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Energies 2019, 12, x FOR PEER REVIEW 15 of 22 Energies 2019, 12, x FOR PEER REVIEW 15 of 22 centrifugal energy (associated with blade speed) and change in relative kinetic energy (associated centrifugal energy (associated with blade speed) and change in relative kinetic energy (associated with relative velocity) [49]: wEnietrhgierse2l0a1t9iv, 1e2,v2e7l9o1city) [49]: energy (associated with blade speed) and change in relative kinetic energy (associated with relative rotor was evaluated using using [50]: (V2 −V2)+(U2 −U2)+(W2 −W2) ΔW=(V2 −V1)+(U2−U1)+(W1 −W2) 222222 ΔW=2 1 221 1 2 2 (6) velocity) [49]: Here and are the absolute and relative velocities of the fluid, respectively. is the blade Here and are the absolute and relative velocities of the fluid, respectively. is the blade (V2 −V2)+(U2 −U2)+(W2 −W2) speed and is calculated by multiplying the blade mean radius with the blade rotational speed ( ω). speed and is calculated by multiplying2the b1lade m2ean r1adius w1ith th2e blade rotational speed (ω). ∆W = (6) ρ222222 both configurations are shoΔwPn in=Fig[u(Vres 1−8Van)d+19(U, res−pUecti)ve−ly(W. The−tWotal)]pressure change across(t7h)e ΔP = [(V2 −V2)+(U2 −U2)−(W2 −W2)] (7) R212121 R2212121 2 As Figure 18 and Figure 19 illustrate, the performance plot of the outflow turbine is comparable As Figure 18 and Figure 19 illustrate, the performance plot of the outflow turbine is comparable ρ 222222 to that of the inflow turbin∆e.PARls=o, th[(eVtot−alVpr)e+ssu(Ure a−cUros)s−th(eWou−tflWow)]rotor is very close to that(7o)f to that of the inflow turbine. Also, the to2tal p1ressure2acro1ss the o2utflow1 rotor is very close to that of 2 the inflow rotor over the whole range of turbine pressure drops. the inflow rotor over the whole range of turbine pressure drops. 15 of 22 (6) Subscript 2 refers to fluid entering the rotor and subs2cript 1 is flow leaving the rotor. Subscript 2 refers to fluid entering the rotor and subscript 1 is flow leaving the rotor. IHIneareraVdiianllldy oWoutawreartdhdeflloaobwsomluactcehiained,, drueuleatoiovcechvaenlgoecsistinensraoadf iituhseoflfuroiodta,atriieosnp,,ectiviiesllyle.ssUs thisantnheb,,ltathdiises cscoponenfefiidguarnradtiioiosnciaislcusluauataelldlybuysemeduflotirpplpyuimnmgptshaenbdlacdoemmprereaesnssoroarsdsituosiinwncirteheatsheethbheleasdsteatriiocthaheteiaodn..aNlNsepverdth(erlRleωss),,. aSanunbosuctrtwipatr2drfefllofoewrsrtaoadfliiauallidcoenftiigegruirnragtiitohne wrwoatsosriinavnvedststiiugbatstecedrdipiint 1thiisisflroewsealercachvhitntogbteheemroptollor.yed as a turbiine.. ThisIdnesaigrandwiaallsyooputitmwiasredfltowhamveacahminaex,idmuiezetodcehffaicnigeenscyinarnaditusseonferogtyatiroan,sUfercisapleasbsitlhitaynwUill,ntohwis This design was optimised to have a maximized efficiency and its energy transfer2 capability wil1l now bcboencfiogmuprartrieodnaigsgauiisnustatlalypuresevevdiioufuosrllypuopmptpiims iaisned ciinonfmfllopwretstusrorbrisinteodinescsirigenans[e[34t4h].e. Tshthaetiicnhflleoawd.tuNrbebviineerethaeaslse7s73s3, gagunuiioduetvwvaanredsflatot twtheraudpisastlreceaoamnmfi,,g3u4rgautiiodnewvanseisnavatet dsdtoigwantestdtreinamthaiasnrde5s5e1arocthtortrobbllaedems,,pmloyredeaetstaaiillstsuorfbtihniies. tTtuhribsiindnescigan wbeasfoupntdidmiininse[d34t]o.. FhFiaigvuereae m17asxscimheimzmeadtiiecffiallclyieinillcluystatrnadteistsbeonthehrrgroytotrasnwsfiiethrhcarpbaiitbtrialrirtyawniglllensoawat tbtheeceoenmtrpyaaraendaegxaiitit.n. IsIntnadpddrdeiitvtiioionu,,stlhyeoepftfiimciieiesnecdyipnplfllootsws atnudrbthihnetdotetaslilgpnre[s3ss4u].reTchcheaingfleoswactrurorsbsinthehehrarost7o3r (g(uid)eovfabnboeotsthactcothnefiigugupursratartieioanms,a3r4egsuhiodwenvaiineFsiigagutudreow18nasatnrdedaFmiigaunrede 151919,,rroetsoprebcltaiivdvellsy,..mTohretdoetataalliplsreoesfstuhriese ctcuhrabnignge acacacrnrobsses tfthoheuenrodotoionr [w34a]s. eFvigaluluraeat1e7dsucshsiienmgautsisciinanglgly[5i0l0l]u]::strates both rotors with arbitrary angles at the entry and exit. In addition, the efficiency plots and the total pressure changes across the rotor (∆PR) of ρ Figure 17. Schematics of the airflow velocity components at the rotor section of the outflow and inflow Figure 17..ScShcehmemataictiscosfothf ethaeirfaliorwflovwelovceiltoyccitoymcpoomnpenotnseantttshaetrothtoerrsoetcotriosneoctfitohne ofutfhleowouatnfldoiwnflaonwd turbines. tiunrflboiwnetsu.rbines. 0.6 0.6 0.4 0.4 0.2 0.2 1 1 0.8 0.8 0 0 0 2000 4000 6000 8000 10000 12000 0 2000 4000 6000 8000 10000 12000 iInflow iInflow Outflow Outflow Δ (Pa) Δ 0 (Pa) 0 Figure 18. Comparison of the efficiency of outflow and inflow turbines over a range of turbine Figure 18. Comparison of the efficiency of outflow and inflow turbines over a range of turbine Figure 18. Comparison of the efficiency of outflow and inflow turbines over a range of turbine pressure differentials. pressure differentials. pressure differentials. η ηPDF Image | Unidirectional Radial-Air-Turbine OWC Wave Energy Converters
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