Solar Spain Receiver

8/18/2019 Solar Spain Receiver

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S olar Facilities for the European Research Area

Solar Receiver ModelingCentral Receiver

SFERA II 2014-2017 , Solar Receiver Modeling, 26/06/14, Odeillo

CNRS PROMES


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• Introduction

• Tubular receiver

• Volumetric receiver

• Solid particle receiver

• Conclusion

Outline


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Introduction

Higher efficiency power cycles pursued to reduce LEC High-temperature receivers

Challenges:

• Development of optimized geometric designs

• High temperature materials• Heat-transfer fluids

• Maximize absorptance, minimize heat loss

• High reliability over thousands of thermal cycles

• Direct vs. indirect heating

No intermediateheat exchange

Ability to store theheat transfer media


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C E

T T h f T F Q

QQ

DNI field

amb Rconvconv Rview

in

lossinth

4

Receiver thermal efficiency:

Introduction


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Introduction

C E

T T h f T F Q

QQ

DNI field

amb Rconvconv Rview

in

lossinth

4

Receiver thermal efficiency:


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Introduction

Tubular receiver Volumetric receiver

Cavity receiver

Solid particle receiver


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Solhyco (SOlar HYbrid power and COgeneration plant)

• Developed by DLR (Germany)

• Profiled multi-layer tube (Alloy/Copper/Alloy)

Ref.: P. Heller, Solar-Hybrid Power and Cogeneration Plants, Final public report, 2011

Tubular receiver

Standard tube Multi-layer tube

Temperature profile

Concentrated solar irradiation


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• 40 metallic tubes of 2.5 meter length arranged in a cavity and connected in parallel

• Wire-coil insert to enhance the heat transfer

• Unpressurized quartz window implemented to reduce thermal radiation and convection losses

Ref.: P. Heller, Solar-Hybrid Power and Cogeneration Plants, Final public report, 2011

Tubular receiver

Wire-coil insert


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Model:• FEMRAY (Finite Element Mesh Ray Tracing) to estimate the heat flux distribution• Creation of a 3D-finite-element model (FEM)• Absorber tubes and cavity considered, distributor and collector neglected• Thermal heat transfer in the tubes : Nusselt-correlation• Thermal radiation between tubes, walls and environment taken into account• Convection losses neglected and cavity walls considered adiabatic• Receiver designed for a pressure drop of 70 mbar in the tubes

Ref.: P. Heller, Solar-Hybrid Power and Cogeneration Plants, Final public report, 2011L. Amsbeck (2008), Development of a tube receiver for a solar-hybrid microturbine system. In: Proceedings of the 14th Biennial CSPSolarPACES Symposium 2008, Las Vegas, NV (USA)

Tubular receiver



11/41Ref .: B. Grange, Modélisation et dimensionnement d’un récepteur solaire à air pressurisé pour le projet PEGASE, PhD, 2012

• Developed by CNRS-PROMES (France)• Manufacturing of the absorber module (50 x 200 x 400 mm) using HIP

process to weld Copper and Incoloy• Whole absorber: 1.2 m 1.2 m, 16 modules (8 per stage)• Cavity of 1 m deep• Heliostat field not adapted to develop a conical cavity• Absorber modules designed for a pressure drop of 150 mbar

Tubular receiver

PEGASE (Production of Electricity from GAs and Solar Energy)

Existing field

Optimal field


12/41Ref .: B. Grange, Modélisation et dimensionnement d’un récepteur solaire à air pressurisé pour le projet PEGASE, PhD, 2012

Tubular receiver


• Assessment of the heat flux distribution with SolTrace

• Analysis of the first impact of the concentrated sunlight

• Reflection and radiation calculated in the net radiationmethod

• Steady-state analytical model

• 3 temperatures for each element

• Losses considered- Through aperture (convective and radiative)- Back of the cavity/absorber

• Finite element discretization of the receiver

• Heat transfer coefficient and pressure drop in the tubescorrelated with experimental results


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Ref .: B. Grange, Modélisation et dimensionnement d’un récepteur solaire à air pressurisé pour le projet PEGASE, PhD, 2012

A.M. Clausing (1981), An analysis of convective losses from cavity solar central receivers, Solar Energy 27, No. 4, pp. 295-300S. Paitoonsurikarn and K. Lovegrove (2011), Numerical investigation of natural convection loss from cavity receivers in solar dishapplications, Transactions of the ASME 133(2)

Methods to calculate the convective coefficient :

• Clausing model

- Power gained by the air slipping out of the cavity:

- Convective heat loss power:

- Bayley correlation:

- with T c verifiyng P a=P c

• Correlation of S. Paitoonsurikarn

Tubular receiver


0,41 0,130,0196. .Pr L L Nu Ra

.conv S L

air

h L Nu

3. . ..

air réc amb S L

air air

g T T L Ra

,.Pr air p air

air

c

3

1

.cos .ib

S i i ii

L a L

,. . . .a air air ouv p air c amb P u S c T T

. .c conv cav réc réf P h S T T

2

130,082. .Pr . 0,9 2, 4. 0,5.réc réc

amb amb

T T Nu Gr

T T


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Ref.: R. Siegel, J.R. Howell, Thermal radiation heat transfer, 3rd edition, Chapter 7Catalog of View factors: http://www.thermalradiation.net/tablecon.html

2

1

2

1

2

1

2

1121221 ,,,11

l k j i

l k jil k ji y xG

y y x x F

• J. R. Howell law:

• Net-radiation method (2 spectral bands):

Radiosity balance

S S inc S i i i ij j

j

J F J

4 IR réc IR IR

i i boltz i i ij j j

J T F J

Tubular receiver

nette inci i i ij j i

j

P S F J J


0,3 3m m 3 m


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Ref.: B. Grange, Modélisation et dimensionnement d’un récepteur solaire à air pressurisé pour le projet PEGASE, PhD, 2012

Tubular receiver


• Convective transfer in the tubes

( )éch glob réc moyi i i i i P h S T T ,

.

éch s e ii i air

i p air

P T T

m c

rés nette éch perduei i i i P P P P • Residual power calculation

• Radiative balance in the infra-red spectral band with the new metal temperatures

• Iterative loop: the thermal balance is reached when , 1 ,réc réc

i n i nT T critère

• By introducing a time interval t, the residual power is converted into heat in the metal

, 1 ,,.

résréc réc i

i n i n réci p réc

P t T T m c

Iterative method


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Tubular receiver



Results of ray-tracing software SolTrace


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Tubular receiver



Current study

• Increasing the number of tube’s row in the depth of the module absorber to decrease the pressure drop

• Enhance the air alimentation in the module

Numerical simulation (FLUENT) using UDF for heat transfer and pressure drop in the tubes

• Comparing simulated results with experimental data (module absorber and whole receiver)

Perspective


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The main goals for the optimization of the volumetric receiver concept are:

• Achievement of high heat transfer coefficients to ensure small temperature differences between gas andabsorber

• Low manufacturing costs in comparison to other receiver types (e.g. nitrate salt or sodium receiver)

• Minimize the emissive losses by having a temperature distribution of the absorber rising from theentrance region of the solar radiation to the inner region of the volumetric receiver

• Under development since the 1980s

• Porous structure irradiated by concentrated sunlight

• Two types: open-loop (no pressurization) and closed-loop (pressurization)

Description

Ref.: A.L. Avila-Marin (2011), Volumetric receivers in Solar Thermal Power Plants with Central Receiver System technology: A review, Solar Energy85, pp. 891-910

Volumetric receiver


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Ref.: J. Karni, A. Kribus (2001), The “Porcupine”: A Novel High-Flux Absorber ForV olumetric Solar Receivers, JSEE, Vol. 120, pp. 85-95

• Developed by Weizmann Institute (Israel)

• Volumetric cavity receiver

• Array of Pin-Fins , constructed with elongated heat transfer elements (Porcupine ‘quills’), implanted in abase plate

• Quills are made of ceramic tubes or rods and the base is made of a relatively soft ceramic insulation board

• Orientation of the pins is designed to match the mean direction of the incoming radiation

• Spacing between them is determined so that the desired radiative flux penetration into the depth of theabsorber is obtained

Volumetric receiver

DIAPR (Directly Irradiated Annular Pressurized Receiver)


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Ref.: I. Hischier (2009), Heat Transfer Analysis of a Novel Pressurized Air Receiver for Concentrated Solar Power via Combined Cycles, J. ofThermal Science and Engineering Applications, Vol.1, pp. 6

Volumetric receiver

Pressurized air receiver of ETH (Switzerland)

• Annular reticulate porous ceramic (RPC) bounded by two concentric cylinders

• CPC at the aperture to boost the solar concentration ratio and reduce the aperture size andreradiation losses

• Absorbed heat is transferred by conduction, radiation, and convection to the pressurized air flowingacross the RPC

• Outer cylinder is made of nonporous insulating material and is surrounded by a metallic shell to maintainthe inner pressure of 10 bar.


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Volumetric receiver


• 2D axisymmetric steady-state heat transfer model

• Radiative transfer is modeled by employing three different approaches: the Rosseland approximation,the P1 approximation, and the collision-based Monte Carlo methodM. Modest (2003), Radiative Heat Transfer, Academic, New York

• Finite volume technique appliedS. Patankar (1980), Numerical Heat Transfer and Fluid Flow, Taylor & Francis, London


Solid phase: 01

r f s s s qT T sh z T

k z r

T rk

r r

f s f

p T T sh z

T

vc Fluid phase:

solved iteratively using Gaussian elimination implemented in MATLABhttp://www.mathworks.fr/fr/help/symbolic/mupad_ref/linalg-gausselim.html

radiative source distributions (from Rosseland, P1 or MC) calculated at each iteration


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Volumetric receiver


Results of the model


Power inputs in kW (solid lines)Constant mass flow rates in g/s (dotted lines)

Reference case indicated by the star

65

301 kW1415 suns

5

15

100

Reference case (dimensions in mm)

For the reference case, thermal ~ 68 %


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Volumetric receiver


Results of the model – Parameter study


ref

ref

P

P P P

• Largest effect is observed for the cavity’s radius and length

• Since q solar is kept constant, a smaller radius implieshigher solar concentration ratios and reduces thereradiation losses

• Optimum length results from a tradeoff betweencapturing efficiently the concentrated solar radiation whilekeeping the highest temperature at the back of the cavity

• Further increase in thermal efficiency may be achieved bydecreasing the RPC’s thickness and increasing the INS’sthickness, but at the expense of increasing the thermalinertia of the system, which results in longer startups


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• Developed by DLR (Germany)

• Secondary concentrator and a pressurized volumetric receiver unit (concave fused silica window)

• Ceramic foam absorber installed on ceramic mounting structure

• Rib geometry was selected to lower the amount of ceramic structures

• 12 rib segments held together by two clamping rings

• Critical point: pressurized windowDevelopment of active window cooling based on air jets blowing towards the window to reach air outlettemperature above 800°C

Ref.: European Commission (2005), SOLGATE – Solar hybrid gas turbine electric power system, Final publishable report, EUR 21615, pp. 47

Volumetric receiver

REFOS (Solgate project)


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Ref.: M. Röger (2006), Multiple Air-Jet Window Cooling for High-Temperature Pressurized Volumetric Receivers: Testing, Evaluation, and Modeling,JSEE, Vol. 128, pp. 265-274

• Radiative heat transfer between the absorber, semi-transparent window, and ambient modeled by applyingthe enclosure method (zone method)Hottel , H. C., 1954, “Radiant -Heat Transmission,” in Heat Transmission, 3 rd ed., W. H. McAdams, ed., McGraw-Hill Book Company,New York, pp. 55 – 125.Hottel, H. C., and Sarofim, A. F., 1967, Radiative Transfer, McGraw-Hill Book Company, New York.

Assumptions:

• Radiation spectrum modeled by discretization in different wavelength bands

• Geometry discretized into many different zones, each zone is assigned individual spectral properties

• To account for transversal heat flux inside the glass volume, the concept of effective thermal conductivityis appliedGardon , R., 1961, “A Review of Radiant Heat Transfer in Glass,” J. Am . Ceram. Soc., 447, pp. 305 –312

• Temperature, incident and outgoing flux density distributions assumed to be homogeneous over eachzone

• Surfaces possess diffuse radiative characteristics

Volumetric receiver



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Ref.: M. Röger (2006), Multiple Air-Jet Window Cooling for High-Temperature Pressurized Volumetric Receivers: Testing, Evaluation, and Modeling,JSEE, Vol. 128, pp. 265-274

• Net radiation method applied

• Configuration factors of different zones are determined by a ray-tracing algorithm

• Four wavelength bands were used to model the spectral properties of fused silica

Volumetric receiver


Simulated Measured

Good agreement


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Ref.: M. Quero, Solugas – Future solar hybrid technology

Tubular/Volumetric receiver

Solugas project = Solhyco + Solgate

• 10 modular panels to keep the overall stresses as low as possible and increase the lifetime expectation

• Honeycomb of several ceramic volumetric receiver individuallyequipped with pressurized quartz windows to get around thethermo-mechanical constraints


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Ref.: T. Tan (2010), Review of study on solid particle solar receivers, Journal of Renewable and Sustainable Energy Reviews, Vol. 14, Issue 1, pp.265-276

• Indirect heating

• Solid particles fed from the top of the receiver

• Air jet may be added on the top of the aperture to separate hot air within the receiverand cold air out of the receiver

• Aerodynamic behavior of particles is impacted by the wind, the air jet flow, the air flow

inside the receiver induced by the falling of particles, and the temperature difference• Thermal interactions that need to be investigated are:

- particle-particle radiation- particle-wall radiation- particle-air convection- air-wall convection


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Ref.: T. Tan (2010), Review of study on solid particle solar receivers, Journal of Renewable and Sustainable Energy Reviews, Vol. 14, Issue 1, pp.265-276Chen H, Chen Y, Hsieh HT, Siegel N. Computational fluid dynamics modeling of gas-particle f low within a solid-particle solar receiver. JSEE2007; 129:160-70R. Clift, J.R. Grace, M.E. Weber, Bubbles, drops and particles. London: Academic Press; 1978

• Air flow inside the receiver influenced by drag forces and buoyant convective heat transfer in the vicinity ofthe particles

• Particle volume fraction found to be less than 0.1 % collisions neglected

• Two-way coupled Euler-Lagrange method (exchange of heat and momentum between the gas phase andthe solid phase) used to simulate the gas-particle flow

• Turbulent flow expected for typical operating conditions of the receiver• Realizable k- model adapted for closing the turbulent Navier-Stokes equation system

• Force balance equates the particle inertia with the forces acting on the particle

p pi

i pi

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p p

i p g uuC

d dt

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,

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,Re

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DC With And



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Ref.: N.P. Siegel (2010), Development and Evaluation of a Prototype Solid Particle Receiver: On-Sun Testing and Model Validation, JSEE, Vol. 132


Solid Particle Receiver of SNL (Albuquerque, USA)

Improvement of the modeling

• Solar ray-tracing algorithm in FLUENT is used to predict the solar illumination energy on the walls

• Small “solar patch” is applied in the middle of the aperture to simulate the concentrated solar irradiation from the heliostat field entering the receiver via the discrete ordinates radiation model

• The magnitude of the solar irradiation (W/m²) applied to the solar patch is calculated using the estimatedinput power for each test

• Heat conduction is simulated within the walls of the cavity

• Convective heat loss to the ambient is simulated assuming a heat transfer coefficient of 5 W/m².K

• Ambient temperature at the aperture boundary has no significant changes

• For each on-sun test, converged solution was achieved for the continuity, velocity, energy, turbulence,and discrete-ordinates intensity residuals


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Unheated test/simulated results


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On-sun simulated results

• As the particle mass flow rate increases, the radiative heat loss decreases because more particlesare available to absorb the input power (greater particle curtain opacity)

• In general, for a given mass flow rate, the relative amount of convective heat loss decreases as theincident power level increases. The amount of convective heat loss at similar power levels does notappear to change with mass flow rate


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On-sun test/simulated results

• Measured increase in particle temperature is within the range of simulated values for all tests

• Increased temperature rise at low flow rates comes at the expense of absorption efficiency


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Milestones to prove the general feasibility

• Particle exit temperature in excess of 900°C Optimize the design

• Receiver efficiency in excess of 70%

• Rigorous analysis of the impact of ambient wind on curtain stability in an open cavity and thedemonstration of strategies to mitigate this issue

• Demonstration of the physical stability of the particles

Conclusion

• This model allows a good estimation of the prototype’s performance

• It is now being used to parametrically evaluate design modifications to the prototype receiver andprovide design input


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• Maximize the heat transfer while minimizing heat losses and pressure drop• For basic tubular geometry, existing Nusselt-Correlations (e.g. Colburn) for heat transfer and

correlations for pressure drop• For complex tubular geometry, development of a correlation for heat transfer and pressure drop• Possible analytical model, fast computation time

Conclusion

Tubular pressurized air receiver

• Study the internal structure to enhance the heat transfer

• Cool down the quartz window to reduce the thermo-mechanical constraints• Numerical model often essential, long computation time

Volumetric pressurized air receiver


• Complex modeling (hydrodynamic, heat transfer, particle behavior…) • Several milestones must be achieved to prove the general feasibility of this concept

High temperature receivers require a cavity to reduce radiative losses


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S olar Facilities for the European Research Area

Thank you for yourattention

SFERA II 2014-2017 , Solar Receiver Modeling, 26/06/14, Odeillo

Main References:

- High-temperature central receivers: C.K. Ho (2014), Review of high-temperature central receiver designs for concentrating

solar power, Renewable and Sustainable Energy Reviews, Vol. 29, pp. 835-846- Volumetric receivers: A.L. Avila-Marin (2011), Volumetric receivers in solar thermal power plants with central receiver system

technology: a review, Solar Energy , Vol. 85, pp. 891-910

- Solid particle receivers: T. Tan (2010), Review of study on solid particle solar receivers, Renewable and Sustainable EnergyReviews, Vol. 14, pp. 265-276

Solar Spain Receiver

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