analytical modeling of forced convection in slotted plate fin heat sinks p. teertstra, j. r. culham...
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Analytical Modeling of Forced Analytical Modeling of Forced Convection in Slotted Plate Fin Heat Convection in Slotted Plate Fin Heat
SinksSinks
P. Teertstra, J. R. Culham & M. M. Yovanovich
Microelectronics Heat Transfer LaboratoryDepartment of Mechanical Engineering
University of WaterlooWaterloo, Ontario, Canada
http://www.mhtl.uwaterloo.ca
Future Challenges in Electronic PackagingFuture Challenges in Electronic PackagingInternational ME’99 Congress and ExpositionInternational ME’99 Congress and Exposition
Nashville, TNNashville, TNNovember 17, 1999November 17, 1999
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Introduction: Plate Fin Heat SinksIntroduction: Plate Fin Heat Sinks
• Heat transfer enhancement for air cooled applications:– increase effective surface area– decrease thermal resistance– control operating temperatures
• Plate fin heat sinks:– most common configuration– convection in channels between fins
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Introduction: Slotted Fin Heat SinksIntroduction: Slotted Fin Heat Sinks
• Enhanced thermal performance:– new thermal boundary layers
initiated at each fin section– increase in average heat
transfer coefficient– decrease in surface area
• Performance of slotted fin heat sinks function of slot size and spacing
• Optimal slotted fin heat sink design balances enhancement of h with reduction of A
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Introduction: Heat Sink SelectionIntroduction: Heat Sink Selection
• Heat sink selection depends on many factors:– performance– dimensional constraints– available airflow– cost
• Quick and accurate design tools are required:– predict performance early in design– perform parametric studies– alternative to numerical simulations,
experiments
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ObjectivesObjectives
• Develop analytical models for average heat transfer rate for slotted fin heat sinks:– laminar, forced convection flow– full range of developing and fully-developed
flow– non-isothermal fins
• Perform experimental measurements to validate proposed models:– range of slot sizes and spacing– inline and staggered slot arrangement
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Problem Definition: Slotted Heat Problem Definition: Slotted Heat SinksSinks
• Uniformly sized and spaced slots in fins– fins slotted from tip to baseplate– fin sections connected only by baseplate
• Slot size and spacing described by dimensionless parameters:
– pitch,
– width,
• Slot arrangement:– inline– staggered
10 LPLP
10 PSPS
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Problem Definition: Plate Fin Heat Problem Definition: Plate Fin Heat SinkSink
• Array of N plates on a single, flat baseplate
• Baseplate assumptions:– fins in perfect thermal contact– isothermal– adiabatic lower surface, edges
• Uniform velocity in all channels with no bypass:– shrouded heat sink– with flow bypass model for un-shrouded heat sinks
• Heat sink modeled as N-1 parallel plate channels
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Problem Definition: Parallel Plate Problem Definition: Parallel Plate ChannelChannel
• Assume b << H– 2D channel flow– neglect baseplate, shroud
effects
• Isothermal boundary conditions
• Reynolds number:
• Nusselt number:
bUbRe
HLATTAk
bQ
asb 2,Nu
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Parallel Plate Channel ModelParallel Plate Channel Model
• Composite solution of 2 limiting cases (Teertstra et al, 1999)
– Fully Developed Flow
L
bU
L
bbb
2
* ReRe
2
PrReNu
*b
b fd
21
*
31*
Re
65.31PrRe664.0Nu
b
bbdev
– Developing Flow
nn
bn
bi devfd
/1NuNuNu
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Plate Fin Heat Sink ModelPlate Fin Heat Sink Model
• Fin effects included in heat sink model:– high aspect ratio heat sinks for power
electronics– dense arrays of tall, thin fins– increased surface area for convection– efficiency reduced
• Fin efficiency:
• Assume adiabatic condition at fin tip:
ib NuNu
b
kh
Ak
Phm
Hm
Hm fi
c Nu,,
tanh
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Plate Fin Heat Sink ModelPlate Fin Heat Sink Model
• Model Summary
iasf
b
TTAkNQ Nu
31321
*
*3*
Re
65.31PrRe664.0
2
PrReNu
b
bb
i
1Nu2
1Nu2tanh
Lt
tH
bH
k
k
Lt
tH
bH
k
k
fi
fi
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Slotted Fin Heat Sink - Model BoundsSlotted Fin Heat Sink - Model Bounds
• Complex problem where exact solution not possible• Upper and lower bounds from plate fin heat sink model:
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Slotted Fin Heat Sink - Lower BoundSlotted Fin Heat Sink - Lower Bound
• No new boundary layers formed
• Modeled using equivalent fin length:
• Lower bound expressions:
PSLSNLL SLB 1
ib
LB PSNu
1
ReRe
**
PS
Lt
L
t
LB 1
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Slotted Fin Heat Sink - Upper BoundSlotted Fin Heat Sink - Upper Bound
• New thermal boundary layer formed at each fin section with no upstream effects
• Modeled using equivalent fin length:
• Upper bound expressions:
PSLPLSPLUB 1
ib
UB PSLPNu
1
ReRe
**
PSLP
Lt
L
t
UB 1
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Experimental ApparatusExperimental Apparatus
• High aspect ratio,
• Various slot configurations
• Back-to-back arrangement
• Mounted in Plexiglas shroud
• Approach velocity measured with hot wire anemometer
• Temperatures measured at 4 locations on baseplate
• Radiation losses measured in separate experiment
20bH LP PS Slots
0.059 0.54 inline
0.11 0.5 inline
0.22 0.5 inline
0.44 0.5 inline
0.22 0.5 staggered
0.44 0.5 staggered
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Experimental ResultsExperimental Results
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Model ValidationModel Validation
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Model ValidationModel Validation
• Arithmetic mean of bounds within 12% RMS of data
2Nu UBLB
bNuNu
5.0
44.011.0
180Re40 *b
PS
LP
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Summary and ConclusionsSummary and Conclusions
• Models developed for upper and lower bounds for slotted fin heat sinks
• Experimental data within bounds for full range of test conditions
• Arithmetic mean of bounds predicts within 12% RMS over range of test conditions
• Reliable optimization procedure cannot be determined from the limited range of values
• Additional study and data are required
bNu
PS
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AcknowledgementsAcknowledgements
The authors gratefully acknowledge the continued financial support of R-Theta Inc. and Materials and Manufacturing Ontario.