outline review for second midterm
TRANSCRIPT
Review for Second Midterm April 19, 2010
ME 483 Alternative Energy Engineering II
Review for Second MidtermReview for Second Midterm
Larry CarettoMechanical Engineering 483
Alternative Energy Alternative Energy Engineering IIEngineering II
April 19, 2010
2
Outlineā¢ Black-body and solar radiationā¢ Emissivity and absorptivityā¢ Path of the sunā¢ Solar collectors
ā Basic analysisā¢ Useful gain = Absorbed solar ā Heat Lossā¢ Overall loss coefficient, Uc
ā¢ Effectiveness terms and factors: F, Fā, FR, FāRā f-chart method
3
ā¢ Radiation heat transfer by electromagnetic radiationā Part of much larger spectrumā Thermal radiation transfers
heat without contactā¢ Use of fire or electric resistance
heating are best examplesā¢ Thermal radiation lies in infrared
and visible part of spectrum (with some in ultraviolet)
Electromagnetic Radiation
Figure 12-3 from Ćengel, Heat and Mass Transfer 4
Black-body Radiationā¢ Perfect emitter ā no
surface can emit more radiation than a black body
ā¢ Diffuse emitter āradiation is uniform in all directions
ā¢ Perfect absorber ā all radiation striking a black body is absorbed
Figure 12-7 from Ćengel, Heat and Mass Transfer
5
Black-Body Radiation IIā¢ Basic black body equation: Eb = ĻT4
ā Eb is total black-body radiation energy flux W/m2 or Btu/hrĀ·ft2
ā Ļ is the Stefan-Boltzmann constantā¢ Ļ = = 2Ļ5k4/(15h3c2) = 5.670x10-8 W/m2Ā·K4 =
0.1714x10-8 Btu/hrĀ·ft2Ā·R4
ā¢ k = Boltzmannās constant = 1.38065x10-23 J/K (molecular gas constant) = Ru/NAvagadro
ā¢ h = Planckās constant = 6.62607x10-34 JĀ·sā¢ c = 299,792,458 m/s = speed of light in a
vacuum
6
Black-body Radiation Spectrumā¢ Energy (W/m2) emitted varies with
wavelength and temperatureā¢ EbĪ» is spectral radiation
ā Units are W/(m2ā Ī¼m)ā EbĪ»dĪ» is fraction of black body radiation in
range dĪ» about wavelength Ī»ā¢ Maximum occurs at Ī»T = 2897.8 Ī¼mĀ·K
ā T increase shifts peak shift to lower Ī»ā¢ Diagram on next chart
Review for Second Midterm April 19, 2010
ME 483 Alternative Energy Engineering II
7
Spectral EbĪ»Black Body Radiation
1
10
100
1,000
10,000
100,000
1,000,000
10,000,000
100,000,000
0.1 1 10 100Wavelength, Ī», Ī¼m
Radiation W/m2-Ī¼m
T = 6000 KT = 5000 KT = 4000 KT = 3000 KT = 2000 KT = 1000 KT = 800 KT = 600 KT = 400 KT = 300 K
visible infrared
ultra-violet
8
Spectral Black-body Energyā¢ EbĪ»dĪ» = black-body emissive power in a
wavelength range dĪ» about Ī»ā Typical units for EbĪ» are W/m2Ā·Ī¼m or
Btu/hrĀ·ft2Ā·Ī¼m
( ) Ī»āĪ»
=Ī» Ī»Ī» de
CdE TCb125
1
ā¢ C1 = 2Ļhc2 = 3.74177 WĀ·Ī¼m4/m2
ā¢ C2 = hc/k = 14387.8 Ī¼m/Kā h = Planckās constant, c = speed of light in
vacuum, k = Boltzmannās constant
9
Partial Black-body Power
ā«Ī»
Ī»Ī»ā Ī»=1
10
0, dEE bb
ā«Ī»
Ī»Ī» Ī»Ļ
=0
4 '1 dET
f b
Black body radiation between Ī» = 0 and Ī» = Ī»1 is Eb,0-Ī»1
Fraction of total radiation (ĻT4) between Ī» = 0 and any given Ī» is fĪ»
Figure 12-13 from Ćengel, Heat and Mass Transfer10
Radiation Tablesā¢ Can show that fĪ» is function of Ī»T
( ) ( ) ( ) ( )ā«ā«ā«Ī»
Ī»
Ī»
Ī»
Ī»
Ī»Ī» Ī»āĪ»Ļ
=Ī»āĪ»Ļ
=Ī»Ļ
=T
TCTCb TdeTCd
eC
TdE
Tf
05
1
05
14
04 1
11
1122
ā¢ Radiation tables give fĪ» versus Ī»Tā See table 12-2,
page 118 in Hodgeā Extract from similar
table shown at right
11
ĪĪ»
Figure 12-14 from Ćengel, Heat and Mass Transfer
ā¢ Radiation in finite band, ĪĪ»
( ) ( )TfTf
dET
dET
dET
f
bb
b
120
40
4
4
12
2
1
21
11
1
Ī»āĪ»=
Ī»Ļ
āĪ»Ļ
=Ī»Ļ
=
ā«ā«
ā«Ī»
Ī»
Ī»
Ī»
Ī»
Ī»Ī»Ī»āĪ»
12
Emissivityā¢ Emissivity, Īµ, is ratio of actual emissive
power to black body emissive powerā May be defined on a directional and
wavelength basis, ĪµĪ»,Īø(Ī»,Īø,Ļ,T) = IĪ»,e(Ī»,Īø,Ļ,T)/IbĪ»(Ī»,T), called spectral, directional emissivity
ā Total directional emissivity, average over all wavelengths, ĪµĪø(Īø,Ļ,T) = Ie(Īø,Ļ,T)/Ib(T)
ā Spectral hemispherical emissivity average over directions, ĪµĪ»(Ī»,T) = IĪ»(Ī»,T)/IbĪ»(Ī»,T)
ā Total hemispheric emissivity = E(T)/Eb(T)
Review for Second Midterm April 19, 2010
ME 483 Alternative Energy Engineering II
13
Emissivity Assumptionsā¢ Diffuse surface ā emissivity does not
depend on directionā¢ Gray surface ā emissivity does not
depend on wavelengthā¢ Gray, diffuse surface ā emissivity is the
does not depend on direction or wavelengthā Simplest surface to handle and often used
in radiation calculations14
15 16
Propertiesā¢ When radiation,
G, hits a surface a fraction ĻG is reflected; another fraction, Ī±G is absorbed, a third fraction ĻG is transmitted
ā¢ Energy balance: Ļ + Ī± + Ļ = 1
Figure 12-31 from Ćengel, Heat and Mass Transfer
17
Properties IIā¢ Fractions on
previous chart are propertiesā Reflectivity, Ļā Absorptivity, Ī±ā Transmissivity, Ļ
ā¢ Energy balance: Ļ + Ī± + Ļ = 1Figure 12-31 from
Ćengel, Heat and Mass Transfer
18
Properties IIIā¢ As with emissivity, Ī±, Ļ, and Ļ may be
defined on a spectral and directional basisā Can also take averages over wavelength,
direction or both as with emissivityā Simplest case is no dependence on either
wavelength or directionā Reflectivity may be diffuse or have angle of
reflection equal angle of incidence
Review for Second Midterm April 19, 2010
ME 483 Alternative Energy Engineering II
19
Ī± Dataā¢ Solar
radiation has effective source temperature of about 5800 K
Figure 12-33 from Ćengel, Heat and Mass Transfer 20
Kirchoffās Lawā¢ Absorptivity equals emissivity (at the
same temperature) Ī±Ī» = ĪµĪ»
ā¢ True only for values in a given direction and wavelength
ā¢ Assuming total hemispherical values of Ī± and Īµ are the same simplifies radiation heat transfer calculations, but is not always a good assumption
21
Effect of Temperatureā¢ Emissivity, Īµ, depends on surface
temperatureā¢ Absorptivity, Ī±, depends on source
temperature (e.g. Tsun ā 5800 K)ā¢ For surfaces exposed to solar radiation
ā high Ī± and low Īµ will keep surface warmā low Ī± and high Īµ will keep surface coolā Does not violate Kirchoffās law since
source and surface temperatures differ 22From Ćengel, Heat and Mass Transfer
23
Average Radiation Propertiesā¢ Integrated average properties over all
wavelengths
ā«ā«āā
==0
40
4
11 Ī»Ī±Ļ
Ī±Ī»ĪµĻ
Īµ Ī»Ī»Ī»Ī» dET
dET bb
ā¢ Look at simple example where ĪµĪ» = Īµ1for Ī» < Ī»1 and ĪµĪ» = Īµ2 for Ī» > Ī»1
ā«ā«ā«āā
+==1
1
240
140
4
111
Ī»Ī»
Ī»
Ī»Ī»Ī» Ī»ĪµĻ
Ī»ĪµĻ
Ī»ĪµĻ
Īµ dET
dET
dET bbb
24
Average Radiation Properties IIā¢ Rearrange to get fĪ», the fraction of black
body radiation between 0 and Ī»
( )11
1
1
1'' 2142
04
1Ī»Ī»
ā
Ī»Ī»
Ī»
Ī» āĪµ+Īµ=Ī»ĻĪµ
+Ī»ĻĪµ
=Īµ ā«ā« ffdET
dET bb
ā¢ Similar equation for absorptivity (Ī±Ī» = ĪµĪ»)
( )11
1
1
1'' 2142
04
1Ī»Ī»
ā
Ī»Ī»
Ī»
Ī» āĪ±+Ī±=Ī»ĻĪ±
+Ī»ĻĪ±
=Ī± ā«ā« ffdET
dET bb
Review for Second Midterm April 19, 2010
ME 483 Alternative Energy Engineering II
25
Exampleā¢ Data: ĪµĪ» = 0.9 for Ī» < 3 Ī¼m and ĪµĪ» = 0.2
for Ī» > 3ā Solar T = 5800 K, Ī»T = 17,400 Ī¼mĀ·K,
fĪ»(17,400 Ī¼mĀ·K) = 0.980155, find Ī±ā¢ Use Ī±Ī» = ĪµĪ»
ā Earth T = 300 K, Ī»T = 900 Ī¼mĀ·K, fĪ»(17,400 Ī¼mĀ·K) = 0.001, find Īµ
( ) ( ) ( ) 886.0980.012.0980.09.0111 215800 =ā+=āĪ±+Ī±=Ī± Ī»Ī» ffK
( ) ( ) ( ) 201.0001.012.0001.09.0111 21300 =ā+=āĪµ+Īµ=Īµ Ī»Ī» ffK
26
27
Solar Angles III
from the sun center
28
Solar Declination AngleDeclination Angle & Relative Earth-Sun Distance
-30
-20
-10
0
10
20
30
0 40 80 120 160 200 240 280 320 360
Julian Date
Dec
linat
ion
Ang
le (d
egre
es
0.97
0.98
0.99
1.00
1.01
1.02
1.03
Rel
ativ
e Ea
rth-
sun
Dis
tancDeclination angle
Relative distance
29
Tangent plane to earthās surface at given location 30
Angles for Tilted Collector
Review for Second Midterm April 19, 2010
ME 483 Alternative Energy Engineering II
31
Equation of Time
Solar Time = Standard Time +
Equation of Time +
(4 min/o) * (Standard Longitude āLocal Longitude)Standard Time = DST ā 1 hour
32
Computing the Sun Pathā¢ Input data: Latitude, L, date, hour hā¢ Find declination from serial date, n
( ) ( ) ( )degreesinĪ“ā„ā¦ā¤
ā¢ā£ā” Ļ
+=Ī“180
284365360sin45.23 no
ā¢ Two angles: altitude (Ī±) and azimuth (Ļ)ā sin(Ī±) = sin(L) sin(Ī“) + cos(L) cos(Ī“) cos(h)ā sin(Ī±s) = sin(Ļ) = cos(Ī“) sin(h) / cos(Ī±)ā Sun path is plot of Ī± vs. Ļ = Ī±s for one dayā Plot is symmetric about solar noonā Typically plot data for 21st of month
33
Path Calculation Problemā¢ Angles given as sin(angle) = x require
arcsin function calculationā¢ Typical arcsine function returns angle
between ā90o and 90o
ā Limits correspond to range for sine between ā1 and +1
ā Special calculation for hour angle limitā¢ hlimit = Ā±tan(Ī“) / tan(L)ā¢ Ļ = Ā±[Ļ ā arcsin(sin Ļ)] for |h| > |hlimit|
34
35
Solar Irradiation by Month in Los Angeles (LAX)Average of Monthly 1961-1990 NREL Data for different collectors
0
1
2
3
4
5
6
7
8
9
10
Jan Feb Mar Apr May Jun Jul Aug Sep Oct Nov Dec
Month
Irrad
iatio
n (k
Wh/
m2 /day
)
Fixed, tilt=0
Fixed, tilt=L-15
Fixed, tilt=LFixed,tilt=L+15
Fixed,tilt=90
1-axis,track,EW horizontal
1-axis,track,NS horizontal
1-axis,track,tilt=L
1axis,tilt=L+15
2-axis,track
Notes:All fixed collectors are facing southThe L in tilt = L means the local latitude (33.93oN)
36
Optimum Fixed Collector Tilt
35o
Review for Second Midterm April 19, 2010
ME 483 Alternative Energy Engineering II
37
Solar
Insolationby collectororientationand monthat 40oNlatitude
38
39 40
41
Active Indirect Solar Water Heating
http://www.dnr.mo.gov/energy/renewables/solar6.htm (accessed March 12, 2007)
42
Passive Direct Solar Water Heatinghttp://southface.org/solar/solar-roadmap/solar_how-to/batch-collector.jpg (accessed March 12, 2007)
Review for Second Midterm April 19, 2010
ME 483 Alternative Energy Engineering II
43
Basic Solar Collector Analysisā¢ Overall heat balance
ā Incoming solar radiationā Heat loss from collector to environmentā Useful energy gain = Incoming Solar
Radiation ā Environmental Heat Lossā¢ Environmental heat loss proportional to
ĪT = Tcollector ā Tambientā Applications that require high collector
temperatures will have more heat loss44
Useful Heat Transferā¢ Heat is added to a collector fluid
ā Typically collector fluid is water or water and anti-freeze solution
ā Air is also used as collector fluid for home heating
ā¢ Energy added from simple first law for open system with consant pressure heat addition
( )infoutfpu TTcmQ ,, ā= &&
45
Solar to Useful Energyā¢ Solar transmission through glass covers
provides absorbed radiation, Ha = HiĻĪ±ā¢ Consider three losses
ā Conduction through bottom of solar collector box
ā Conduction through edge of boxā Loss through top
ā¢ Convection between absorber plate and glass covers with conduction through glass
ā¢ Convection from top glass cover to ambient
46
Loss Through Topā¢ In steady state the following heat rates
will be the sameā Between absorber plate and bottom glassā From bottom glass to top glass
ā¢ Consider two-plate collectorā From top glass to ambientā Look at exchange between absorber plate
at temperature TP and bottom glass at temperature Tg2
ā Have convection plus radiation
47
Loss from Absorber Plate( ) ( )
1112
42
4
22
ā+
ā+ā= ā
gP
gPcgPcgptop
TTATTAhQ
ĪµĪµ
Ļ
( ) ( )( )( ) ( )22,
2
2222
2
2
42
4
111111 gPgpr
gP
gPgPgPc
gP
gPc TThTTTTTTATTA
ā=ā+
ā++=
ā+
āā
ĪµĪµ
Ļ
ĪµĪµ
Ļ
( ) ( )2
222,2
gp
gPgPcgprgptop R
TTTTAhhQ
āāā
ā=ā+=
48
Remaining Top Loss Path
ā¢ Between glass plates
( ) ( )12
121212,12
gg
ggggcggrggtop R
TTTTAhhQ
āāā
ā=ā+=
( )( )111
21
2122
21
12,
ā+
++=ā
gg
ggggcggr
TTTTAh
ĪµĪµ
Ļ
( ) ( )12
111,1
gg
agagcagragtop R
TTTTAhhQ
āāā
ā=ā+=
( )( )ag
skyg
gg
skygskygcagr TT
TTTTTTAh
ā
ā
ā+
++=ā
1
1
21
122
11,
111ĪµĪµ
Ļ
ā¢ Top plate to ambient
Review for Second Midterm April 19, 2010
ME 483 Alternative Energy Engineering II
49
Loss Through Top/Bottomā¢ Combine three resistances in series to
get Rtop = RP-g2 + Rg2-g1 + Rg1-aā Qtop = (TP ā Ta)/Rtop = UtopAc(TP ā Ta)
ā¢ Loss through bottom is conduction through insulation (kins, Īxins) in series with convection to ambient with hb-a
( )aPcbottom
cabcins
ins
aP
convins
aPbottom TTAU
AhAxk
TTRRTTQ ā=
+Ī
ā=
+ā
=
ā
1
50
Total Lossā¢ Qsides = UāsideAside(TP ā Ta)
ā Can estimate Uāside = 0.5 W/m2Ā·Kā Use UsideAc = UāsideAside for common areaā Qsides = UsideAc(TP ā Ta) = (TP ā Ta)/Aside
ā¢ Total is sum of individual lossesā¢ Qloss = UcAc(TP ā Ta)= (TP ā Ta)/Rc
ā¢ Overall conductance and resistanceā¢ Uc = Utop + Ubottom + Usides
sidebottomtopc RRRR1111
++=
51
Approximate Utop Equation
( )( )
( ) NBNN
TTTT
hBNTT
TA
U
gpp
apap
w
ap
p
top
āāāā
āāāā
ā
Īµā+
+Īµā+Īµ
++Ļ+
+āāā
āāāā
ā+
ā=
12105.0
1
1'
1
22
33.0
N = number of glass coversAā = 250[1 ā 0.0044(s ā 90)]s = tilt angle (degrees)B = (1 ā 0.04hw +
0.0005hw2)(1 + 0.091N)
hw = heat transfer coeffi-cient from top to ambient
Other symbols have previous definitions
Equation uses SI units: Uc and h in W/m2Ā·K, T in K, Ļ= 5.670x10-8 W/m2Ā·K4, Īµg is same for all glass covers
52
Absorber Plate Analysisā¢ Three analysis steps for solar energy to
heat fluid (Hottel-Whillier-Bliss equation)ā Solar energy into plate flows across plate
to location of tubes at some line on plateā At same line heat flow into collector fluid
from plate is determinedā Integrate heat flow into fluid from inlet to
exit to get total useful heat transfer to fluid
( )[ ]ainfcacRu TTUHAFQ āā= .&
53
Flat Plate Collector2L = distance between outside of flow tubes
D = flow tube outer diameter
t = absorber plate thickness
w = distance between flow tube centerlines = 2L + D
Di = flow tube inner diameter
k = absorber thermal conductivity
54
Absorber Plate Analysis
ā¢ Define m2 = Uc/(tkplate)ā¢ Effectiveness factor, F = tanh(mL) / (mL)ā¢ Total (useful) heat transfer per unit length of
tube ( ) ( )[ ] '2 uabcatotal qTTUHDLFq =āā+=
Review for Second Midterm April 19, 2010
ME 483 Alternative Energy Engineering II
55
Absorber Plate Analysis II
ā¢ Heat flow into fluid at any point
( )[ ]
( )
( )[ ]afca
iicBc
afcac
u TTUHwF
DhCUDLF
TTUHUq āā=
ā„ā„ā¦
ā¤
ā¢ā¢ā£
ā”āāā
āāāā
ā++
+
āā= '
112
1
1
,
'
Ļ
56
Factors, Fā and FR
AmbientandFluidBetweenResistanceThermalAmbientandPlateBetweenResistanceThermal
='F
( )[ ] ( )( )[ ]iicBc
cDhCUDLFw
UFĻ+++
=,1121
1'
ā¢ Collector efficiency factor, Fā
( )p
ccacmFAU
cc
pRcm
FAUaea
eFAU
cmFF p
cc
&
& & '111''
'
=ā=āāā
ā
ā
āāā
ā
āā= ā
ā
ā¢ Heat removal factor, FR
[ ] [ ]āāā ,0/1,1' aasaFFR
57
FR/F' Chart
0.6
0.65
0.7
0.75
0.8
0.85
0.9
0.95
1
1 10 100
F R/F
'
( )cc
cp
UFA
cm
'
&58
Summary of Resultsā¢ Qu = useful heat transfer to working fluid
( ) ā„ā¦
ā¤ā¢ā£
ā”++
+
=
iiBcc hDCDLFUUw
F
Ļ11
21
1'
ā„ā„ā¦
ā¤
ā¢ā¢ā£
ā”ā=
āp
ccmAFU
c
pR e
AUcm
F &&'
1
( )[ ]p
uinfoutfainfcaRu cm
QTTTTUHAFQ&
+=āā= ,,,
( )ĻĪ±= ia HH
59
Collector Efficiency, Ī·c = Qu/AcHi
ā¢ Replace Ha by HiĻĪ±
( )[ ]ainfcacRu TTUHAFQ āā= .
ā¢ Start with Hottel-Whillier-Bliss Equation
( )[ ]ainfcicRu TTUHAFQ āā= .ĻĪ±
ā¢ Substitute into efficiency equation
( )[ ] ( )i
ainfcRR
ic
ainfcicR
ic
uc H
TTUFF
HATTUHAF
HAQ ā
ā=āā
== .. ĻĪ±ĻĪ±
Ī·
60
Solar Collector Efficiency Tests
0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0.9
1
0 0.05 0.1 0.15
Effic
ienc
y
1-cover, black1-cover, selective2-cover, black2-cover, selective
Slope = āFRUc
Intercept = FR(ĻĪ±)n
Review for Second Midterm April 19, 2010
ME 483 Alternative Energy Engineering II
61
Sample Rating Sheet
http://www.builditsolar.com/References/Ratings/SRCCRating.htm 62
Sample Rating Sheet II
slope = āFRUcintercept = FR(ĻĪ±)n
63
F-chart Water Heating Only
64
System with Solar Air Heating
65
F-Chart Water and Space Heating
66
Tf,in
Tf,out
Tw,in
Tw,out
http://starfiresolar.com/db2/00144/starfiresolar.com/_uimages/solardiagramallred.jpg
(C)ollectorfluid loop(S)torage
fluid loop
( ) ( ) ( ) ( )inwoutwspinwoutfpcu TTcmTTcmQ ,,,,minā=ā= &&Īµ
Īµc = heat-exchanger effectiveness
( )( ) ( )[ ]
cpsp
p
cmcmcm
&&
&
,minmin
=
Review for Second Midterm April 19, 2010
ME 483 Alternative Energy Engineering II
67
Heat Exchangerā¢ Start with Hottel-Whillier-Bliss equation
ā Replace Tf,in by Tw,in
( ) ( ) ( )ainwcRcaRcpc
cRc
cp
cRcu TTUFAHFA
cmUFA
cmUFAQ āā=
ā„ā„ā¦
ā¤
ā¢ā¢ā£
ā”+ā ,
min
1&& Īµ
( )[ ]ainwcaRcu TTUHFAQ āā= ,'
( ) ( ) ( )( )( )
1
min
1
min
' 111
āā
ā„ā„ā¦
ā¤
ā¢ā¢ā£
ā”
āā
ā
ā
āā
ā
āā
Īµ+=
ā„ā„ā¦
ā¤
ā¢ā¢ā£
ā”
Īµ+ā=
pc
cp
cp
cRcR
pc
cRc
cp
cRcRR cm
cm
cmUFAF
cmUFA
cmUFAFF
&
&
&&&
68
F'R/FR Chart
0.3
0.4
0.5
0.6
0.7
0.8
0.9
1
1 10 100
F'R/F
R
ratio = 0.9ratio = 0.8ratio = 0.7ratio = 0.6ratio = 0.5ratio = 0.4ratio = 0.3ratio = 0.2ratio = 0.1
( )( )
cp
pc
cm
cm&
&min
Īµ=ratio
( )cRc
cp
UFA
cm&
69
f-chart Methodā¢ Predicts fraction of demand over a time
period (usually monthly) than can be supplied by solar
ā¢ Two empirical pamameters, X and Yā X is ratio of reference collector loss to total
heating loadā Y is ratio of absorbed solar energy to total
heating load
( )arefcRc TT
DUFAX ā='
totaliRc H
DFAY ,
' ĻĪ±=
70
Computing X (dimensionless)( )ā„
ā¦
ā¤ā¢ā£
ā”ā
Ī= aref
R
RcRc TT
Dt
FFUFAX
'
ā¢ FRUc (W/m2Ā·K) from slope of collector test data
ā¢ FāR/FR computed or assumed = 0.97ā¢ Usual averaging period, Īt = 1 month,
converted to secondsā¢ D = heating demand for averaging
period (J)ā¢ Tref = 100oC; from NREL dataaT
ā¢ Ac = collector area (m2)
71
Computing Y (dimensionless)
ā¢ FR(ĻĪ±)n from intercept of collector testā¢ FāR/FR computed or assumed = 0.97ā¢ Ratio = 0.94 (October ā March),
= 0.90 (April ā September) or computedā¢ Hi,total is available from NREL data for Īt
= 1 month (convert to J/m2)ā¢ D is heating demand J
( ) ( ) ā„ā¦
ā¤ā¢ā£
ā”=
DH
FFFAY totali
nR
RnRc
,'
ĻĪ±ĻĪ±ĻĪ±
( )nĻĪ±ĻĪ± /
ā¢ Ac = collector area (m2)
72
f Equationsā¢ For water heating: f = 1.029Y ā 0.065X
ā 0.245Y2 + 0.0018X2 + 0.0215Y3
ā Adjustments requiredā¢ Adjust X for hot water supply only and storage
capacity different from standardā¢ Adjust Y for load heat exchanger capacity
ā¢ For air heating: f = 1.040Y ā 0.065X ā0.159Y2 +0.00187X2 ā 0.0095Y3
ā Solar collectors heating air have no heat exchanger so FāR = FR
Review for Second Midterm April 19, 2010
ME 483 Alternative Energy Engineering II
73
f-Chart
0.0
0.5
1.0
1.5
2.0
2.5
3.0
0 2 4 6 8 10 12 14 16
X
Y
f = 0.9f = 0.8f = 0.7f = 0.6f = 0.5f = 0.4f = 0.3f = 0.2f = 0.1
F-Chart for Collectors Using Water
74
Adjustmentsā¢ Adjust X for storage capacity, M, in L/m2
Xā = X(75/M)1/4
ā¢ Adjust Y for load heat exchanger factor, Z: Yā = Y(0.39 + 0.65e-0.139/Z)ā ĪµL = heat exchanger effectivenessā mass flow times heat capacity and UA
factors defined previously
( ) ( )LpL UAcmZmin
&Īµ=
75
Another Adjustmentā¢ For systems with only water heating
ā Tw = water temperature to householdā Tm = cold water supply temperatureā Ta = monthly average ambient temperature
ā¢ Multiply X by correction factor, CF, below
a
amwT
TTTCFā
ā++=
10032.286.318.16.11
76
NREL Dataā¢ National Renewable Energy Laboratoryā¢ Collector data for 1961-1990 for 360
individual months and monthly averagesā Available for variety of collectors
ā¢ Flat plate collector data for several angles
ā¢ TMY3 data: Typical Meteorological Yearā Hourly data on radiation componentsā Compute resultant for given collector
geometry
77
NREL Collector Types ā61-ā90ā¢ Data available at
different tilt levels for flat-plate collectors facing southā Horizontal (0o)ā Latitude ā 15o
ā Latitudeā Latitude + 15o
ā Vertical (90o)78
NREL 1961-1990 LAX AverageSOLAR RADIATION FOR FLAT-PLATE COLLECTORS FACING SOUTH AT A FIXED-TILT (kWh/m2/day) Percentage Uncertainty = 9Tilt(deg) Jan Feb Mar Apr May Jun Jul Aug Sep Oct Nov Dec Year 0 Average 2.8 3.6 4.8 6.1 6.4 6.6 7.1 6.5 5.3 4.2 3.2 2.6 4.9
Minimum 2.3 3.0 4.0 5.5 5.7 5.6 6.4 6.1 4.4 3.8 2.7 2.1 4.7 Maximum 3.3 4.4 5.6 6.8 7.2 7.7 8.0 7.0 5.8 4.5 3.6 3.0 5.1
Lat - 15 Average 3.8 4.5 5.5 6.4 6.4 6.4 7.1 6.8 5.9 5.0 4.2 3.6 5.5Minimum 2.9 3.6 4.5 5.8 5.7 5.4 6.3 6.3 4.7 4.4 3.4 2.7 5.2Maximum 4.6 5.7 6.4 7.3 7.3 7.3 7.9 7.2 6.6 5.6 4.9 4.3 5.7
Lat Average 4.4 5.0 5.7 6.3 6.1 6.0 6.6 6.6 6.0 5.4 4.7 4.2 5.6Minimum 3.3 3.8 4.7 5.6 5.4 5.0 5.9 6.1 4.8 4.7 3.7 3.0 5.3Maximum 5.4 6.4 6.7 7.2 6.8 6.7 7.3 7.0 6.7 6.0 5.6 5.0 5.9
Lat + 15 Average 4.7 5.1 5.6 5.9 5.4 5.2 5.8 6.0 5.7 5.5 5.0 4.5 5.4Minimum 3.4 3.8 4.5 5.2 4.8 4.4 5.2 5.5 4.5 4.7 3.9 3.1 5.1Maximum 5.9 6.6 6.6 6.7 6.1 5.8 6.3 6.4 6.5 6.1 6.0 5.4 5.7
90 Average 4.1 4.1 3.8 3.3 2.5 2.2 2.4 3.0 3.6 4.2 4.3 4.1 3.5 Minimum 2.9 3.0 3.1 2.9 2.3 2.1 2.3 2.8 2.9 3.5 3.2 2.7 3.3 Maximum 5.2 5.4 4.5 3.6 2.7 2.3 2.5 3.2 4.1 4.7 5.2 5.0 3.7