Download - eurammon Natural Refrigeration Award 2020
eurammon Natural Refrigeration Award 2020
Lecture event, October 9, 2020
2
Programme and Presentations
8:30 – 8:40 Welcome and Introduction of the Award WinnersMonika Witt - TH. WITT Kältemaschinenfabrik GmbH, eurammon Vice Chair
8:40 – 9:10 Winner 1st place - Benjamin Zühlsdorf DTU Technical University of Denmark“High-performance heat pump systems - Enhancing performance and rangeof heat pump systems for industry and district heating”
9:10 – 9:40 Winner 2nd place - Maaike Leichsenring Delft University of Technology, Netherlands“Flow visualization of downward condensing ammonia in a gasketed plate heat exchanger”
9:40 –10:10 Winner 3rd place - Fabio Giunta KTH – Royal Institute of Technology, Sweden“Techno-economic assessment of CO2 refrigeration systems with geothermal integration,a field measurements and modelling analysis”
10:10 – 10:30 Q&A session and closing remarksAndrew Stockman, Managing Director for Europe and the Middle East at EVAPCO EuropeGroup and eurammon executive board
The future is Natural!
3
The smartest decision is to leapfrog other refrigerant options and turn to the natural choices…
eurammon Natural Refrigeration Award 2020High-performance heat pump systems
Enhancing performance and range of heat pump systems for
industry and district heating
Webinar, October 9, 2020 – Benjamin Zühlsdorf, Technical University of Denmark
Agenda
High-performance heat pump systems 2
• Zeotropic working fluids in heat pumps
− Motivation and potential
− Screening procedure
− Optimization of cycle and working fluid
− Summary and outlook
• [High-temperature heat pumps]
ThermCyc
Efficient use of low-temperature heat sources
High-performance heat pump systems 3
March 2014 – February 2019
Hypothesis:
Low-temperature heat sources represent a favorable energy source.
There is a great potential to enhance their utilization by:
- Novel cycle layouts
- Utilization of working fluid mixtures
- Improved component design
Tem
pera
ture
Heat
PumpORCPower Power
http://www.thermcyc.mek.dtu.dk/
Project Partners
HP
Heat Sink
(District heating)75 °C50 °C
50 °C 25 °CHeat Source
(Data Center)
Motivation and potential
Use of zeotropic working fluid mixtures
High-performance heat pump systems 4
75 °C50 °C 50 °C 25 °C
Motivation and potential
Use of zeotropic working fluid mixtures
High-performance heat pump systems 5
Super-
Heater
Heat Sink
Source InSource Out
Sink OutSink In
Condenser Desuper-
Heater
Sub-
Cooler
Evaporator
Throttling
Valve Compressor
Heat Source
75 °C50 °C 50 °C 25 °C
Motivation and potential
Use of zeotropic working fluid mixtures
High-performance heat pump systems 6
Super-
Heater
Heat Sink
Source InSource Out
Sink OutSink In
Condenser Desuper-
Heater
Sub-
Cooler
Evaporator
Throttling
Valve Compressor
Heat Source
75 °C50 °C 50 °C 25 °C
Motivation and potential
Use of zeotropic working fluid mixtures
High-performance heat pump systems 7
Exergy
Product48%
Compressor
21%
TV 5%
Evaporator
14%
Condenser
12%
Exergy
Destruction52%
Exergetic Efficiency = 48 %
75 °C50 °C 50 °C 25 °C
Motivation and potential
Use of zeotropic working fluid mixtures
High-performance heat pump systems 8
ሶ𝐸D,fluid
ሶ𝐸D,pinch
ሶ𝐸D,fluid
Exergy
Product48%
Compressor
21%
TV 5%
HX (Pinch) 5%
HX (Fluid)
21%
Exergy
Destruction52%
Exergetic Efficiency = 48 %
75 °C50 °C 50 °C 25 °C
Motivation and potential
Use of zeotropic working fluid mixtures
High-performance heat pump systems 9
ሶ𝐸D,fluid
ሶ𝐸D,pinch
ሶ𝐸D,fluid
ሶ𝐸D,fluid
ሶ𝐸D,pinch
ሶ𝐸D,fluid
Motivation and potential
Relating exergy destruction and COP
High-performance heat pump systems 10
6.1
6.1
5.8
6.3
10.8
10.7
43.4
29.2
24.8
2.1
19.3
1.7
0 20 40 60 80 100 120
Butane
30 % DME /
70 % Isopentane
ĖD / ĖP, %
Pinch (Sink)
Pinch (Source)
Valve
Compressor
Fluid (Source)
Fluid (Sink)
2
4
6
8
10
12
14
CO
P
COP75 °C50 °C 50 °C 25 °C
Screening procedure
Case study: Data Center to District heating
High-performance heat pump systems 11
75 °C50 °C 50 °C 25 °C
Screening procedure
Case study: Data Center to District heating
High-performance heat pump systems 12
75 °C50 °C 50 °C 25 °C
Screening procedure
How to find promising mixtures?
High-performance heat pump systems 13
DME/
Isopentane
Propylene/
R-1234ze(Z)
DEE/
R-1234ze(E)
Hexane/
R-1234ze(Z)
DME/
DEE
Propylene/
Butane
Boundary
conditions
List of fluids
Pre-Screening
Energy
Analysis
Further Analysis
and Optimization
Post-Screening
Technical
Analysis
Economic
Analysis
Screening
Screening procedure
Case study: Data Center to District heating
High-performance heat pump systems 14
75 °C50 °C 50 °C 25 °C
Screening procedure
Case study: Data Center to District heating
High-performance heat pump systems 15
75 °C50 °C 50 °C 25 °C
• Pure fluids:
− COP around 4.5
− Lower ch mainly due to lower TCIspec
• Mixtures:
− Higher TCIspec allows for higher COP
− Increase in COP compensates higher
TCIspec
Screening procedure
Underlying assumptions for comparisons
High-performance heat pump systems 16
75 °C50 °C 50 °C 25 °C
a) Fixed Pinch
− Simple design approach for each fluid
− Requires design experience
− Yields economically fair results
b) Fixed HX Investment
− Total investment in HX area fixed to result from ammonia in
a)
− Distribution to source/sink of area optimized
− Results were biased by choice of area/investment
c) Optimized area w.r.t. NPV
− Investment in HX area optimized w.r.t. NPV
− Numerically more demanding
Optimization of cycle and working fluid
Standard cycle
High-performance heat pump systems 17
HP
Heat Sink
(District heating)70 °C40 °C
20 °C 10 °CHeat Source
(e.g., process cooling)
Optimization of cycle and working fluid
Standard cycle
High-performance heat pump systems 18
HP
Heat Sink
(District heating)70 °C40 °C
20 °C 10 °CHeat Source
(e.g., process cooling)
70 °C40 °C 20 °C 10 °C
Super-
Heater
Heat Sink
Source InSource Out
Sink OutSink In
CondenserDesuper-
Heater
Sub-
Cooler
Evaporator
Throttling
ValveCompressor
Heat Source
Optimization of cycle and working fluid
Standard cycle
High-performance heat pump systems 19
HP
Heat Sink
(District heating)70 °C40 °C
20 °C 10 °CHeat Source
(e.g., process cooling)
70 °C40 °C 20 °C 10 °C
Super-
Heater
Heat Sink
Source InSource Out
Sink OutSink In
CondenserDesuper-
Heater
Sub-
Cooler
Evaporator
Throttling
ValveCompressor
Heat Source
Optimization of cycle and working fluid
Standard cycle
High-performance heat pump systems 20
HP
Heat Sink
(District heating)70 °C40 °C
20 °C 10 °CHeat Source
(e.g., process cooling)
70 °C40 °C 20 °C 10 °C
No superheating in
evaporatorSuper-
Heater
Heat Sink
Source InSource Out
Sink OutSink In
CondenserDesuper-
Heater
Sub-
Cooler
Evaporator
Throttling
ValveCompressor
Heat Source
Optimization of cycle and working fluid
Internal Heat Exchanger cycle
High-performance heat pump systems 21
HP
Heat Sink
(District heating)70 °C40 °C
20 °C 10 °CHeat Source
(e.g., process cooling)
70 °C40 °C 20 °C 10 °C
Heat Sink
Source InSource Out
Sink OutSink In
CondenserDesuper-
Heater
Sub-
Cooler
EvaporatorInternal
HX
Throttling
Valve
Compressor
Heat Source
Optimization of cycle and working fluid
Internal Heat Exchanger cycle
High-performance heat pump systems 22
HP
Heat Sink
(District heating)70 °C40 °C
20 °C 10 °CHeat Source
(e.g., process cooling)
70 °C40 °C 20 °C 10 °C
No Superheating in
IHX
Heat Sink
Source InSource Out
Sink OutSink In
CondenserDesuper-
Heater
Sub-
Cooler
EvaporatorInternal
HX
Throttling
Valve
Compressor
Heat Source
Optimization of cycle and working fluid
Internal Heat Exchanger cycle
High-performance heat pump systems 23
HP
Heat Sink
(District heating)70 °C40 °C
20 °C 10 °CHeat Source
(e.g., process cooling)
70 °C40 °C 20 °C 10 °C
Partial
Evaporation &
Superheating in
Internal HX
Heat Sink
Source InSource Out
Sink OutSink In
CondenserDesuper-
Heater
Sub-
Cooler
EvaporatorInternal
HX
Throttling
Valve
Compressor
Heat Source
Optimization of cycle and working fluid
Overview results
High-performance heat pump systems 24
70 °C40 °C 20 °C 10 °C
a)
b)
c)d)
e)f)
23456789
CO
P
COP
22.4
21.2
20.2
18.7
18.0
17.9
9.3
11.6
12.6
3.8
4.7
3.2
11.7
8.0
4.7
7.0
4.8
4.9
20.9
16.6
14.1
17.9
14.8
14.8
1.0
1.1
1.6
0 10 20 30 40 50 60 70 80
a) Std-Cycle, 5 K SH
Butane
b) Std-Cycle, 5 K SH
20 % Propane / 80 % Butane
c) Std-Cycle, 0 K SH
50 % Propane / 50 % Butane
d) IHX-Cycle, 5 K SH
10 % Propane / 90 % Butane
e) IHX-Cycle, 0 K SH
30 % Propane / 70 % Butane
f) IHX-Cycle, qevap= opt
30 % Propane / 70 % Butane
ĖD / ĖP, %
Compressor Valve Evaporator Condenser Internal HX
qevap,out = opt
Zeotropic working fluids in heat pumps
Summary and outlook
High-performance heat pump systems 25
• Heat pump applications often show temperature glides (contrary to refrigeration systems)
• Conclusions:
− Large potential for zeotropic working fluid mixtures
⬧ COP increases >30 %
⬧ Higher COP can compensate additional investment
− Temperature glide matching possible
⬧ Glide match on source side has dominating impact
⬧ Further influence from e.g., compression & expansion
− Screening required for identifying promising fluids
− Cycle layout
⬧ Considerable increases possible using standard cycle
⬧ Further improvements obtainable by cycle optimization (e.g., IHX, reduction of superheating, …)
• Challenges
− Design procedure following the screening procedure
− Experimental validation of these procedures
Benjamin Zühlsdorf
Consultant
Energy and Climate
+45 72201258
Thank you for your attention!
1/32
eurammon Natural Refrigeration Award 2020
Flow visualization of downward condensing
ammonia inside a gasketed plate heat exchanger
Webinar, October 9, 2020
Maaike Leichsenring
2/35
Content
Introduction
Experimental setup
Flow visualization experiments
Data analysis and evaluation
Conclusions & Recommendations
University
of
Technology
1/22‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
3/35
IntroductionOTEC – by means of Ammonia
4/35
Introduction
Setup
Experiments
Analysis
Conclusions
2/22
Ocean Thermal Energy Conversion• Renewable• Natural Refrigerant
OTEC
Ammonia• Zero GWP & ODP• High availability
PHEPlate Heat Exchanger• Condensing ammonia
1
2 4
3
‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
Introduction
OTEC – by means of Ammonia
5/35
Introduction
Setup
Experiments
Analysis
Conclusions
Expected
Flow patterns influence the performance
Better predictions of flow patterns enhance the accuracy
of performance calculations
Benefits
• Favourable heat transfer
coefficients
• Compactness
• Design flexibility
• Thermal effectiveness
Challenge
• Two-phase behaviour
not yet fully understood
• Over- and underestimating
heat transfer and pressure
drop correlations
IntroductionPlate heat exchangers (PHEs)
3/22‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
6/35
IntroductionFlow patterns
FilmSlug ChurnBubbly
4 main flow patternsGeometric configuration
of vapor and liquid
Occurring flow pattern in the
PHE generally unknown
Liquid
Vapor
4/22
Introduction
Setup
Experiments
Analysis
Conclusions
‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
7/35
IntroductionResearch question
Scientific knowledge gapNo information is available on flow patterns of
condensing ammonia in corrugated PHE’s
Main research question’Which flow patterns are dominant inside the PHE condenser
and how do they relate to its performance?’
ApproachPerforming flow visualization experiments
and data analysis
5/22
Introduction
Setup
Experiments
Analysis
Conclusions
‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
8/35
Experimental setupTest section
9/35
Water(cold)
6/22
Introduction
Setup
Experiments
Analysis
Conclusions
‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
Experimental setupTest section
10/35
100W small scale setup
• Organic Rankine Cycle
• Pure ammonia
• OTEC purposes
High speed camera
LED
Visualization plate
ammonia
PHEVisualization section
• Plate heat exchanger
• LED illumination
• 3000 fps camera
• Visualization plate
Water(cold)• Visualization plate
Similar components to
Refrigeration cycle
7/22
Introduction
Setup
Experiments
Analysis
Conclusions
‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
Experimental setupTest section
11/35
Experimental setupMaterial selection
Requirements visualization plate
Chemically resistant to ammonia
High mechanical performance
Transparent
Easy to machine
• Chemical resistance charts
• Actual chemical resistance
Contradicting Chemically resistant to ammonia
Chemical resistance tests
• Transparent materials
• Liquid ammonia
• Four days
Glass PS PMMAPS / PMMA
Introduction
Setup
Experiments
Analysis
Conclusions
8/22‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
12/35
Experimental setupFinal setup
PS
PMMA
Top layer
• Corrugated PS layer (4.75 mm)
• Chemically resistant
Base plate
• PMMA (20 mm)
• High mechanical performance
9/22
Introduction
Setup
Experiments
Analysis
Conclusions
‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
13/35
Experimental setupFinal setup
PS
10/22
Introduction
Setup
Experiments
Analysis
Conclusions
‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
14/35
Visualization experimentsTest conditions
15/35
Vapor quality
𝑥 =𝑚𝑉
𝑚𝑉+𝑚𝐿[-]
Mass flux
𝐺 =ሶ𝑚𝑎
𝐴𝑐ℎ𝑎𝑛𝑛𝑒𝑙[kgm−2s−1]
Varying parameters 𝐺, 𝑥
Introduction
Setup
Experiments
Analysis
Conclusions
11/22‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
Visualization experimentsTest conditions
16/35
Vapor quality
𝑥 =𝑚𝑉
𝑚𝑉+𝑚𝐿[-]
𝑥 [-]
𝐺[kgm
−2s−
1]
Varying parameters 𝐺, 𝑥
𝑃Condenser 7 [bar]
𝑇cold water 10 [°𝐶]
Constant parameters
Conditions chosen for
OTEC applications
Introduction
Setup
Experiments
Analysis
Conclusions
12/22‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
Visualization experimentsTest conditions
17/35
Visualization experimentsFlow path & flow pattern
1
Film flow
Separated flow
‘Dry’ zone
13/22
Introduction
Setup
Experiments
Analysis
Conclusions
‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
18/35
Visualization experimentsFlow path & flow pattern
Film flow
Separated flow
‘Dry’ zone
14/22
Introduction
Setup
Experiments
Analysis
Conclusions
‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
43≤ 𝐺 ≤ 64 [kgm−2s−1] 64 > 𝐺 ≥ 91 [kgm−2s−1]
19/35
Visualization experimentsInfluence of 𝐺
𝐺 = 43 [kgm−2s−1] 𝐺 = 64 [kgm−2s−1] 𝐺 = 81 [kgm−2s−1]
15/22
𝐺 = 43[kgm−2s−1]
𝑥= 0.22 𝑥 = 0.48 𝑥 = 0.62
Partial film flow
‘Dry zone’
Introduction
Setup
Experiments
Analysis
Conclusions
‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
20/35
Visualization experimentsInfluence of 𝑥
Partial film flow Partial film flow Film flow
𝑥 = 0.3 [−]
𝐺 = 43 [kgm−2s−1] 𝐺 = 64 [kgm−2s−1] 𝐺 = 81 [kgm−2s−1]
16/22
‘Dry zone’
Introduction
Setup
Experiments
Analysis
Conclusions
‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
21/35
Data analysisDry zone fraction
22/35
Introduction
Setup
Experiments
Analysis
Conclusions
17/22‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
Data analysisDry zone fraction
23/35
Dry-zone fraction
𝜖𝐴 =𝐴𝑑𝑟𝑦
Aplate%
Matlab image processing
Assumptions
• Dynamic Fluid = 𝑓 𝑡• Static dry area ≠ 𝑓(𝑡)
𝐺 = 64 [kgm−2s−1]
𝑥 = 0.2 [-]
𝐺 = 43 [kgm−2s−1]
𝑥 = 0.3 [-]
𝜖𝐴 = …% ?
Conclusion
𝜖𝐴 increases with 𝑥𝜖𝐴 decreases with 𝐺
Introduction
Setup
Experiments
Analysis
Conclusions
18/22‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
Data analysisDry zone fraction
24/35
Data analysisHeat transfer vs. flow pattern
𝜖 𝐴[−]
Conclusion
Partial film flow and film flow show
different heat transfer characteristics
Partial film flow is preferred flow
pattern w.r.t. heat transfer
𝜖𝐴 trendline𝜖𝐴 Matlab data pointsHTCs partial film flowHTCs film flow*
𝛼𝑎Wm
−2K−1
∙103
𝑅𝑒𝐿[−]
19/22
Introduction
Setup
Experiments
Analysis
Conclusions
‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
25/35
Data analysis Flow pattern maps (FPMs)
FPMs:
• Prediction tools
• Describe which flow pattern is expected
Experimental results do not agree with
FPM
Experimental results
20/22
General FPM by Tao et al. (2018):
• vertical downward PHEs
• Mainly air-water
• Expected applicable for ammonia
Introduction
Setup
Experiments
Analysis
Conclusions
‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
26/35
Data analysis Flow pattern maps (FPMs)
FPMs:
• Prediction tools
• Describe which flow pattern is expected
Proposed new FPM
• Downward condensing ammonia
• PHEs, current geometry
21/22
General FPM by Tao et al. (2018):
• vertical downward PHEs
• Mainly air-water
• Expected applicable for ammonia
Can be used to optimize accuracy of FPM
by Tao et al. (2018)
Introduction
Setup
Experiments
Analysis
Conclusions
‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
27/35‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
Conclusions & recommendations
28/35
RecommendationsConclusions
Flow patterns
• Partial film flow
• Film flow
Partial film flow
• 𝐺 ≤ 64 kgm−2s−1
• 𝜖𝐴 increases with 𝑥
Film flow
• 𝐺 ≥ 81 [kgm−2s−1]
Flow pattern maps (FPMs)
• Results contradict FPMs
• New FPM is proposed
Performance calculations
• Flow patterns show different
Heat transfer characteristics
• Use results to improveperformance calculations
Perform more flow visualization
experiments with ammonia
In order to:
• Improve performance calculations
• Prevent faulty heat exchanger design
• Reduce unnecessary costs
In Natural Refrigeration applications.
Introduction
Setup
Experiments
Analysis
Conclusions
Main research question’Which flow patterns are dominant inside the PHE condenser
and how do they relate to its performance?’
22/22‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
Conclusions & recommendations
29/35
RecommendationsConclusions
Flow patterns
• Partial film flow
• Film flow
Partial film flow
• 𝐺 ≤ 64 kgm−2s−1
• 𝜖𝐴 increases with 𝑥
Film flow
• 𝐺 ≥ 81 [kgm−2s−1]
Flow pattern maps (FPMs)
• Results contradict FPMs
• New FPM is proposed
Performance calculations
• Flow patterns show different
Heat transfer characteristics
• Use results to improveperformance calculations
Perform more flow visualization
experiments with ammonia
In order to:
• Improve performance calculations
• Prevent faulty heat exchanger design
• Reduce unnecessary costs
In Natural Refrigeration applications.
Introduction
Setup
Experiments
Analysis
Conclusions
Main research question’Which flow patterns are dominant inside the PHE condenser
and how do they relate to its performance?’
15/15‘Flow visualization of downward condensing ammonia in a Gasketed Plate Heat Exchanger’
Conclusions & recommendations
Questions?
Name Maaike Leichsenring
Country Netherlands
Phone +316-41913087
Mail [email protected]
eurammon Natural Refrigeration Award 2020Techno-economic assessment of CO2 refrigeration systems with
geothermal integration
Fabio Giunta - KTH – Royal Institute of Technology, Sweden
Webinar, October 9, 2020
Agenda
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 2
• Objectives
• Introduction
• Field measurements analysis
• Techno-economic analysis of the geothermal integration
• Conclusion & future work
Objectives
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 3
In relation to supermarkets’ CO2 refrigeration systems integrated with geothermal storage
• Assess the heat recovery control strategy
• Evaluate the efficiency of the heat recovery system
• Assess the economic savings related to the geothermal storage
• Identify the most important parameters affecting the cost-effectiveness
• Suggest relevant future work
Introduction Field Measurements Techno-economic Assessment Conclusions
Introduction - Supermarkets’ CO2 Transcritical Booster System
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 4
Cabinets
Freezers
MT
LT
Outdoor
Heat Recovery
Introduction Field Measurements Techno-economic Assessment Conclusions
The most common CO2 refrigeration system installed in supermarkets is a transcritical booster system. In
these systems the heat recovered can cover both tap water and space heating demand. The heat is
recovered in the so-called “heat pump mode”. This consists of increasing the discharge pressure of the MT
compressors to recover heat at higher temperatures. When the system performs a transcritical cycle the
COP heat recovery is particularly high, thanks to the properties of the refrigerant.
Introduction - Supermarkets’ CO2 Transcritical Booster System
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 5
Cabinets
Freezers
MT
LT
Outdoor
Heat Recovery
Introduction Field Measurements Techno-economic Assessment Conclusions
The most common CO2 refrigeration system installed in supermarkets is a transcritical booster system. In
these systems the heat recovered can cover both tap water and space heating demand. The heat is
recovered in the so-called “heat pump mode”. This consists of increasing the discharge pressure of the MT
compressors to recover heat at higher temperatures. When the system performs a transcritical cycle the
COP heat recovery is particularly high, thanks to the properties of the refrigerant.
Cabinets
Freezers
MT
LT
Outdoor
Heat Recovery
Introduction - Supermarkets’ CO2 Transcritical Booster System
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 6
50 bar
Introduction Field Measurements Techno-economic Assessment Conclusions
The most common CO2 refrigeration system installed in supermarkets is a transcritical booster system. In
these systems the heat recovered can cover both tap water and space heating demand. The heat is
recovered in the so-called “heat pump mode”. This consists of increasing the discharge pressure of the MT
compressors to recover heat at higher temperatures. When the system performs a transcritical cycle the
COP heat recovery is particularly high, thanks to the properties of the refrigerant.
Introduction - Supermarkets’ CO2 Transcritical Booster System
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 7
65 bar
Cabinets
Freezers
MT
LT
Outdoor
Heat Recovery
Introduction Field Measurements Techno-economic Assessment Conclusions
The most common CO2 refrigeration system installed in supermarkets is a transcritical booster system. In
these systems the heat recovered can cover both tap water and space heating demand. The heat is
recovered in the so-called “heat pump mode”. This consists of increasing the discharge pressure of the MT
compressors to recover heat at higher temperatures. When the system performs a transcritical cycle the
COP heat recovery is particularly high, thanks to the properties of the refrigerant.
Introduction - Supermarkets’ CO2 Transcritical Booster System
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 8
75 bar
Cabinets
Freezers
MT
LT
Outdoor
Heat Recovery
Introduction Field Measurements Techno-economic Assessment Conclusions
The most common CO2 refrigeration system installed in supermarkets is a transcritical booster system. In
these systems the heat recovered can cover both tap water and space heating demand. The heat is
recovered in the so-called “heat pump mode”. This consists of increasing the discharge pressure of the MT
compressors to recover heat at higher temperatures. When the system performs a transcritical cycle the
COP heat recovery is particularly high, thanks to the properties of the refrigerant.
Introduction - Supermarkets’ CO2 Transcritical Booster System
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 9
The most common CO2 refrigeration system installed in supermarkets is a transcritical booster system. In
these systems the heat recovered can cover both tap water and space heating demand. The heat is
recovered in the so-called “heat pump mode”. This consists of increasing the discharge pressure of the MT
compressors to recover heat at higher temperatures. When the system performs a transcritical cycle the
COP heat recovery is particularly high, thanks to the properties of the refrigerant.
Cabinets
Freezers
MT
LT
Outdoor
Heat Recovery
Introduction Field Measurements Techno-economic Assessment Conclusions
90 bar
Introduction - Supermarkets’ CO2 Transcritical Booster System
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 10
The most common CO2 refrigeration system installed in supermarkets is a transcritical booster system. In
these systems the heat recovered can cover both tap water and space heating demand. The heat is
recovered in the so-called “heat pump mode”. This consists of increasing the discharge pressure of the MT
compressors to recover heat at higher temperatures. When the system performs a transcritical cycle the
COP heat recovery is particularly high, thanks to the properties of the refrigerant.
Cabinets
Freezers
MT
LT
Heat Recovery
Introduction Field Measurements Techno-economic Assessment Conclusions
Gas Cooler
by-pass
Introduction - CO2 Transcritical Booster System with geothermal integration
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 11
In the coldest period of the year, when the heat recovered from cabinets and freezers
cannot cover the heating demand, heat is extracted from the geothermal storage. Since in
summer, the ground is colder than the outdoor air, the geothermal storage is “re-charged”
sub-cooling the refrigerant. Parallel compressors are used to extract heat from the ground.
Introduction Field Measurements Techno-economic Assessment Conclusions
Introduction - CO2 Transcritical Booster System with geothermal integration
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 12
In the coldest period of the year, when the heat recovered from cabinets and freezers
cannot cover the heating demand, heat is extracted from the geothermal storage. Since in
summer, the ground is colder than the outdoor air, the geothermal storage is “re-charged”
sub-cooling the refrigerant. Parallel compressors are used to extract heat from the ground.
Introduction Field Measurements Techno-economic Assessment Conclusions
Electricity is the only energy vector, no gas, no district heating
Introduction - CO2 Transcritical Booster System with geothermal integration
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 13
In the coldest period of the year, when the heat recovered from cabinets and freezers
cannot cover the heating demand, heat is extracted from the geothermal storage. Since in
summer, the ground is colder than the outdoor air, the geothermal storage is “re-charged”
sub-cooling the refrigerant. Parallel compressors are used to extract heat from the ground.
Introduction Field Measurements Techno-economic Assessment Conclusions
Methodology
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 14
Introduction Field Measurements Techno-economic Assessment Conclusions
Field Measurements Analysis
Inputs as a function of the outdoor temperature
Modelling with BIN Hours Method
Model validation with Power Meters Readings
Geothermal Field Optimization and Techno-economic analysis
Sensitivity Analysis
Field Measurements – Cooling Demands
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 15
Cabinets
Freezers
MT
LT
0
20
40
60
80
100
120
-20 -10 0 10 20 30 40
Co
oli
ng
De
ma
nd
[k
W]
Outdoor Temperature [°C]
Cooling load averaged on the outdoor temperature
Cabinets Freezers
The typical cooling demand of the cabinets in a supermarket increases when the heating period
ends. This is due to a rise in indoor absolute humidity which is translated into a more frequent
defrosting in the cabinets. The cooling demand of the freezers is more stable since there is less
air exchange with the supermarket’s indoor environment
Introduction Field Measurements Techno-economic Assessment Conclusions
0
10
20
30
40
50
60
70
-20 -10 0 10 20 30 40
Po
wer
[kW
]
Outdoor Temperature [°C]
Tap-water Heating averaged on the outdoor temperature
Field Measurements – Heat Recovery
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 16
0
20
40
60
80
100
-15 -10 -5 0 5 10 15 20 25
Po
we
r [k
W]
Outdoor Temperature [°C]
Space Heating provided averaged on the outdoor temperature
The heat recovery system is driven by the space heating demand. The tap-water demand is
considered a secondary product. Therefore, the pressure is increased only when the space
heating demand requires it. This is the reason for a decrease in high-temperature heat (tap-
water) supply between 10 and 20°C. Electric resistances are used to provide the (small) extra
heating capacity for tap-water demand.
Introduction Field Measurements Techno-economic Assessment Conclusions
Field Measurements – COP Heat Recovery
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 17
𝐶𝑂𝑃𝐻𝑅 =𝑄𝐻𝑅𝑇𝑂𝑇
𝐸𝑇𝑂𝑇 − 𝐸𝑐𝑜𝑜𝑙 𝑜𝑛𝑙𝑦
-2
0
2
4
6
8
10
-20 -15 -10 -5 0 5 10 15
CO
P H
eat
Rec
ove
ry
Outdoor Temperature [°C]
COP Heat Recovery as a function of outdoor temperature
The electricity spent only for recovering the heat (𝐸𝑇𝑂𝑇 − 𝐸𝑐𝑜𝑜𝑙 𝑜𝑛𝑙𝑦)
is calculated as the total electricity spent (𝐸𝑇𝑂𝑇) and the electricity
that would have been spent if the system had satisfied only
the cooling load (𝑬𝒄𝒐𝒐𝒍 𝒐𝒏𝒍𝒚).
Introduction Field Measurements Techno-economic Analysis Conclusions
Field Measurements – COP Heat Recovery
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 18
𝐻𝑅𝑅 =𝑄𝐻𝑅𝑇𝑂𝑇
𝑄𝑐𝑜𝑜𝑙𝑖𝑛𝑔𝑀𝑇+ 𝑄𝑐𝑜𝑜𝑙𝑖𝑛𝑔𝐿𝑇
+ 𝐸𝐿𝑇𝑆ℎ𝑎𝑓𝑡
𝑄𝐻𝑅𝑇𝑂𝑇
𝑄𝑐𝑜𝑜𝑙𝑖𝑛𝑔𝑀𝑇
𝑄𝑐𝑜𝑜𝑙𝑖𝑛𝑔𝐿𝑇
𝐸𝐿𝑇𝑠ℎ𝑎𝑓𝑡
MT
LT
0
2
4
6
8
10
12
20% 40% 60% 80% 100% 120% 140% 160% 180% 200% 220%
CO
P H
eat
Rec
ove
ry
Heat Recovery Ratio HRR
COP Heat Recovery as a function of HRR
COP Heat Recovery (system as a whole)
Introduction Field Measurements Techno-economic Assessment Conclusions
Field Measurements – COP Heat Recovery
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 19
𝐶𝑂𝑃𝑔𝑒𝑜𝑒𝑥𝑡𝑟𝑎𝑐𝑡𝑖𝑜𝑛=
Qgeosupplied
𝐸𝑝𝑎𝑟𝑎𝑙𝑙𝑒𝑙 𝑐𝑜𝑚𝑝𝑟𝑒𝑠𝑠𝑜𝑟𝑠 + 𝐸𝑠𝑒𝑐𝑜𝑛𝑑𝑎𝑟𝑦 𝑝𝑢𝑚𝑝𝑠
0
2
4
6
8
10
12
20% 40% 60% 80% 100% 120% 140% 160% 180% 200% 220%
Hea
t R
eco
very
CO
P
Heat Recovery Ratio HRR
COP Heat Recovery as a function of HRR
COP Heat Recovery (system as a whole) COP Geothermal Heat Extraction
When the COP geothermal extraction and total COP heat recovery overlaps
it means that geothermal heat pump function is working in steady
conditions. This happens only during the peaks of heating demand. In
other words, the parallel compressors are forced to work in start-and-stop for
low values of HRR.
Introduction Field Measurements Techno-economic Assessment Conclusions
Field Measurements – Sub-cooling
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 20
0
5
10
15
20
25
30
35
40
-20 -10 0 10 20 30 40
CO
2Te
mp
erat
ure
[˚C
]
Outdoor Temperature [˚C]
Great Sub-cooling effect
Gas Cooler Outlet Temperature Expansion valve inlet Temperature
Heat recovery mode Floating Condensing
8% yearly electricity savings on the power consumed by the machine room
16 x 200m
Introduction Field Measurements Techno-economic Assessment Conclusions
(Over-dimensioned)
High-pressure expansion valve inlet temperature
Model validation - through power meters readings
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 21
11%
64%
18%
3% 4%
Annual electricity consumption for the refrigeration room
PC
MT
LT
Pumping
Gas Cooler Fans
0
20
40
60
80
100
-20 -10 0 10 20 30 40
Elec
tric
Po
wer
Co
nsu
mp
tio
n [
kW]
Outdoor Temperature [°C]
Model Results vs Field Measurements – Error ±7.5%
Average Power Consumption from power meters Average Power Consumption Calculated
Floating Condensing mode + ACHeat Recovery mode
A model representing the system was built to simulate the effect of
potential improvements and different sizes of the geothermal storage.
The model was validated comparing the expected power consumption
and the readings from the power meter installed in the machine room.
Introduction Field Measurements Techno-economic Assessment Conclusions
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 22
The amount of heat exchanged with the ground influences the
temperature of the secondary refrigerant which in turns influences the
amount of heat extracted (efficiency of the heat pump function) or
injected (capability to sub-cool the CO2). This means that the techno-
economic assessment needs to be solved through an iterative process!
Introduction Field Measurements Techno-economic Assessment Conclusions
How to size a geothermal storage for this application?
Techno-economic assessment
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 23
-50
-40
-30
-20
-10
0
10
20
30
40
50
0 1000 2000 3000 4000 5000 6000 7000 8000
Gro
un
d L
oad
[kW
]
Hours
Modelling Output - Ground Load
Heat Injection
Heat Extraction
Introduction Field Measurements Techno-economic Assessment Conclusions
The ground load represents the amount of heat extracted from or injected
into the ground in one year.
The ground is extremely unbalanced. This means the amount of heat
injected in summer is much more than the heat injected in winter. This
increases the necessary size of the storage reducing its cost-effectiveness.
Techno-economic assessment
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 24
-50
-40
-30
-20
-10
0
10
20
30
40
50
0 1000 2000 3000 4000 5000 6000 7000 8000
Gro
un
d L
oad
[kW
]
Hours
Modelling Output - Ground Load
Heat Injection
Heat Extraction
Introduction Field Measurements Techno-economic Assessment Conclusions
The ground load represents the amount of heat extracted from or injected
into the ground in one year.
The ground is extremely unbalanced. This means the amount of heat
injected in summer is much more than the heat injected in winter. This
increases the necessary size of the storage reducing its cost-effectiveness.
Techno-economic assessment
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 25
-50
-40
-30
-20
-10
0
10
20
30
40
50
0 1000 2000 3000 4000 5000 6000 7000 8000
Gro
un
d L
oad
[kW
]
Hours
Modelling Output - Ground Load
Heat Injection
Heat Extraction
Introduction Field Measurements Techno-economic Assessment Conclusions
The ground load represents the amount of heat extracted from or injected
into the ground in one year.
The ground is extremely unbalanced. This means the amount of heat
injected in summer is much more than the heat injected in winter. This
increases the necessary size of the storage reducing its cost-effectiveness.The present value of the operational savings represents the amount that
the supermarket should be willing to pay per meter of storage, taking into
account only the operational savings. This does not take into account
a potential difference in the CAPEX.
Techno-economic assessment
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 26
43 kW
0
5
10
15
20
25
30
35
40
0 500 1000 1500 2000 2500
Pre
sen
t V
alu
e o
f th
e O
pe
rati
on
al S
avin
gs[€/m
]
Total Length of the storage [m]
Present Value of the Operational Savings
-50
-40
-30
-20
-10
0
10
20
30
40
50
0 1000 2000 3000 4000 5000 6000 7000 8000
Gro
un
d L
oad
[kW
]
Hours
Modelling Output - Ground Load
Heat Injection
Heat Extraction
Introduction Field Measurements Techno-economic Assessment Conclusions
The ground load represents the amount of heat extracted from or injected
into the ground in one year.
The ground is extremely unbalanced. This means the amount of heat
injected in summer is much more than the heat injected in winter. This
increases the necessary size of the storage reducing its cost-effectiveness.
Moreover, also the power peaks of heat injected (in this application)
are one of the parameters driving the size of the storage.
7.4% Discount rate
15 Years lifetime
The present value of the operational savings represents the amount that
the supermarket should be willing to pay per meter of storage, taking into
account only the operational savings. This does not take into account
a potential difference in the CAPEX.
Techno-economic assessment
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 27
43 kW
40 kW
0
5
10
15
20
25
30
35
40
0 500 1000 1500 2000 2500
Pre
sen
t V
alu
e o
f th
e O
pe
rati
on
al S
avin
gs[€/m
]
Total Length [m]
Present Value of the Operational Savings
-50
-40
-30
-20
-10
0
10
20
30
40
50
0 1000 2000 3000 4000 5000 6000 7000 8000
Gro
un
d L
oad
[kW
]
Hours
Modelling Output - Ground Load
Heat Injection
Heat Extraction
Introduction Field Measurements Techno-economic Assessment Conclusions
The ground load represents the amount of heat extracted from or injected
into the ground in one year.
The ground is extremely unbalanced. This means the amount of heat
injected in summer is much more than the heat injected in winter. This
increases the necessary size of the storage reducing its cost-effectiveness.
Moreover, also the power peaks of heat injected (in this application)
are one of the parameters driving the size of the storage.
7.4% Discount rate
15 Years lifetime
The present value of the operational savings represents the amount that
the supermarket should be willing to pay per meter of storage, taking into
account only the operational savings. This does not take into account
a potential difference in the CAPEX.
Techno-economic assessment
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 28
43 kW40 kW33 kW
0
5
10
15
20
25
30
35
40
0 500 1000 1500 2000 2500
Pre
sen
t V
alu
e o
f th
e O
pe
rati
on
al S
avin
gs[€/m
]
Total Length [m]
Present Value of the Operational Savings
-50
-40
-30
-20
-10
0
10
20
30
40
50
0 1000 2000 3000 4000 5000 6000 7000 8000
Gro
un
d L
oad
[kW
]
Hours
Modelling Output - Ground Load
Heat Injection
Heat Extraction
Introduction Field Measurements Techno-economic Assessment Conclusions
The ground load represents the amount of heat extracted from or injected
into the ground in one year.
The ground is extremely unbalanced. This means the amount of heat
injected in summer is much more than the heat injected in winter. This
increases the necessary size of the storage reducing its cost-effectiveness.
Moreover, also the power peaks of heat injected (in this application)
are one of the parameters driving the size of the storage.
7.4% Discount rate
15 Years lifetime
The present value of the operational savings represents the amount that
the supermarket should be willing to pay per meter of storage, taking into
account only the operational savings. This does not take into account
a potential difference in the CAPEX.
Techno-economic assessment
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 29
43 kW40 kW33 kW
25 kW
0
5
10
15
20
25
30
35
40
0 500 1000 1500 2000 2500
Pre
sen
t V
alu
e o
f th
e O
pe
rati
on
al S
avin
gs[€/m
]
Total Length [m]
Present Value of the Operational Savings
-50
-40
-30
-20
-10
0
10
20
30
40
50
0 1000 2000 3000 4000 5000 6000 7000 8000
Gro
un
d L
oad
[kW
]
Hours
Modelling Output - Ground Load
Heat Injection
Heat Extraction
Introduction Field Measurements Techno-economic Assessment Conclusions
The ground load represents the amount of heat extracted from or injected
into the ground in one year.
The ground is extremely unbalanced. This means the amount of heat
injected in summer is much more than the heat injected in winter. This
increases the necessary size of the storage reducing its cost-effectiveness.
Moreover, also the power peaks of heat injected (in this application)
are one of the parameters driving the size of the storage.
7.4% Discount rate
15 Years lifetime
The present value of the operational savings represents the amount that
the supermarket should be willing to pay per meter of storage, taking into
account only the operational savings. This does not take into account
a potential difference in the CAPEX.
Techno-economic assessment
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 30
-50
-40
-30
-20
-10
0
10
20
30
40
50
0 1000 2000 3000 4000 5000 6000 7000 8000
Gro
un
d L
oad
[kW
]
Hours
Modelling Output - Ground Load
Heat Injection
Heat Extraction
43 kW40 kW33 kW
25 kW
15 kW
0
5
10
15
20
25
30
35
40
0 500 1000 1500 2000 2500Pre
sen
t V
alu
e o
f th
e O
pe
rati
on
al S
avin
gs[€/m
]
Total Length [m]
Optimizing the cost-effectiveness reducing design capacity -
Present Value of the Operational Savings Current Drilling Cost
7.4% Discount rate
15 Years lifetime
Introduction Field Measurements Techno-economic Assessment Conclusions
The present value of the operational savings represents the amount that
the supermarket should be willing to pay per meter of storage, taking into
account only the operational savings. This does not take into account
a potential difference in the CAPEX.
Techno-economic assessment
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 31
-50
-40
-30
-20
-10
0
10
20
30
40
50
0 1000 2000 3000 4000 5000 6000 7000 8000
Gro
un
d L
oad
[kW
]
Hours
Modelling Output - Ground Load
Heat Injection
Heat Extraction
43 kW40 kW33 kW
25 kW
15 kW
0
5
10
15
20
25
30
35
40
0 500 1000 1500 2000 2500Pre
sen
t V
alu
e o
f th
e O
pe
rati
on
al S
avin
gs[€/m
]
Total Length [m]
Optimizing the cost-effectiveness reducing design capacity -
Present Value of the Operational Savings Current Drilling Cost
7.4% Discount rate
15 Years lifetime
Introduction Field Measurements Techno-economic Assessment Conclusions
The present value of the operational savings represents the amount that
the supermarket should be willing to pay per meter of storage, taking into
account only the operational savings. This does not take into account
a potential difference in the CAPEX.-10
0
10
20
30
40
50
15kW 25kW 33kW 40kW 43kW
Gro
un
d L
oad
[M
Wh
/ye
ar]
Design Sub-cooling Capacity
Net Ground Balance
Heat Extraction (heat pump mode) Heat Injection (Subcooling) Net Ground Balance
Sensitivity Analysis – Supermarket size
Techno-economic assessment of CO2 refrigeration systems with geothermal integration
Different cooling demand profiles were tested, varying the other
parameters proportionally (e.g. heating demand).
0
5
10
15
20
25
30
35
40
45
0 200 400 600 800 1000 1200 1400 1600 1800
Pre
sen
t V
alu
e o
f th
e O
pe
rati
on
al S
avin
gs[€
/m]
Total Length [m]
Present Value of the Operational Saving – Size Variation
Reference Higher Cooling Demand Lower Cooling Demand Current Drilling Cost
Introduction Field Measurements Techno-economic Assessment Conclusions
32
Umeå
Stockholm
Kiruna
Sensitivity Analysis – Climate zone
Techno-economic assessment of CO2 refrigeration systems with geothermal integration
Different climate zones were tested. This was
performed using BIN hours from other climate zones.
0
5
10
15
20
25
30
35
40
45
50
0 200 400 600 800 1000 1200 1400
Pre
sen
t V
alu
e o
f th
e O
pe
rati
on
al S
avin
gs[€
/m]
Total Length [m]
Present Value of the Operational Saving - Climate Zone Variation
Reference (Stockholm) Umea Kiruna Current Drilling Cost
Introduction Field Measurements Techno-economic Assessment Conclusions
33
Sensitivity Analysis - Heat Recovery Ratio
Techno-economic assessment of CO2 refrigeration systems with geothermal integration
Different values of heat recovery ratio were tested. A higher heat recovery ratio
means operating a system with a higher heating demand for the same cooling load.
Typical examples of systems operating with a high heat recovery ratio are
supermarkets embedded in shopping malls or ice rinks exporting heat to the
neighbouring facilities.
0
10
20
30
40
50
60
70
80
90
0 200 400 600 800 1000 1200
Pre
sen
t V
alu
e o
f th
e O
per
atio
nal
Sav
ings
[€/m
]
Total Length [m]
Present Value of the Operational Saving - Variation of HRR
Reference (HRR 54%) HRR 70% HRR 76% Current Drilling Price
Introduction Field Measurements Techno-economic Assessment Conclusions
𝐻𝑅𝑅 =𝐻𝑒𝑎𝑡 𝑅𝑒𝑐𝑜𝑣𝑒𝑟𝑒𝑑
𝑇𝑜𝑡𝑎𝑙 𝐶𝑜𝑜𝑙𝑖𝑛𝑔 𝐿𝑜𝑎𝑑
Seasonal
HRR 54%
Seasonal
HRR 70%
Seasonal
HRR 76%
34
Conclusion
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 35
Introduction Field Measurements Techno-economic Assessment Conclusions
• The COP heat recovery can compete with the most modern heat pumps
• The operational savings only do not pay back the installation cost. There must be savings on the
CAPEX when comparing alternatives for satisfying the peaks of heating demand.
• The average HRR is the parameter affecting the cost-effectiveness the most
Conclusion
Techno-economic assessment of CO2 refrigeration systems with geothermal integration 36
Future Work:
• Is it possible and profitable to use these systems for exporting heat to district heating networks in power-to-heat
applications?
• Is it cost-effective to use air-to-CO2 load evaporators instead of a geothermal integration?
Introduction Field Measurements Techno-economic Assessment Conclusions
• The COP heat recovery can compete with the most modern heat pumps
• The operational savings only do not pay back the installation cost. There must be savings on the
CAPEX when comparing alternatives for satisfying the peaks of heating demand.
• The average HRR is the parameter affecting the cost-effectiveness the most
Thank You!
Questions?
Fabio Giunta
Brinellvägen 68, 10044 Stockholm, Sweden
eurammon Contact Details
Dr. Karin JahnManaging Directoreurammon e.V.Lyoner Straße 1860528 [email protected] +49 69 6603 1277