Thermodynamic study of an EFGT (externally fired gas turbine) cycle with one detailed model for the ceramic heat exchanger

Mello, Paulo Eduardo Batista de; Monteiro, Deiglys Borges

doi:10.1016/j.energy.2012.01.003

Cited by 32 publications

(19 citation statements)

References 11 publications

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“…However, drifted ash and particles from the furnace can block the narrow passages of the heat exchanger, and also the low thickness of the plates making the metallic plate-type heat exchanger unsuitable as HTHE. To overcome the temperature limitation, ceramic platetype HTHE were proposed by Schulte-Fischedick et al [106], Mello and Monteiro [107]. Moreover, the MGT plate-type recuperator can be placed after the HTHE at lower temperature and ash contamination levels as an air pre-heater as demonstrated experimentally by Traverso et al [98,99].…”

Section: Hthe Different Designsmentioning

confidence: 96%

Externally fired gas turbine technology: A review

2015

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Section: Hthe Different Designsmentioning

confidence: 96%

Externally fired gas turbine technology: A review

2015

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“…The overall efficiency for the B and E configurations is depicted in Figure for three values of pressure ratios: r p = 5, 15, 20. The following parameters have been selected: η 0 = 0.84 and M = 0.29 for the solar collector and ε H = ε L ≡ ε = 0.90, T L = 300 K, and γ = 1.4 for the heat engine . From Figure , we see that η = η ( τ ) always has a parabolic shape that is independent of r p for E. We stress that the interval for τ giving positive efficiencies for B rapidly gets narrower for larger pressure ratios.…”

Section: Some Particular Limit Cases: External Irreversibilitiesmentioning

confidence: 96%

“…We show in Figure the efficiency as a function of τ for the B, E, IT, and IC configurations when both the external and internal irreversibility sources are considered together. We take reference parameters for all the irreversibility sources: ε t = 0.89, ε c = 0.84 , ε r = 0.85 , and ε H = ε L ≡ ε = 0.90 , ρ H = ρ L = 0.98, ξ = 0.02, T L = 300 K, and γ = 1.4 . Parameters for the solar collector are as those in the previous section: η 0 = 0.84 and M = 0.29.…”

Section: Fully Irreversible System: Optimization With Respect To the mentioning

confidence: 99%

Maximum overall efficiency for a solar-driven gas turbine power plant

Orgaz

Medina

Hernández

2012

Int. J. Energy Res.

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SUMMARY A general model for an irreversible solar‐driven Brayton multi‐step heat engine is presented. The model incorporates an arbitrary number of turbines (Nt) and compressors (Nc) and the corresponding reheating and intercooling processes; thus, the solar‐driven Ericsson cycle is a particular case where Nt, Nc → ∞. For the solar collector, we assume linear heat losses, and for the Brayton multi‐step cycle, we consider irreversibilities arising from the non‐ideal behavior of turbines and compressors, pressure drops in the heat input and heat release, heat leakage through the plant to the surroundings, and non‐ideal couplings of the working fluid with the external heat reservoirs. We obtain the collector temperatures at which maximum overall efficiency ηmax is reached as a function of the thermal plant pressure ratio, and a detailed comparison for several plant configurations is given. This maximum efficiency is obtained in two cases: when only internal irreversibilities are considered and when both internal and external irreversibilities (which corresponds to the fully irreversible realistic situation) are simultaneously taken into account. Differences between both situations are stressed in detail. In the fully irreversible realistic case, it is possible to perform an additional optimization with respect to the pressure ratio, ηmax∗. In particular, this double optimization leads to a valuable increase in efficiency (between 34% and 65%) for a plant with two turbines and two compressors compared to the simple solar‐driven one‐turbine one‐compressor Brayton engine. Copyright © 2012 John Wiley & Sons, Ltd.

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“…This is done by substituting Eqs. (39)- (41) in Eqs. (42)- (45) provided that the ratios T 3 =T L ; T 1 =T L , and T x =T L can be expressed in terms of the mentioned temperature and pressure ratios, and the parameters associated to losses.…”

Section: Modeling Subsystems: Solar Plant and Combustion Chambermentioning

confidence: 98%

“…So, some parameters (see Table 2) were assumed from those of similar facilities owned by Abengoa Solar in the same location (optical efficiency, concentration ratio, and design point irradiance) [7,46] and other were taken from standard values in the literature [18,28,40,41].…”

Section: Model Validationmentioning

confidence: 99%