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![Page 1: Non-constant wall thickness scroll expander investigation for a micro solar ORC power plant by Ir. Rémi DICKES (MIT/ULg) Dr. Matt OROSZ (MIT) Pr. Harry.](https://reader030.fdocuments.us/reader030/viewer/2022012913/56649ed05503460f94bdeec8/html5/thumbnails/1.jpg)
Non-constant wall thickness scroll expander investigation for a micro solar ORC power
plantb y
I r. R é m i D I C K E S ( M I T / U L g )D r. M a t t O R O S Z ( M I T )
P r. H a r r y H E M O N D ( M I T )
Conference Presentation
AMSE-ORC 2013 Rotterdam – October 8th 2013
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PRESENTATION STRUCTURE
1) Context and Issues
2) Optimal scroll geometries selection
3) CAD modeling of a single stage prototype
4) Prototype fabrication and assembly
5) Conclusion and perspectives
1
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CONTEXT AND
ISSUES
PART 1 2
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1. Context and Issues
Environmental concerns
Electricity access in
developing countries
Favorable insolation conditions
MicroCSP = Micro “Concentrated Solar Power” plant |||| ORC = Organic Rankine Cycle
MicroCSP
Photovoltaic
3
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1. Context and Issues
Environmental concerns
Electricity access in
developing countries
Favorable insolation conditions
MicroCSP = Micro “Concentrated Solar Power” plant |||| ORC = Organic Rankine Cycle
MicroCSP
Photovoltaic
• Thermal storage Batteries
• Cogeneration available
• Hybridization with a back up generator
3
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1. Context and Issues
MicroCSP description:
MicroCSP = micro ‘Solar Power Power’ plant
1) Sun rays
2) Parabolic trough collectors
3) ORC unit
4) Off-grid electric load
5) Ambient air
6) Thermal storage
4
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1. Context and Issues
MicroCSP description:
MicroCSP = micro ‘Solar Power Power’ plant
Operating conditions (Tev/Tcond)
Low Carnot efficiency
Improve expansion device
4
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1. Context and Issues
MicroCSP description:
MicroCSP = micro ‘Solar Power Power’ plant
4
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1. Context and Issues
Motivations for a new design of scroll expander
Optimized internal volumetric ratios
Two-stage/single-shaft architecture Single signal frequency f and output voltage V Half of the power electronic required cheaper and more
simple
Variable wall thickness profile More compact expansion device Heat and mechanical losses reduced
5
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1. Context and Issues
Motivations for a new design of scroll expander:
Optimized internal volumetric ratios
Two-stage/single-shaft architecture Single signal frequency f and output voltage V Half of the power electronic required cheaper and more
simple
Variable wall thickness profile More compact expansion device Heat and mechanical losses reduced
5
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1. Context and Issues
Motivations for a new design of scroll expander:
Optimized internal volumetric ratios
Two-stage/single-shaft architecture Single signal frequency f and output voltage V Half of the power electronic required cheaper and more
simple
Variable wall thickness profile More compact expansion device Heat and mechanical losses reduced
prop. to ηis
5
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OPTIMAL SCROLL GEOMETRIES SELECTION
PART 2 6
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2. Optimal scroll geometries selection
Operating requirements given by a steady-state model (EES)
135°C 35°C 5kW R245fa 3000 rpm =
rv,1st = 4.9
rv,2nd = 3.36
=0.15 kg/s
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2. Optimal scroll geometries selection
Minimum wall thickness requirement Cantilever beam theory :
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2. Optimal scroll geometries selection
Danfoss frame
26.000 scrolls
database
26 candidates
2 geometries selected
rv criteria Deterministic modelingCF ranking
sx = c1 + c2 φ + c3 φ² + c4 φ³ +c5 φ4
R, d and N1 geometry 8 parameters
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2. Optimal scroll geometries selection
26.000 scrolls
database
26 candidates
2 geometries selected
rv criteria Deterministic modelingCF ranking
prop. to
ηis
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2. Optimal scroll geometries selection
26.000 scrolls
database
26 candidates
2 geometries selected
rv criteria Deterministic modelingCF ranking
Increasing wall
thickness
Decreasing wall
thickness
Constant wall
thickness
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2. Optimal scroll geometries selection
26.000 scrolls
database
26 candidates
2 geometries selected
rv criteria Deterministic modelingCF ranking
Deterministic model of a scroll expander taking into account
Radial and flank leakages Intake and exhaust throttling losses Friction losses between the scrolls Mechanical losses into the bearings
ηis , , FF
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2. Optimal scroll geometries selection
1st stage:
2nd stage:
Full expansion: ηis,tot = 68.6 %
26.000 scrolls
database
26 candidates
2 geometries selected
rv criteria Deterministic modeling
o η1st,is = 73.12%
o highest CF among candidates
o = 3.03 kW
o η2nd,is = 66.14 %
o highest CF among candidates
o = 2.5 kW
CF ranking
12
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2. Optimal scroll geometries selection
1st stage:
2nd stage:
Full expansion: ηis,tot = 68.6 %
26.000 scrolls
database
26 candidates
2 geometries selected
rv criteria Deterministic modeling
o η1st,is = 73.12%
o highest CF among candidates
o = 3.03 kW
o η2nd,is = 66.14 %
o highest CF among candidates
o = 2.5 kW
CF ranking
12
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2. Optimal scroll geometries selection
Losses study
Losses modeled First stage Second stage
---- η (%) Δη (%) η (%) Δη (%)
Inlet/Outlet Throttling losses 97.19 - 88.7 -
Same as the previous + Mechanical losses
82.77 14.43 68.75 19.95
Same as the previous + Flank leakages 77.26 5.51 68.02 0.73
Same as the previous + Radial leakages 73.67 3.59 66.68 1.34
Same as the previous + Heat losses 73.12 0.55 66.14 0.54
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2. Optimal scroll geometries selection
Losses study
Losses modeled First stage Second stage
---- η (%) Δη (%) η (%) Δη (%)
Inlet/Outlet Throttling losses 97.19 - 88.7 -
Same as the previous + Mechanical losses
82.77 14.43 68.75 19.95
Same as the previous + Flank leakages 77.26 5.51 68.02 0.73
Same as the previous + Radial leakages 73.67 3.59 66.68 1.34
Same as the previous + Heat losses 73.12 0.55 66.14 0.54
Main source : mechanical losses
13
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2. Optimal scroll geometries selection
Losses study : mechanical source analysis
Losses source First stage Second stage
Thrust bearing 42.1 W 74.06 W
Journal bearing (top) 269.8 W 276.3 W
Journal bearing (low) 179.9 W 184.2 W
Scroll friction 33.07 W 181.6 W
TOTAL ≈530 W ≈ 720 W
14
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2. Optimal scroll geometries selection
Performance enhancement?
Design A B C
Wall thickness profile Constant Constant Decreasing
Volumetric ratio
2,8 (both stages) Optimized Optimized
5.04 kW 5.45 kW 5.5 kW
ηis,tot 62.4 % 67.43 % 68.6 %
Δ ηis,tot = + 6.2%
Δ ηis,tot = 5.03%
Δ ηis,tot = 1.17 %
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2. Optimal scroll geometries selection
Performance enhancement?
Design A B C
Wall thickness profile Constant Constant Decreasing
Volumetric ratio
2,8 (both stages) Optimized Optimized
5.04 kW 5.45 kW 5.5 kW
ηis,tot 62.4 % 67.43 % 68.6 %
Δ ηis,tot = + 6.2%
Δ ηis,tot = 5.03%
Δ ηis,tot = 1.17 %
15
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2. Optimal scroll geometries selection
Performance enhancement?
Design A B C
Wall thickness profile Constant Constant Decreasing
Volumetric ratio
2,8 (both stages) Optimized Optimized
5.04 kW 5.45 kW 5.5 kW
ηis,tot 62.4 % 67.43 % 68.6 %
Δ ηis,tot = + 6.2%
Δ ηis,tot = 5.03%
Δ ηis,tot = 1.17 %
15
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2. Optimal scroll geometries selection
Performance enhancement?
Design A B C
Wall thickness profile Constant Constant Decreasing
Volumetric ratio
2,8 (both stages) Optimized Optimized
5.04 kW 5.45 kW 5.5 kW
ηis,tot 62.4 % 67.43 % 68.6 %
Δ ηis,tot = + 6.2%
Δ ηis,tot = 5.03%
Δ ηis,tot = 1.17 %
15
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CAD MODELING OF A SINGLE-STAGE
PROTOTYPE
PART 3
CAD = ‘Computer-Aided Design’
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3. CAD modeling of a single-stage prototype
CAD modeling
SolidWorks 2012
Architecture derived from Copeland compressors (ZR series)
Expander: 30 assembled pieces
CAD = ‘Computer-Aided Design’
17
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3. CAD modeling of a single-stage prototype
Mechanical viability checked by a 60% scale 3D-printed model (FDM printer)
Oil delivery circuit/BPC control system
CAM with HSMXpress
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3. CAD modeling of a single-stage prototype
Mechanical viability checked by a 60% scale 3D-printed model (FDM printer)
Oil delivery circuit andBPC control system
CAM with HSMXpress
18
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3. CAD modeling of a single-stage prototype
Mechanical viability checked by a 60% scale 3D-printed model (FDM printer)
Oil delivery circuit and BPC control system
CAM with HSMXpress
CAM = ‘Computer-Aided Manufacturing’
18
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PROTOTYPE FABRICATION
AND ASSEMBLY
PART 4 19
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4. Prototype fabrication and assembly20
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4. Prototype fabrication and assembly21
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4. Prototype fabrication and assembly22
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CONCLUSIONAND
PERSPECTIVES
PART 5 23
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5. Conclusion & Perspectives
Finish the single-stage prototype Check the envelope sealing Instrumentation Oil delivery circuit
& BPC circuit piping
Experimental test and validation Test rig at Eckerd College (FL) Validate the deterministic model (Update the second stage geometry)
Design and fabrication of the two-stage prototype
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5. Conclusion & Perspectives
Finish the single-stage prototype Check the envelope sealing Instrumentation Oil delivery circuit
& BPC circuit piping
Experimental test and validation Test rig at Eckerd College (FL) Validate the deterministic model (Update the second stage geometry)
Design and fabrication of the two-stage prototype
24
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Test rig (Eckerd College – FL)
Condenser
HTF tank
Collectors
ORC unit
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5. Conclusion & Perspectives
Finish the single-stage prototype Check the envelope sealing Instrumentation Oil delivery circuit
& BPC circuit piping
Experimental test and validation Test rig at Eckerd College (FL) Validate the deterministic model (Update the second stage geometry)
Design and fabrication of the two-stage prototype
26
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Thank you for your attention
QUESTIONS ?
More information : Design and fabrication of a variable wall thickness two-stage scroll expander to be integrated in micro-solar power plant - Master thesis – Rémi DICKES
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APPENDIX
Variable wall thickness geometries Danfoss frame
1 geometry 8 parameters
Warning : non reversible process! random generation
Select the best candidates among a database
sx = c1 + c2 φ + c3 φ² + c4 φ³ +c5 φ4
R, d and N
All parameter combinations are not
viable
Only exploring viable parameter domains
Using a hierarchical parameter selection strategy
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APPENDIX
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APPENDIX
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APPENDIX