m oil Q oil p oil (4) Where: Qt power lost by a collector [W]; power absorbed by the oil [W/grd]; C p oil oil specific heat at constant pressure [J/kg K]; m oil is mass flow rate for a collecting loop [kg/s]; Pt is thermal power [W]. The number of collectors for a loop (N) is calculated with the following relation: N= ∆Tloop (5) ∆Tcolec Where, ∆Tloop is the heat jump in one loop of collectors, ∆Tcolec is the heat jump in only one collector. The calculation of the number of parallel loops (M) in the solar field can be described by: M Where, Aa is the absorbed area of the collector (m2), ηopt is the optical efficiency and Idr solar irradiance falling on collector aperture (W/m2) ∆ T colec = Qp Qoil (1) Where, the useful energy Qu is the difference between the energy absorbed at the receiver tube, and the energy losses at the receiver, Qi is the incident energy. Vol. (5) – No. (4) October 2014 = P t . 10 6 Q t − Q p (6) N oil C p oil (Tpb inlet − Tpb outlet ) Poil = m (7) p thermal = p oil steamgen (8) Where, Tpb inlet Tpb outlet , are the inlet and outlet temperatures of the power block, steam generation efficiency. steamgen is the B. Heat exchanger modeling The HTF used is synthetic oil, namely Therminol VP-1, which is a mixture of biphenyl and diphenyl oxide and stable at temperatures below 400°C. The temperature of the HTF increases of around 160°C, from 70°C to 230°C. Also, the condensed water entered the heat exchanger at 50 oC and exit as saturated steam at 200 oC. The fundamental equation for heat transfer across a surface of heat exchanger is given by [26]: power generated by a collector [W]; Reference Number: JO-P-0056 505 International Journal on Power Engineering and Energy (IJPEE) ISSN Print (2314 – 7318) and Online (2314 – 730X) steam C p steam ( t 2 − t 1 ) = m oil c p oil (T1 − T2 ) Q=m Where Q Btu/h); (9) =0 Q cv g( Z1 − Z 2 ) = 0 heat transferred per unit time (kJ/h, C p oil specific heat of oil; C p steam specific heat of steam (kJ/kg-ºK, Btu/lb- 2 2 V 1− V 2 =0 2 ºF); Therefore, m steam mass flow rate of steam; m oil Wt = h1 − h2 m mass flow rate of oil; T1 inlet shell side fluid (oil) temperature; T2 outlet shell side fluid (oil) temperature; t1 inlet tube side fluid (water ) temperature; t2 outlet tube-side (steam) temperature. C. Rankine cycle mathematical model The principal work and heat transfers of Rankine cycle solar power plant are illustrated in Fig. 6. In subsequent discussions, these energy transfers are taken to be positive in the directions of the arrows. The unavoidable stray heat transfer that takes place between the plant components and their surroundings is neglected here for simplicity. Kinetic and potential energy changes are also ignored. Each component is regarded as operating at steady state. Using the conservation of mass and conservation of energy principles together with these idealizations, we develop expressions for the energy transfers shown on Fig 6 beginning at state 1 and proceeding through each component in turn. The mathematical model of the Rankine cycle units in Fig. 6 is introduced as follows: a. Turbine: Vapor from the heat exchanger at state 1, having an elevated temperature (200 oC) and pressure (1.55 MPa), expands through the turbine to produce work and then is discharged to the condenser at state 2 with relatively low pressure (0.012 MPa). Neglecting heat transfer with the surroundings, the mass and energy rate balances for a control volume around the turbine reduce at steady state to give [27-31]: 2 2 V1−V2 h1 −h2 + 0 = Qcv −Wt +m +g(Z1 −Z2) 2 Reference Number: JO-P-0056 Vol. (5) – No. (4) October 2014 (10) (11) Where, h1 (obtained from steam table) and h2 are the specific enthalpies of the working fluid at the inlet and outlet of the turbine respectively [32]. denotes the mass flow rate of the working m m W t fluid (steam), and is the rate at which work is developed per unit of mass of steam passing through the turbine. As noted above, kinetic and potential energy changes are ignored. h2 is obtained according to the following equation: h2 = h f + x 2 h fg (12) The quality of stage 2 (x2) is obtained from the following equation: x2 = S2 − S f Sg − S f (13) Where, Sf , Sg are obtained from steam table and they are corresponding to the liquid and vapor entropy at turbine outlet respectively [32 ]. b. Condenser: In the condenser there is heat transfer from the vapor to cooling water flowing in a separate stream. The vapor condenses and the temperature of the cooling water increases. The cooling water enters the condenser at 15 oC and exits at 50 oC. At steady state, mass and energy rate balances for a control volume enclosing the condensing side of the heat exchanger give as: Q out = (h 2 − h 3 ) m (14) 506 International Journal on Power Engineering and Energy (IJPEE) ISSN Print (2314 – 7318) and Online (2314 – 730X) Where, h3 is the specific enthalpy of the working fluid at the outlet of the condenser. It is corresponding to 50 oC of saturated liquid at condenser output and it is obtained from steam Q out is the rate at which energy is m table [32]. transferred by heat from the working fluid to the cooling water per unit mass of working fluid passing through the condenser. This energy transfer is positive in the direction of the arrow on Figure (6). c. Pump: The liquid condensate leaving the condenser at state 3 is pumped from the condenser into the higher pressure heat exchanger (boiler). Taking a control volume around the pump and assuming no heat transfer with the surroundings, mass and energy rate balances given as: W p (15) = h4 − h3 m h4 is the specific enthalpies of the working fluid W p is the rate of m at the outlet of the pump, power input per unit of mass passing through the pump. This energy transfer is positive in the direction of the arrow on Fig. 6. h4 can be obtained according to the following two equations: h4 = h3 + W p / m h4 = h3 + W p / m = h3 + 3 ( p4 − p3 ) (16) (17) d. Heat Exchanger: The working fluid completes a cycle as the liquid leaving the pump at state 4, heat exchanger feedwater, is heated to saturation and evaporated in the heat exchanger. Taking a control volume enclosing the heat exchanger tubes carrying the feedwater from state 4 to state 1, mass and energy rate balances is given as follow: Q in = h1 − h4 m Reference Number: JO-P-0056 (18) Where Q in Vol. (5) – No. (4) October 2014 is the rate of heat transfer from m the energy source into the working fluid per unit mass passing through the heat exchanger. e. Thermal Efficiency: A measure of the effectiveness of an energy conversion device is its thermal efficiency .The thermal efficiency gauges the extent to which the energy input to the working fluid passing through the heat exchanger is converted to the net work output, it is defined as the ratio of the cycle net work to the heat supplied from external sources. Thus, by using Equations (12), (13), and (18) we can express the ideal Rankine-cycle thermal efficiency in terms of cycle enthalpies as: = /m /m −W (h1 − h2) − (h4 − h3) W t p = /m Q (h1 − h4) in (19) The net work output equals the net heat input. Thus, the thermal efficiency can be expressed alternatively as: η= /m /m /m −Q Q Q in out = 1 − out /m /m Q Q in in = 1− (h 2 − h 3 ) (h 1 − h 4 ) (20) (21) Another parameter used to describe power plant performance is the back work ratio, or bwr, defined as the ratio of the pump work input to the work developed by the turbine. The back work ratio for the power cycle of Fig. 6 is expressed as: bwr = /m (h 4 − h 3 ) W p = /m (h 1 − h 2 ) W t (22) The mass flow rate is obtained from the following formula: = m Wcycle ( h 1 − h 2 ) − ( h 4 − h 3) (23) Q Alternatively, out can be determined from an energy rate balance on the overall vapor power plant. At steady state, the net power developed equals the net rate of heat transfer to the plan: 507 International Journal on Power Engineering and Energy (IJPEE) ISSN Print (2314 – 7318) and Online (2314 – 730X) W cycle = Wt − Wp (24) Vol. (5) – No. (4) October 2014 Table3: Data of the solar field Or W cycle = Q in − Q out (25) =Q −W Q out in cycle (26) VI. RESULTS AND DISCUSSIONS The obtained results of sizing and analysis of STPP Will be presented and discussed in the following subsections. 6.1 Sizing of a Solar Field of Parabolic Trough Collector The sizing of parabolic trough collector solar field is based on the lowest ambient temperature of Suez suburb during the sunny period witch is around 8 oC. The sizing of a solar field consists of determining the number of collectors necessary for a loop of the solar field and the number of necessary loops so as to obtain the pressure and temperature conditions of the fluid when exiting the solar field. The temperature increase of the fluid between the entrance and exit points determines the number of collectors per loop, whereas the thermal power that has to be supplied by the entire solar field determines the number of loops in the solar field. The selected model is EUROTROUGH with an overall length of 100 m, and opening width of 5.67 m. It is found that, the solar field size required to produce 1 MWe electricity is an array of a Eurotrough parabolic trough collector consists of a parallel 10 loops each loop is a string of 4 collectors and the total required area is 22680 m2. Table 3 presents the technical characteristics of solar field. Also, table 4 presents the parabolic trough collector system specifications. Table4: Parabolic trough collector system specifications [22] 6.2 Heat Exchanger Equation 9 is used to calculate the mass flow rate m of heat transfer fluid oil , also the parameters of the two fluids passing through the heat exchanger are illustrated in table 5. Table 5: Heat exchanger data 6.3 Rankine Cycle According to the specified temperatures of heat transfer fluid and working fluid, the obtained parameters of RC considered in this study are given in table 6. Reference Number: JO-P-0056 508 International Journal on Power Engineering and Energy (IJPEE) ISSN Print (2314 – 7318) and Online (2314 – 730X) Table 6: Calculated parameter of RC power plant Vol. (5) – No. (4) October 2014 [3] K. Azizian, M. Yaghoubi, R. Hesami, P. Kanan, Design Analysis for Expansion of Shiraz Solar Power Plant to 500 kW Power Generation Capacity, World Renewable Energy Congress, 2011-Sweden, 8-13 May, Linkoping, Sweden, pp. 3897-3904. [4] Vahab Hassani, Henry W. Price, Modular Trough Power Plants, Proceedings of Solar Forum 2001 Solar Energy: The Power to Choose APRIL 21-25, 2001, Washington, DC, pp. 1-7. [5] Adel El-Menchawy, Hesham Bassioni, Abdel-Aziz Farouk, Photovoltaic Systems in Existing Residential Building in Egypt, International Journal of Scientific & Engineering Research Vol. 2, No. 7, 2011, pp. 1-11. [6] Abolhassan Mokhtari, Mahmood Yaghoubi, Thermo-Economic Design of a Parabolic Solar Collector, Proceedings of the Middle East Mechanical Engineering Conference MEMEC 2007, November 4-7, 2007, Manama, kingdom of Bahrain, pp. 1-8. 7. CONCLUSION The parabolic trough solar collector is one of the main technologies currently used in the solar electric power generation plants. This paper presents the design and sizing of a parabolic trough solar thermal power plant with a net capacity of 1 MW using direct steam generation in one of Suez Suburbs in Egypt to feed a small local grid in this Suburb during the day sunny period. The thermal cycle uses a heat transfer fluid (synthetic oil) to transfer energy from the collector field to a Rankine steam cycle via a heat exchanger. 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