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Thermal Optimization of Solar Biomass Hybrid Cogeneration Plants

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Thermal Optimization of Solar Biomass Hybrid Cogeneration Plants Journal of Scientific & Industrial Research Vol. 65 April 2006, pp. 355-363 Thermal optimization of solar biomass hybrid cogeneration plants Anuradha Mishra 1, M N Chakravarty 2 and N D Kaushika 2, * 1IEC College of Engineering and Technology, Greater Noida 2School of Research and Development, Bharati Vidyapeeth College of Engineering, Paschim Vihar, New Delhi Received 10 February 2005; accepted 25 January 2006 Thermal optimization and performance matching of subsystems in solar biomass hybrid plant are investigated. The plant incorporates solar collector field, multiple fuel boiler, steam turbine, deaerator and economizer units. The solar field consists of line focus parabolic trough collectors. The thermal model is used for comparative study of various variations of parabolic trough collectors; LS3, Euro Trough (ET) and Duke solar excel over others. The matching of the output heat Qu and the temperature to the feed water conditions indicate that ET is the most suitable for the application; its inlet temperature requirement also matches the energy balance of the deaerator. Keywords : Biogas, Cogeneration, Hybrid power plant, Parabolic trough collector Introduction Cogeneration Plant Configuration India produces abundant quantities of agro residues A solar biomass hybrid plant would incorporate (rice husk, coffee husk, cashew shells, groundnut solar collector field, multiple fuel boiler, steam shells) and wastes (distillery waste). Co-generation of turbine, deaerator and economizer units (Fig. 1). The process heat and power is an important energy saving solar field consists of concentrating collectors. Three approach. It is particularly suitable for paper, solar thermal collector technologies (parabolic trough, chemicals, textiles, food and petroleum refining parabolic dish and solar tower) have reached the stage industries. Two configurations are possible, the 1 of maturity but the parabolic trough collectors are topping cycle and the bottoming cycle . In the topping most advanced and commercially available. There- cycle, waste heat from power generation is used to fore, parabolic trough solar collector (PTSC) based produce process steam. In the bottoming cycle, fuel is plant is considered. Luz Company (capacity 354 burnt to produce process steam and the waste heat is MW), California, USA has used PTSC power plants used to produce power. In India, effective utilization in solar electricity generating systems 4. The heat of biomass fuels and wastes in co-generation plants generating collectors, heat transportation systems and has vast potential (over 3500 MW). Several biomass heat delivery units such as heat exchanger provide based co-generation plants have been proposed and 2,3 pressurized hot water as boiler heat. In cogeneration tested . However, scattered availability of biomass plant, there is relative cogeneration of steam and often results in short supply of raw material at some process heat. This study considered 2.5 MW of industrial co-generation plant sites. Hybridization of electricity and 25 TPH of process steam at 145°C and these biomass fuels with conventional fuels would a pressure of 2.5 atm for the plant configuration of adversely affect the financial incentives usable by topping cycle based on multifuel boiler fueled by them. Proposed integrated power project being setup biogas generated from suitable biomass. The flue gas at Mathania in Jodhpur district would use combined is used for boiler combustion process. In solar thermal cycles based on conventional gaseous fuels and solar hybridization, solar heat may be used for preheating energy. This paper investigates engineering design the boiler feed water. Line-focus parabolic trough optimization of solar biomass hybrid cogeneration collectors have, received steadily increasing attention plants. _______________ for medium and high temperature heat production; *Author for correspondence temperature of about 300°C can be obtained without 5,6 E-mail: [email protected] any serious degradation in collector efficiency . The 356 J SCI IND RES VOL 65 APRIL 2006 Fig. 1 Solar biogas hybrid cogeneration plant collector consists of a reflector of parabolic section To (t) = Tr (t)FR + Ti (t)[ 1− FR ] … (3) with a cylindrical surface and selectively coated evacuated tube absorber placed at the focal line. The Energy balance across the boiler is given as: reflector focuses beam radiation onto the absorber if ' the Sun is in the plane containing the focal axis and Qm=η B( Q BIO + QQ u + w ) … (4) the vertex line of the reflector. Oil (Hytherm 500) is used for heat retrieval from the collector and its QBIO is the energy generated from the biogas as a fuel transport to the successive units. and added to the boiler is given as: Thermal Model QBIO = m BIO ×c BIO … (5) Let there be ‘n’ parallel loops of parabolic trough 3 cBIO = 5391 kCal/Nm collectors in the solar field. The energy balance equation for the quantity of heat produced by each The fraction of energy generated, solar heat loop of parabolic trough solar collector can be component ( Q′u), in the collector field is supplied as expressed as, heat input to the boiler through the heat exchanger. It can be expressed as Qu= Q opt − Q L … (1) ' Qu= f4 Q u … (6) The heat may be extracted from the receiver by fluid flowing through receiver tube. The rate of solar heat Q′u is transported to the boiler by the flow of output may be expressed as follows: pressurized hot water and may be expressed as Q' = mf S( T − T ) … (7) Qu= mcTt wwo{ () − Tt i () } … (2) u1 wpT (,)1 1 2 o The output temperature of fluid [ To(t) ] based on Similarly, the feed water heat component, Qw, from energy balance may be written as 4,7,8 economizer to the boiler can be expressed as MISHRA et al : THERMAL OPTIMIZATION OF SOLAR BIOMASS COGENERATION PLANTS 357 Q= mS( T − T ) … (8) Table 1 Thermo physical parameters used in solar collectors w w() p2, T 2 2 4 LS-3 Euro Duke Qu and To are obtainable from Eqs 1 and 2 and T2 Trough Solar and T4 may be specified as operational parameters of 2 the plant. Total heat input to the turbine in the form of Area, m 545.0 817.0 235.0-313.0 superheated steam from the boiler is given as Aperture, m 5.76 5.76 5.0 Length, m 99.0 150.0 49.0-65.0 Q = mS (T −T ) … (9) HCE diam, m 0.07 0.07 0.07 m s( p3 ,T3 ) 3 1 Average focus 1.71 1.71 1.49 The energy balance across the turbine is distance, m Optical efficiency 0.80 0.80 0.80 Qm= Q d + Q g + Q p … (10) Inner radius of the 20 33 30 receiver tube, mm The total heat from the turbine to the deaerator, Qd, is Outer radius of the 22.5 35 35 given by receiver tube, mm Qm=(1 − fS ) T … (11) Radius of the glass 35 58 58 d2 spT (,)55 5 envelope, mm T5 is obtainable from the energy balance across the Emmisivity of the 0.19 0.15 0.24 deaerator and boiler feed pump as follows receiver tube m(1− fS ) TmS + fTmS = T 2spT (,)55 5 wpT (,)3a a a wpT (,)44 4 economizer and the heat transfer fluid. The minimum … (12) temperature requirement of the economizer is 160°C for normal operation. So the oil temperature at all Qg is heat equivalent of power at generator terminal and may be expressed as times should be more than 160°C. The flash point of the boiler is 210°C. Therefore, the maximum tempe- Eg rature of the oil entering the boiler should not be more Q = … (13) g than 210°C. Hence, the input temperature constraint ηg× η T × η M for the plant is 160-210°C. The mass flow rate (MFR) Eg is the electrical generation capacity at the is to be chosen according to this constraint for all the generator. Net power generation, En, is given by collectors. Daily variation of To as a function of MFR is shown in Fig. 2. According to the above-mentioned E c E n= g × g … (14) constraint, the optimum MFR for LS3, ET and Duke Solar is 1 kg/s, 1.7 kg/s and 0.7 kg/s respectively. Results and Discussion Furthermore, the variability of minimum and maxi- Several types of PTSCs are now commercially mum values of To during the year round variation for available namely LS1, LS2, LS3, Euro Trough (ET), the optimum mass flow rates is shown in Fig. 3. The 9 Industrial Solar Technology (IST) and Duke solar . A variations in To are characteristics of hot water comparative study of these collectors is desirable for pressurized up to 35 atm, which is of the right order system optimization. For this purpose, the perfor- of magnitude for boiler feed water. The daily mance parameters such as receiver output tempera- efficiency of the collectors at the optimum MFR is ture, useful heat output, collection efficiency and investigated; it is found that the efficiency of LS3 overall heat loss coefficient have been considered. collector is comparable to the ET collector (Fig. 4a). From the Luz solar collectors, LS3 is the modified The efficiency of Duke Solar is very low as compared form of LS1 and LS2. The commercial availability of to others. The diurnal variability of Qu for all the IST collectors is not so common. This study therefore months of year with the optimum MFRs and a system investigates the relative performance of LS3, ET and containing four loops of collector (Fig. 4b) show that Duke solar collectors. Thermo physical parameters the ET collector excels over other collectors. used in the computations of their performance To simulate the performance, plant (Fig. 1) was parameters is given in Table 1.
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