可再生能源生产淡水和电力外文文献

Contents lists available at ScienceDirect Sustainable Energy Technologies and Assessments journal homepage Development of an innovative cogeneration system for fresh water and power production by renewable energy using thermal energy storage system B Ghorbania R Shirmohammadib M Mehrpooyab aFaculty of Engineering Modern Technologies Amol University of Special Modern Technologies Amol Iran bDepartment of Renewable Energy and Environment Faculty of New Sciences Received in revised form 19 September 2019 Accepted 7 November 2019 Corresponding author at Renewable Energies and Environment Department Faculty of New Sciences and Technologies University of Tehran Tehran Iran E mail address mehrpoya ut ac ir M Mehrpooya Sustainable Energy Technologies and Assessments 37 2020 100572 2213 1388 2019 Published by Elsevier Ltd T value and then it decreases Then using a single objective genetic al gorithm and a two objective optimization energy and economic structure of the integrated structure IS were conducted 11 The solar energy ratio used to provide the heat supply of the entire IS is equal to 24 2 6 Ashouri et al 12 developed a Kalina cycle with a solar thermal heat source A storage tank is used to save energy The pro portion of solar energy used to supply heat to the entire IS in this paper is 69 In the IS the overall electrical exergy effi ciency is 5 24 and the total thermal exergy effi ciency is 62 In an integrated solar combined cycle plant using parabolic collectors is introduced and analyzed 13 The results indicate that in the proposed solar power plant average effi ciency is 60 9 Ahmadi et al 14 used solar col lectors to heat the Isfahan steam power plant located in Isfahan pro vince in Iran In order to pre heating the input water which is entered into the recovery boiler seven diff erent scenarios were used In the scenario of replacing the solar collector instead of all high pressure boilers the energy effi ciency is increased by 45 and the exergy effi ciency is increased by 43 91 Maleki et al 15 developed a co production system for water and power using a photoluminescence system wind turbine fuel cell and desalination system They improved the IS using economic analysis and system optimization In order to provide hydrogen production in this IS the electrolyzer was used for the production of fresh water from the RO desalination system Ahmadi et al developed many new methods of power generation 16 17 They developed an integrated cogeneration structure with the molten car bonate fuel cell and CO2Brayton cycle Multi objective optimization was used to evaluate the newly developed structure 18 Due to the water and energy crisis improving the effi ciency of thermal systems and heat recycling along with the use of the water desalination process has attracted the attention of many researchers in recent years Javadi and et al modifi ed the structure of the Bandar Abbas steam power plant They used solar collectors to supply input heat organic Rankine cycles for auxiliary power generation cycles and thermal desalination cycle to replace the condenser 19 Piadehrouhi et al 20 developed a Nomenclature AaSurface area of the concentrator m2 AcSurface area of the receiver aperture m2 AwCavity internal area of receiver m2 QsPower reached on the surface of the dish W IsBeam solar radiation reached to concentrator surface W m2 QrPower reached to the receiver W QuUseful thermal power reached to the receiver W QlPower lost in the receiver W QlkPower lost from receiver through conduction W QlcPower lost from receiver through convection W QlrPower lost from receiver through radiation W NulNusselt number TwReceiver temperature C TaAmbient Temperature C GrlGrash of number gGravitational acceleration 9 806m s2 LDiameter m hc Convection heat transfer coeffi cient between the absorber and air and ambient air W m2K KThermal conductivity of the ambient air W m K KtClearness index of a day GonExtraterrestrial radiation incident GscSolar constant 1367 W m2 cGeometrical concentration ratio H0Extraterrestrial solar radiation on a horizontal surface Hd Daily diff use solar radiation IsHourly global solar radiation on the horizontal surface Id Hourly diff use solar radiation on the horizontal surface ItHourly global solar radiation on the tilted surface ms Heating steam mass fl ow rate hs Specifi c enthalpy of the heating steam LlogLocal geographical longitude D Distillated mass fl ow rate kg s CP Specifi c heat capacity RaEntrainment ratio of the steam ejector Ex Exergy rate kW m Mass fl ow rate kg s T0Temperature of the dead state K si specifi c entropy kJ kg K ex Specifi c exergy kJ kg h0 Specifi c enthalpy at reference state kJ kg s0 Specifi c enthalpy at reference state kJ kg K n iMole rate of the ith stream mole kg xiMole fraction of thejth component in the stream ei0Standard chemical exergy of the component in the stream kJ mole inInput outOutput Q Rate of heat transfer kW W Rate of shaft work kW h Specifi c enthalpy ex Exergy Effi ciency Greek Letters iActivity factor Refl ectance Land factor of un shading Transmittance Absorptance Intercept factor Effi ciency 1Tilt angle of cavity Radian Coeffi cient of thermal expansion 1 C vKinematic viscosity m2 s Declination Latitude sSunset hour angle eff Eff ective infrared emittance of cavity cCavity surface emittance Stefan Boltzmann constant 5 67 10 8W m2K4 Hour angle Subscripts and superscripts exExergy phPhysical chChemical oOptical rReceiver cCollector Abbreviation MED Multi eff ect desalination SDCSolar dish collector ISIntegrated structure PCMPhase change material B Ghorbani et al Sustainable Energy Technologies and Assessments 37 2020 100572 2 hybrid power production system comprising molten carbonate fuel cell solar parabolic dish Oxy fuel and Rankine power generation cycles equipped with CCS unit and liquefaction process The system was analyzed through the exergy approach and the overall exergy effi ciency of the system was attained 63 19 Khoshgoftar Manesh et al 21 conducted a multi objective ther moeconomic analysis of a steam power plant with MSF sweating water The 3000MW nuclear power plant was used to supply heat They used to pinch and exergy analyses to modify the network heat exchanger Peng et al 22 developed two ISs of the steam power plant driven by solar The exergy analysis of the two ISs disclosed that the share of exergy destruction of solar collectors is 62 81 and 64 84 respec tively Blumberg et al 23 conducted the exergoeconomic assessment for two cases of power generation in power plant The F Class has an electric effi ciency of 58 7 and H Class has an electrical effi ciency of 60 The exergy analysis of these two structures exposed that the production of F Class power is 56 and for the steam cycle and the production of H Class power is 58 3 according to the exergy effi ciency of the steam cycle Akbari et al 24 developed a new hybrid system utilizing geothermal energy as a heat source and contains a Kalina cycle a LiBr H2O heat transformer and a water desalination system for generating power and pure water Ansari et al 25 developed an in tegrated power plant for the production of water with a MED system The IS has a capacity of 24 000 tons per day for freshwater production and the GOR is 8 81 for this 7 stage desalination system Meratizaman et al 26 presented several integrated power and heat generation systems for heavy fuel oil gasifi cation for use in fuel cell and desali nation system They used sensitivity exergy and economic analyses to evaluate the ISs 27 Ghorbani et al 28 developed a natural gas fi red power plant integrated with two regenerative boilers in which para bolic solar dish collectors a replaced with the one of the boilers The thermal energy was stored by PCM in a storage tank They concluded that presence of an auxiliary boiler to deliver constant load for the whole day is vital They also concluded that the new confi guration declined the energy effi ciency slightly yet the exergy effi ciency of the power plant increased Ghorbani et al 29 investigated an integrated structure includes photovoltaic thermal collector ejector refrigeration cycle and phase change material storage energy system to generate and store refrigeration using the Hysys Transys and Matlab software In order to evaluate the system the energy and exergy analyses were employed and the overall thermal and total exergy effi ciencies of the system were obtained with the amount of 60 51 and 50 84 One of the major problems of power plants in the world is carbon dioxide emission from the heat source due to the consumption of fossil fuels and natural gas A signifi cant portion of the heat in the condenser of the power plant is also wasted or requires large water sources for cooling Extensive studies have been carried out to replace high tem perature solar collectors to supply input heat to the plant to reduce CO2 emissions and natural gas consumption Extensive studies have also been carried out to utilize the heat lost in the condenser for water de salination Supplying heat for integrated freshwater and power systems during the night is one case that has not been studied In this paper the process of thermal desalination and solar collectors are dynamically used in steam power plants along with the thermal phase change system in a specifi c climatic condition An integrated power generation cycle has been developed with the aid of the solar collector as a heat supplier The heat should be cooled at high temperature causing many en vironmental problems thus it is used to sweeten the seawater using a multi eff ect desalination method Process description Fig 1 demonstrates an integrated power and heat generation from a solar power plant The coding is developed in Matlab software to si mulate the solar collectors and Hysys simulator and Matlab program ming language are employed for simulating the system of the steam power plant and desalination system The desired climatic information in this article is related to city of Bushehr located in the south of Iran which is extracted by the Transys software Fig 2 illustrates the IS of power and fresh water production equipped with the solar dish collector This IS can produce 1063 MW of net power and 8321kg s of fresh water Table 1 depicts the mole fraction of each stream in the IS This table presents that the oil used in the oil cycle has a molar ratio of 0 2462 for BiPhenyl and 0 7528 for diPH Ether Table 2 depicts the temperature pressure and mass fl ow rates of the IS Table 3 depicts the Fig 1 The block diagram of the IS B Ghorbani et al Sustainable Energy Technologies and Assessments 37 2020 100572 3 specifi cations of the equipment in the IS The highest power capacity is generated by ST100 turbine with 601 MW and the lowest power is generated in the ST103 turbine with 107 7 MW Solar dish collectors Absorbing part is the main component of the solar dish collector system The action of absorbing solar radiation and transferring heat to the fl uid is done by this section The solar collector must have good heat transfer properties and thermal conductivity as well as the high coef fi cient of absorption 30 31 It must be stable against high tempera tures and have low emission coeffi cient Moreover it must be resistant to internal and external corrosion The collector s effi ciency depends entirely on the condition and material which are used to make it Solar parabolic plates are considered to be on two axes of the sun to reach the required temperature in the absorption section which is 1230 K The power of each dish can be obtained from the following relationships The the total amount of energy lost from the absorber of the dish can be obtained by means of following equation in whichQlkis equal to the heat lost during conduction in the absorber QlcandQlrare equal to the conduction and radiation heat lost at the absorber aperture QI ASolarenergyincidentonthedishconcentratoraperture ssa 1 cos Opticalefficiency 0 2 QQ Radiantsolarenergyfallingonthereceiver rs 0 3 Grg TT L GrashnumberbasedonlengthL lwa 32 4 h 1 16771 0762sin 11 0 8324 5 NuGrTTAAh 0 106 4 256 NusseltnumberbasedonlengthL llwacw s1 30 18 1 6 hNu K L Theconvectiveheattransfercoefficient cl 7 Qh ATT Convectiveheatlossthroughthereceiveraperture lccwwa 8 AA1 1 1 1 Effectiveinfraredemittanceofthecavity effccw 9 AAc Entranceapertureareaofthereceiver ca 10 QA TT Radiativeheatlossthroughthereceiveraperture lrc effwa 44 11 QQQQHeatlossesfromthereceivertothesurroundings llklclr 12 QQQUsefulenergycollected url 13 The amount of radiation from above the Earth on a simple surface is calculated as follows 32 GGn 10 033cos 360 365 onsc 14 where n refers to a specifi c day of the year and G is the solar constant 1367 W m2 The value ofGonon the horizontal plane is obtained by the following equation 32 H G 243600 coscossin 180 sinsin on s s 0 15 n23 45 sin 360 284 365 16 cos tantan s 1 17 N 2 15 s 18 N is equal to the monthly average amount of the maximum sunlight duration KThas been calculated analogously to the presented proce dure in the Ref 32 HH Kn1365 T0 19 The amount of total solar radiation on the horizontal surface can be Fig 2 The process fl ow diagram of the IS Table 1 The molar ratio of some streams in the IS StreamWaterSodium ChlorideBiPhenyldiPH Ether Oil 1000 24620 7528 1001000 1301000 201 2081000 2090 97680 023200 2130 94950 050500 214 2201000 221 Brine 0 92920 070800 227 Desalinated Water 1000 228 Sea Water 0 96100 039000 B Ghorbani et al Sustainable Energy Technologies and Assessments 37 2020 100572 4 obtained from the following Eq 32 hn nn L 15 9 87sin 2360 81 364 7 53cos 360 81 364 1 5sin 360 81 364 4 120 6012 log 20 is defi ned as the hour angle The transmitted solar radiation on the horizontal surface can be calculated as follows 32 I H 24 coscos sincos d ds s s 2 360 s 21 Hd is defi ned as the daily solar radiation on the horizontal surface 32 H H K KK KK K KK K 0 990 17 1 1882 2729 473 21 86514 648 0 170 75 0 540 6320 750 8 0 20 8 d T TT TT T TT T 2 34 22 The heat supply structure of solar dish collector system is shown in red in Fig 2 The Oil1 stream is containing BiPhenyl and diPH Ether with a mole fraction of 24 62 and 75 38 respectively The stream is introduced at 600 C and the input pressure of 200 kPa into the E100 heat exchanger and with the temperature of 283 7 C and the pressure of 180 kPa is exited The solar collector system along with the auxiliary boiler transfer 3740MW heat to the E100 heat exchanger evaporator of power plant Fig 3 depicts the plot of solar radiation throughout the year per hour in Bushehr Fig 4 depicts the plot of ambient temperature changes throughout the year per hour in Bushehr Steam power plant The line 100 with temperature and pressure of 275 8 C and 7205 kPa enters into the E100 heat exchanger evaporator of the steam power plant and exchange heat with the solar collector cycle line 101 at 590 C and 7200 kPa enters into the ST100 steam turbine and gen erate output power of 601MW Part of line 102 exited from ST100 is introduced into the ST101 steam turbine and the rest is fed to the E101 heat exchanger to preheat the stream entered into the evaporator The line 103 at 392 9 C and 1705kPa enters into the ST101 steam turbine generates 170 3 MW of power The stream 107 exited from the ST101 is divided into two parts About 84 of this stream enters into the ST102 steam turbine and the rest is combined with the stream exited from the E101 heat exchanger and entered into the E102 heat ex changer Stream 108 at 321 6 C and 926 9kPa is introduced into the ST102 steam turbine and produces power with the amount of 199 7 MW Similarly part of the streams exited from the steam turbine at 221 4 C and 3 447 kPa is fed into the ST103 steam turbine and produces 107 8 MW of power About 98 47 of the output stream from the ST103 steam turbine is sent into the E104 and the rest is entered into the E109 for preheating The stream of 114 which is at 165 2 C and 183 3 kPa is delivered to the E104 and provides the required heat for the desalination system The stream of 119 at 63 C and 183 3kPa enters into the E105 condenser so that it exchanges heat to the sea Multi eff ect desalination system Multi eff ect desalination MED systems take advantage of heat energy and are categorized in thermal processes The system is con sidered as the fi rst and foremost method of pure water production from Table 2 Specifi cations of temperature pressure and mass fl ow rate of streams in the IS StreamTemperature C Pressure kPa Mass fl ow kg s StreamTemperature C Pressure kPa Mass fl ow kg s 100275 87204 91595 7200122 080 01009 4 101590 07200 01595 720182 229 12883 9 102392 91704 71595 720262 926 12883 9 103392 91704 71403 020356 329 96171 6 104392 91704 7192 620468 025 96171 6 105392 91704 71250 020562 926 11009 4 106392 91704 7153 020662 926 11874 6 107321 6926 91250 020762 980 01009 4 108321 6926 91050 020868 025 92812 8 109321 6926 9200 020968 025 93358 8 110221 4344 71050 021063 422 92812 8 111221 4344 71020 021156 326 16171 6 112221 4344 730 021264 522 16171 6 113165 2183 31020 021364 522 19530 4 114165 2183 31004 421464 522 12754 4 115165 2183 315 621564 522 16776 0 11663 0183 31004 421660 519 12754 4 11738 76 91004 421756 322 76171 6 11838 8386 11004 421861 018 76171 6 11947 1386 11004 421961 018 712947 6 120117 4183 315 622061 018 72753 7 121117 4344 715 622161 018 710193 9 12248 2344 71020 022256 397 36171 6 123392 91704 7345 622361 018 71874 6 124177 81704 7345 622461 018 7879 1 125176 7926 9545 622561 319 17441 8 126131 0926 9545 622660 918 78320 9 12788 7344 71595 722752 115 78320 9 12889 47496 01595 722825 0101 318514 8 129171 47349 01595 722956 397 318514 8 13025 0101 31542 923056 397 36171 6 13140 7101 31542 923156 397 36171 6 Oil1600 0200 03602 5Oil3283 7250 03602 5 Oil2283 7180 03602 5 B Ghorbani et al Sustainable Energy Technologies and Assessments 37 2020 100572 5 seawater operating under vacuum and condense seawater vapors in which an ej