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Thermodynamics, economic and environmental analyses of a hybrid waste–solar thermal power plant

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Abstract

A novel hybrid configuration of solar parabolic trough collectors–waste incineration power plant was recently analyzed energetically in Denmark. Taking into account the true meaning of sustainability which is environmental friendliness and cost-effectiveness, and considering the existing gap of knowledge on the thermodynamic performance aspects of this hybrid system, this work conducts a thorough thermodynamic and sustainability analysis of this power plant. The main aim is to give a clear picture of the main advantages and any possible shortcomings of the hybrid power plant. For this purpose, the performance of the system is simulated for an entire year of operation under realistic solar irradiation fluctuations. The energy performance indices of the system are quantified and discussed. The exergy assessment of the hybrid cycle is accomplished, and the main sources of exergy destruction and economic losses are identified. The results show that the steam generator and the turbine cause the largest rates of irreversibilities of 36% and 20.8%. The environmental benefits and the overall cost of energy production of the system are calculated and compared to some other alternative power plants. In addition to the consistency of electricity production, the LCOE of the hybrid power plant decreases by 67% in comparison with the solar power plant. Comparing the system with a natural gas-fired power plant in terms of CO2 emission, it is shown that the hybrid system leads to less 74.5 thousand tonnes of CO2 emitted over an entire year.

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Abbreviations

A :

Area (m)2

D :

Diameter (m)

\(E_{{{\text{CO}}2{\text{e}}}}\) :

Amount of CO2e emission (–)

\(\dot{E}_{\text{gen}}\) :

Electricity power (kW)

E λ :

Emission of different types of greenhouse gases (–)

Ex:

Exergy (kW)

GWPλ :

Global warming potential of greenhouse gases (–)

h :

Enthalpy (kJ kg−1)

\(h_{\text{c}}\) :

Convective heat transfer coefficient (kJ m−2K−1)

\(I{{\$ }}_{{\rm t}}\) :

Installation fees (\({{\$ }}\))

\({\text{IAM}}\) :

Incidence angle modifier (–)

K :

Thermal conductance (kJ m−1K−1)

\({\text{LHV}}\) :

Low heat value (kJ kg−1)

\(M{{\$}}\) :

Maintenance fees ($)

\(\dot{m}\) :

Mass flow rate of the first preheating line (kg s−1)

\(\dot{m}_{\text{PTC}}\) :

Mass flow rate solar field (kg s−1)

\(\dot{m}_{\text{s}}\) :

Total mass flow rate of steam (kg s−1)

Nu:

Nusselt Number (–)

\(O{{\$ }}_{{\rm t}}\) :

Operation fees (\({{\$ }}\))

P :

Pressure (kPa)

Pr:

Prandtl number (–)

\(q_{{12{\text{Conv}}}}^{ '}\) :

Convective heat transfer between SHTF and the absorber (kJ m−1)

\(q_{{23{\text{Cond}}}}^{ '}\) :

Conductive heat transfer through the absorber wall (kJ m−1)

\(q_{{34{\text{Rad}}}}^{ '}\) :

Heat transfer from the absorber to the glass envelope (kJ m−1)

\(q_{{3{\text{SolAbs}}}}^{ '}\) :

Solar Heat absorbed by the absorber (kJ m−1)

\(q_{{45{\text{Cond}}}}^{ '}\) :

Conductive heat transfer through the glass envelope (kJ m−1)

\(q_{{56{\text{Conv}}}}^{ '}\) :

Convective Heat transfer from the glass envelope to the atmosphere (kJ m−1)

\(q_{{56{\text{Rad}}}}^{ '}\) :

Radiative Heat transfer from the glass envelope to the atmosphere (kJ m−1)

\(q_{{57{\text{Rad}}}}^{ '}\) :

Radiative Heat transfer from the glass envelope to the sky (kJ m−1)

\(q_{{5{\text{SolAbs}}}}^{ '}\) :

Solar absorption in the glass envelope (kJ m−1)

\(q_{\text{cond}}^{ '}\) :

Heat rejected in condenser (kJ kg−1)

\(q_{{{\text{Cond}},{\text{bracket}}}}^{ '}\) :

Conductive heat transfer through the bracket support (kJ m−1)

\(q_{\text{si}}^{ '}\) :

Solar irradiation per receiver length (kJ m−1)

\(\dot{Q}_{\text{cond}}\) :

Rate of heat rejected in condenser (kW)

\(\dot{Q}_{\text{WI}}\) :

Heat released in waste incineration process (kW)

T :

Temperature (K)

y :

The flow rate of steam withdrawals form the first turbine (–)

y′:

The flow rate of steam withdrawals form the second turbine (–)

\(\dot{W}\) :

Work production rate (kW)

\({{\$ }}_{{\rm MSW}}\) :

Annual cost of the municipal waste ($)

C, H, O, N, S:

Mass fraction of carbon, hydrogen, oxygen, nitrogen and sulfur

\(\alpha_{\text{abs}}\) :

Absorptance of the absorber

α env :

Absorptance of the envelope

\(\varepsilon\) :

Emittance

\(\varepsilon x\) :

Exergy efficiency

\(\varepsilon_{1}^{ '}\) :

Shadowing factor

\(\varepsilon_{2}^{ '}\) :

Tracking error

\(\varepsilon_{3}^{ '}\) :

Geometry error (mirror alignment)

\(\varepsilon_{4}^{ '}\) :

Dirt on mirrors

\(\varepsilon_{5}^{ '}\) :

Dirt on collector

\(\varepsilon_{6}^{ '}\) :

Unaccounted factor

\(\eta\) :

Efficiency

\(\eta_{\text{abs}}\) :

Effective optical efficiency at absorber

η env :

Effective optical efficiency at the glass envelope

\(\eta_{\text{gen}}\) :

Electricity generation efficiency

ξ :

Exhaust gas volume

\(\eta_{\text{WI}}\) :

Thermal efficiency of waste incineration plant

τ :

Transmittance

A:

Air

abs:

Absorber

c:

Cover

ci:

Cover inner

CFWH:

Closed feed water heater

ch:

Chemical

conv:

Convection

CT:

Cooling Tower

De:

Destruction

env:

Envelope

FG:

Flue gas

G:

Generator

gen:

Generation

HC:

Hybrid cycle

\({\text{HPT}}\) :

High-pressure turbine

\({\text{IPT}}\) :

Intermittent pressure turbine

\({\text{LPT}}\) :

Low-pressure turbine

MC:

Mixing chamber

MSW:

Municipal solid waste

Net:

Net

OFWH:

Open feed water heater

opt:

Optical

P:

Pump

PH:

Preheater

PTC:

Parabolic trough collector

Rad:

Radiation

RC:

Rankine cycle

s:

Steam

SF:

Solar fluid

SG:

Steam generator

Sol:

Solar

ST:

Steam turbine

WI:

Waste incineration

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  1. Department of Energy Technology, Aalborg University, Esbjerg, Denmark

    A. Arabkoohsar & M. Sadi

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Arabkoohsar, A., Sadi, M. Thermodynamics, economic and environmental analyses of a hybrid waste–solar thermal power plant. J Therm Anal Calorim 144, 917–940 (2021). https://doi.org/10.1007/s10973-020-09573-3

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