 Open Access
 Total Downloads : 161
 Authors : Nagendra Kumar
 Paper ID : IJERTV6IS050521
 Volume & Issue : Volume 06, Issue 05 (May 2017)
 DOI : http://dx.doi.org/10.17577/IJERTV6IS050521
 Published (First Online): 23052017
 ISSN (Online) : 22780181
 Publisher Name : IJERT
 License: This work is licensed under a Creative Commons Attribution 4.0 International License
Design and Optimisation of Solar Thermal Organic Rankine Power Cycle using Parabolic Collector
Nagendra Kumar
Assistant Professor & Head of Department Mechanical Engineering
KLSIET Bijnor Uttar Pradesh in India
Abstract – In the present investigation, The design and optimisation of solar thermal organic Rankine power cycle using parabolic collector has been done. Parabolic trough collector to be used such as absorber tube, glass cover and reflector surface has been designed for direct normal solar radiation. Concentration collecting device is selection for dilute form of solar energy. The studies are mainly focussed keeping in view the objective like design of parabolic trough collector for Patna city (Bihar), selection of the working fluid to be used the organic Rankine cycle (ORC) and the design and optimisation of organic Rankine power cycle. Working fluid nPentane which has suitable thermodynamic properties and Ecofriendly has been selected here and used. From the studies carried out it has been formed that npentane ORC have batter performance in the temperature ranging from 600C to 900C. The ORC is optimised at a constant condenser temperature of 350C and the evaporator temperature was varied from 650C to 950C. The maximum efficiency of the cycle was formed to be 4.10% at saturation and 4.76% when evaporator temperature is superheated.

INTRODUCTION
The parabolic collector device is large amount of thermal energy source, the optimization power of the organic rankine cycle at the heat source parabolic trough collector. Cylindrical parabolic trough collector has been designed for the Patna city. Parabolic trough power plants use parabolic trough collectors to concentrate the direct normal solar radiation on a tubular receiver. Large collector fields supply the thermal energy, which is used to organic rankine cycle via the counter flow heat exchanger. The working fluid used is npentane. The selection of working fluid suitable for the ORC has been done[1]

DESIGN OF PARABOLIC TROUGH COLLECTOR.
2.1Solar Radiation Geometry;
The latitude of a location is the made of angle by the radial line joining the location to the centre of the earth. The slope angle made by the plane surface with the horizontal axis. The declination angle is the made by the line joining the centre of the sun. The declination angle varies from the maximum value and minimum value depend the time condition, the maximum value of +23.450on 21 June and minimum value of 23.450 on 21 December.
(in degrees) (284+n)]..(2.1.1) Where n is the number of day in the year.
The hour angle is an angular measurement of time and is the equivalent to 150 per hour. The hour angle also varies to +1800 to 1800 the time measuring it from noon based on local apparent time (LAT).the positive value at morning time and negative value at evening time.
It can be shown that the equation,
Cos = sin (sin cos + cos cos cos sin ) + cos (cos cos cos sin cos sin) + cos sin sin sin …. (2.1.2)
Therefore the tilted factor
…… (2.1.3)[2]
2.2Thermal Analysis of Cylindrical Parabolic Collector Thermal analysis may be discuss of a cylindrical parabolic collector, the thermal analysis same types of the flat plate collector an energy balance on the absorber yield following equation.
qu=Assql. (2.2.1) Where,
qu= rate of useful heat gain,
Aa= effective area of the aperture of the cylindrical parabolic collector
S = Solar beam radiation per unit effective aperture area absorber
ql=rate of heat loss from the absorber.
The similar equation of a rate of heat loss and that equation can be written in items of an overall loss coefficient. ( ). (2.2.2)
Where = overall loss coefficient
= area of the absorber surface,
= average temperature of the absorber surface,
= temperature of the surrounding air, We combine equation,
]…. (2.2.3) [2]
2.3Design Equation of the Collector Efficiency.
Concentration Ratio,
C =
C= …. (2.3.1) Where,
C = Concentration ratio W = the aperture width
D0= Outer diameter of the absorber L = length of the aperture
Parabolic Collector Efficiency Factor, ),
F= ….. (2.3.2)
Where = parabolic collector efficiency factor, U1 = Overall heat loss coefficient.
D0= Outer diameter of the absorber,
hf= heat transfer coefficient.
Collector Heat Removal Factor,( ,
= [1exp( …..(2.3.3)
Thus, the useful heat gain rate
qu= [S ( ] ….( 2.3.4)
The collector efficiency
= (2.3.5)
In this case of the parabolic collection only direct normal beam radiation condition following,
If the parabolic collector efficiency, than the diffuse radiation is zero
= .. (2.3.6) [2]
Time (LAT) 
Beam irradiation W/ 
Efficiency % 
0708 
641.2 
29.24 
0809 
707.8 
31.90 
0910 
752.8 
33.90 
1011 
828.3 
35.62 
1112 
760.3 
35.90 
1213 
817.6 
35.37 
1314 
800.8 
34.65 
1415 
738.1 
33.03 
1516 
668.2 
30.38 
Table. 2.3.1 Relationship between full day efficiency of beam irradiation & Time
Figure.2.3.1 Collector Efficiency vs Time
3DESIGN & OPTIMIZATION OF ORGANIC RANKINE CYCLE

Feed pump are working condition following the working fluid inter the feed pump to increase fluid pressure. If feed pump work produce
=)….. (3.1)

The condenser are working condition following to rejected heat to the environment, it is normally to working fluid. =m )… (3.2)

Heat exchanger to transfer heat from heat source to the following working fluid. The heat source heat is collect to the solar thermal energy collected by the parabolic trough collector. Heat received the collector,
= m .. (3.3)

Turbine are working condition following the work conversion. Turbine work is
=m ). (3.4)

the organic rankine cycle efficiency is define as the ratio of the total work done of a system to heat supplied in the heat exchanger is called the organic rankine power cycle. It is denoted by .
The Total work done of a system = turbine work pump work
= m ( – ) (3.5)
= … (3.6)
= (3.7)
The pump work is very small
= = .. (3.8) [3]
The Carnot cycle Efficiency,
= 1– ………………………………………….. (3.9) [4]
Where. = Maximum Temperature C
= Minimum Temperature C And Overall Efficiency,
= x ………. (3.10) [4]
4 – RESULT & DISCUSSION

Optimize organic rankine cycle the system has been optimized and following figure no.6.4 shows the depended overall ORC efficiency with respect to evaporator temperature at saturation condition, the optimize efficiency is 4.10% and 85Â°C
Figure.4.1 Overall ORC efficiency vs Evaporator teperature at saturation
condition

Optimize organic rankine cycle the system has been optimized and following figure no.6.8 shows the depended overall ORC efficiency with respect to evaporator temperature at superheated condition, the optimize ORC efficiency is 4.76% and 85Â°C
Figure.4.2.Overall ORC efficiency vs Evaporator temperature at superheated condition
5CONCLUSION
It is observed that from design & optimization analysis of solar thermal organic rankine power cycle using parabolic trough collector. .

Solar energy conversation to power through ORC is feasible and commercially used also.

From the literature it is inferred that the challenges still exist required proper Selection of working fluid.

Cylindrical parabolic collector concentrating solar and storage thermal energy at a high temperature.
4 The Cylindrical parabolic collector efficiency is 46.66% at inlet fluid temperature (60Â°C) ORC system.
5. ORC system is optimized for a maximum efficiency of 4.10% saturation condition and for 4.76% superheated condition at a condenser temperature of 35Â°C and evaporator & superheated temperature of 85Â°C
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Sotirios Karellas, & Andreas Schuster*(2008) Supercritical Fluid Parameters in Organic Rankine Cycle Applications. Vol. 11 (No. 3), pp. 101108, Germany

S P sukhame & J N Nayak 3rd edition (2008) Solar Energy Principle of thermal collection and storage Tata Megraw Hill

Cheng Eng Cong, Sanjayan Velautham &Amer Nordin Darus (2005) Solar Thermal Organic Rankine Cycle as a Renewable Energy Option vol No.20,6877

P K NAG fourth edition (2008) Engineering Thermodynamic, Tata Megraw Hill

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Matthew Roesle, Volkan Coskun & Aldo Steinfeld (2011) Numerical Analysis of Heat Loss from a Parabolic Trough Absorber Tube with Active Vacuum System. Vol. 133 / 0310151

Angad Singh Panesar (2012) A study of organic Rankine cycle systems with the expansion process performed by twin screw machines, Ph.D. Thesis. City University London