Project No:
298093
Project Acronym:
BIPV-PCM-COGEN
Project Full Name:
A Novel BIPV-PCM Heat and Power Cogeneration System for Buildings
Marie Curie Actions
FP7-PEOPLE-2011-IIF-Final Activity and Management Report
Period covered: from 07/12/2012
to
06/12/2014
Period number:
1
Start date of project: 07/12/2012
Project coordinator name: Professor Xudong Zhao
Project coordinator organisation name: University of Hull Royal Charter
Date of preparation: 08/01/2015
Date of submission (SESAM): 06/02/2015
Duration:
2 years
Version:
WORK PROGRESS AND ACHIEVEMENTS DURING THE PERIOD
Summary of progress towards objectives and details for each task
1. A summary of progress towards objectives and details of each work
This Marie Curie research project is to develop a novel BIPV-PCM-slurry energy (heat and
power) system involving several technical initiatives: (1) unique BIPV structure allowing the
PCM slurry to flow across, and (2) dedicated PCM-slurry-to-refrigerant (water, air) heat
exchangers appropriate for building ventilation and heating. These initiatives will have the
potential to overcome the difficulties associated with existing BIPV and BIPV/thermal
(water-based) systems, i.e., low efficiency, high cost and ineffective heat removal. The
specific objectives of the research are:
(1) To design a conceptual PCM-slurry adapted BIPV module and associated energy (heat
and power) system.
(2) To develop a computer model to optimize the configuration of the BIPV-PCM-slurry
energy system and predict its operational performance.
(3) To construct and test a prototype BIPV-PCM-slurry energy system and validate the
computer model using the experimental data.
(4) To carrying out economic and environmental analyses of the BIPV-PCM-slurry energy
system.
Table 1 - The diagrammatic project plan
Programme Tasks
3
1 Conceptual design of the proposed BIPV
module and modules-based energy system
2 Developing a computer model to optimise the
system configuration and predict its
operational performance
Construction and testing of a prototype solar
façade system in laboratory
4 Economic and environmental and
regional acceptance analyses
Reporting/Deliverables
6
Year 1
9
Year 2
18 21
24
*
M2
*
*
*
M3
*
*
D1
Q1
2
15
M1
3
Meetings
12
D2
Q2
Q3
Q4
D3
Q5
Q6
Q7
M4
*
D4
*
D5
Q8
Over the two-year project duration, all the above tasks have been successfully completed and
these are briefed as follows:
Task 1. Conceptual design of the PCM-slurry adapting BIPV façade module and
associated heat and power system
Task 1 addressed the conceptual design of a novel BIPV façade module compatible to PCM
slurry, as well as associated heat and power system (see Fig. 1 - schematic diagram of the
novel energy system). The critical items are the BIPV module, PCM slurry and slurry-torefrigerant heat exchanger, which should be devised to enable effective heat transfer and
meanwhile, minimise the flow resistance when the slurry travels across the absorbing pipes.
Fig. 1 schematic diagram of the novel energy system
Apart from these three critical items, other system components were also addressed. These
include (1) connectors among the façade modules, (2) module fixing-up mechanism, (3)
slurry circulating lines; (4) coupling measure with existing grid and water heating system;
and (5) heat storage.
3
All these components are appropriately connected, integrated into the building façade, and
coupled into the existing building heat and power supply networks, thus forming a solardriven, highly energy efficient, and relatively lower cost energy generation and transportation
loop that can act as the complementary pair to the traditional building energy system.
The preliminary design and identification of the performance specifications of the system
components were completed; these are detailed in Table 2.
Table 2 Characteristic parameters of components
No
1
2
3
Item
BIPV-PCMSlurry
module
MPCM
slurry
Slurry-torefrigerant
heat
exchanger
Size /type
1600*800
mm
MPCM28,
17-20um
206*76*5
5mm/Stai
nless steel
plate type
structure
Capacity
1.Glazing
cover
2.PV layer
3.Serpentine
tube with fins
4. Insulation
5. Frame set
heat out
put:0.735 kW
electricity:
150W
Uvalue:<0.172
W/m2.℃
slurry flow
rate:40-87.5
kg/h
flow
resistance:26
5-280kPa
Core material:
paraffin, shell
material:
polymer,
concentration:
10%
20 Flat plates
Latent
heat:213.5kJ/
kg
Viscosity:
1.07-1.29
mPa s
Specific
heat:39404060W/m.K
>3000W
Connection/ins
tallation
Hang onto the
wall surface
using the
standard
cladding
supporters;
With stainless
steel hoses to
connect each
other and to
the main slurry
line using
standard pipe
thread
connections
Physical
stability should
be inspected
during
operation
Compact, Small
installation
space demand
4
Heat
pump
1kW
n/a
Heat output:
4000W
n/a
5
connector
15mm
hoses
n/a
1/2'' standard
4
Remarks
Diameter of the
absorbing pipes
and other
configurations
of the module
are to be
validated and
confirmed by
the following
modelling and
experimental
work
Detailed
physical
properties, for
instance,
viscosity, etc.,
will be
measured
afterward
light, compact,
low resistance,
low cost
Condensing
temperature:50
-75℃
evaporation
temperature:15
-25℃
n/a
s among
the façade
modules,
6
7
module
fixing-up
mechanis
m
hanging
Studs and
support
n/a
Pressing,
hanging and
fixing
The BIPV
module will be
moulded with
studs on its two
side wings.
During the
installation, a
standard wallfixing support
will be bolted
into the wall,
and the
enclosure will
then be pressed
into the
supports
through the
interfaces
slurry
circulating
lines
7mm and
15mm
copper/st
ainless
steel pipes
Circular
n/a
standard pipe
thread
n/a
n/a
Electricity
generated by
the BIPV
modules is prior
s to be used to
reduce the grid
power usage
n/a
The slurry to
refrigerate heat
exchanger is
used as an
evaporator
connection
scheme: as a
Pass-by of
slurry to
refrigerant heat
exchanger
Size, type,
storage
capacity and
insulation
performance
are to be
confirmed by
the following
modelling and
experimental
wok
8
coupling
measure
with
existing
grid
9
coupling
measure
with
existing
heating
system
10
pipe thread
Heat
storage
DC/AC
Microinverter
n/a
100L,
cylinder
storage
tank for a
BIPV
module
n/a
n/a
1. stainless
steel wall;
2. >150mm
mineral wool
insulation
100W-30kW
n/a
3600kJ
storage
capacity
5
It should be addressed that the above performance data were developed based on the
fundamental knowledge and established experience by the researchers. These are subject to
correction, modification and update, through the subsequent computer modelling and
experimental works.
Task 2. Development of a computer model to optimize system configuration and predict
its operational performance
Task 2 addressed the computer model development and operation that are aimed to analyse
the power generation, fluid flow and heat transfer problems occurring in the BIPV-PCMSlurry system, which are detailed as below:
(i) Prediction of the operational performance of the PV/T module
(a) Impact of the PCM mass fraction and fluid flow state
Remaining a number of operational parameters fixed, i.e., solar radiation at 1,000W/m 2, wind
speed at 1 m/s, ambient temperature at 20℃, fluid inlet temperature at 25℃ and mass flow
rate at 0.02kg/s, simulation was conducted under the condition of variable PCM mass fraction
in the range 0 (pure water) to 20%. The simulation results were presented in Figs. 2 to 9,
which illustrate the impacts of the PCM mass fraction onto the fluid flow state, PV cells’
temperature, serpentine piping’s pressure drop, and the module’s electrical, thermal, overall
and net efficiencies.
It is found that under the fixed mass flow rate of 0.02kg/s, the PCM mass fraction had direct
impact onto the fluid flow state. As shown in Figs. 2 and 3, when the mass fraction was in
the range 0 to 10%, the PCM slurry was in turbulent flow state; during which the fluid
viscosity grew and the Reynolds number fell with the growth in the PCM mass fraction. This
effect actually suppressed the growth of the turbulent fluid and somehow offset the heat
transfer enhancement caused by the phase changing. As a result, the temperature of the PV
cells slightly grew (Fig. 4), and the module’s thermal, electrical and overall efficiency fell
slightly (Figs. 6 – 8). In terms of the pressure drop, it remained a downward trend when the
concentration grew from 0 to 10%, simply because of the reduced Reynolds number that led
to the reduced pressure drop (Fig. 5). As a consequence, the net efficiency obtains a highest
value at mass fraction of 10%.
6
When the PCM mass fraction exceeded 10%, the flow was changed into the laminar
condition, owing to the increased fluid viscosity and significantly decreased Reynolds
number. It is clear that a turbulent flow led to the reduced PV cell's temperature and the
increased electrical, thermal and overall efficiencies than a laminar flow owing to its
enhanced heat transportation capability (Fig. 4 and Figs. 6 - 8). At the laminar flow
condition, the cooling effect was largely affected by the mass fraction; the higher the ratio
value was, the better the cooling effect that the slurry can achieve (Fig. 4). With regard to the
pressure drop, it remained an upward trend when the mass fraction grew from 15 to 20%, just
because of the remarkably increased viscosity that led to the increased pressure drop (Fig. 5).
As a consequence, the net efficiency reaches a lower value at the mass fraction of 20% at the
laminar flow condition. At 15% of mass fraction, the PV cells reached the lowest temperature
and consequently, the module’s thermal, electrical and overall efficiency reached the
maximum level. Furthermore, owing to the lowest pressure drop achieved at the 15% of mass
fraction condition, the module had the highest net efficiency (Fig. 9).
5000
3
4000
2.5
3000
2
Re
Dynamic viscocity/μ/mPa·s
3.5
1.5
2000
1
1000
0.5
0
0
0
5
10
15
20
0
5
Particle mass fraction, W/%
15
20
Particle mass fraction, W/%
Fig. 2. The Dynamic viscosity as a function
of particle mass fraction
Fig. 3. The Reynolds number as a function
of particle mass fraction
43
30
42
Pressure drop, Δp/104Pa
PV temperature, tPV/℃
10
41
40
39
38
37
36
20
10
0
5
10
15
20
0
Particle mass fraction, W/%
5
10
15
20
Particle mass fraction, W/%
Fig. 4. The PV temperature as a function
of particle mass fraction
Fig. 5. The thermal efficiency as a function
of particle mass fraction
7
46
15.75
Thermal efficiency, ηth/%
Electrical efficiency, ηel/%
15.8
15.7
15.65
15.6
15.55
15.5
15.45
15.4
45
44
43
42
41
0
5
10
15
20
0
10
15
20
Particle mass fraction, W/%
Particle mass fraction, W/%
Fig. 6. The electrical efficiency as a function
of particle mass fraction
Fig. 7. The thermal efficiency as a function of
of particle mass fraction
62
Net efficiency, ηnet/%
62
Overral efficiency, ηO/%
5
61
60
59
58
57
61
60
59
58
57
0
5
10
15
20
0
5
10
15
20
Particle mass fraction, W/%
Particle mass fraction, W/%
Fig. 8. The overall efficiency as a function
of particle mass fraction
Fig. 9. The net efficiency as a function of
of particle mass fraction
(b) Impact of the Reynolds number
Remaining a number of operational parameters fixed, i.e., solar radiation at 1,000W/m 2, wind
speed at 1 m/s, ambient temperature at 20℃, and fluid inlet temperature at 25℃, simulation
was conducted under the condition of variable PCM concentration in the range 0 to 20% and
Reynolds numbers of 3,350, 2,600 and 1,800 respectively. The simulation results were
presented in Figs. 10 to 15, which illustrate the impacts of the PCM mass fraction and
Reynolds number onto the PV cells’ temperature, serpentine piping’s pressure drop, and
module’s electrical, thermal, overall and net efficiencies.
Figs. 10 and Figs 12 to 14 show the PV cells’ temperature fell with the growth in the mass
fraction and consequently, the module’s thermal, electrical and overall efficiency grew
8
accordingly. Inversely, the pressure drop of the PCM slurry across the serpentine piping grew
with the increase in the mass fraction (Fig. 11). As the combined effort, the net efficiency of
the module initially grew with the increase in the mass fraction and when the mass fraction
exceeded a certain value (named the ‘turning point’), the net efficiency presented a
downward trend. The turning points of the three flow conditions, i.e., Reynolds number of
1,800, 2,600, 3,350, are 15%, 10%, 5% respectively (Fig.15).
Under the three selected Reynolds numbers, the most favourable operational condition is the
one with the Reynolds number of 2600 at the mass fraction 10%. The electrical, thermal,
overall, and net efficiency are 15.6%, 43.8%, 59.4%, 57.1% respectively. They are much
higher than the average values for BIPV panels (around 4.67%), the PV panels (around 10–
12% ) and solar thermal collectors (around 40%).
60
55
Re=2600
Pressure drop, ∆P/ 104Pa
PV temperature, tPV/℃
Re=1800
Re=3350
50
45
40
35
30
0
5
10
15
20
300
280
260
240
220
200
180
160
140
120
100
80
60
40
20
0
Re=1800
Re=2600
Re=3350
0
10
15
20
Particle mass fraction, W/%
Particle mass fraction, W/%
Fig. 10. The PV cell's temperature as a function
of particle mass fraction
and Renault number
Fig. 11. The pressure drop as a function
of particle mass fraction
and Renault number
16.5
50
Thermal efficiency, ηth/%
Electrical efficiency, ηel/%
5
16
15.5
15
Re=1800
Re=2600
Re=3350
14.5
14
0
5
10
15
Particle mass fraction, W/%
45
40
Re=1800
Re=2600
Re=3350
35
30
20
0
Fig. 12. The electrical efficiency as a function
of particle mass fraction
and Renault number
5
10
15
Particle mass fraction, W/%
20
Fig. 13. The thermal efficiency as a function
of particle mass fraction
and Renault number
9
65
60
55
Re=1800
Re=2600
Re=3350
50
Net efficiency, ηnet/%
Overall efficiency, ηo/%
65
45
0
5
10
15
60
55
50
Re=1800
Re=2600
Re=3350
45
40
35
20
0
Particle mass fraction, W/%
5
10
15
20
Particle mass fraction, W/%
Fig. 14. The overall efficiency as a function
of particle mass fraction and
Renault number
Fig. 15. The net efficiency as a function
of particle mass fraction and
Renault number
(c) Effect of the serpentine piping size
Remaining a number of operational parameters fixed, i.e., solar radiation at 1,000W/m 2, wind
speed at 1 m/s, ambient temperature at 20℃, fluid inlet temperature at 25℃, mass flow rate at
0.02kg/s, and Reynolds number at 3,350, simulation was conducted under the condition of
variable PCM mass fraction in the range 0 to 20% and serpentine piping diameter in the range
6 to 8mm. The simulation results were presented in Figs. 16 to 21, which illustrate the
impacts of the PCM mass fraction and piping diameter onto the PV cells’ temperature,
serpentine piping’s pressure drop, and module’s electrical, thermal, overall and net
efficiencies.
Fig. 16 and Figs 18 to 20 show, under a certain serpentine piping size, the PV cells’
temperature fell with the increase in the mass fraction and consequently, the module’s
thermal, electrical and overall efficiency grew accordingly. Inversely, the energy
consumption of the PCM slurry pump piping grew with the increase in the mass fraction due
to the pressure drop increase (Fig. 17). As the combined effort, the net efficiency of the
module initially grew with the increase in the mass fraction and when the mass fraction
exceeded 5%, the net efficiency presented a downward trend (Fig. 21).
Under the above pre-justified condition, increasing the serpentine piping’s diameter resulted
in decrease in the PV cells’ temperature and consequently, the module’s thermal, electrical,
overall and net efficiency grew accordingly. At the same mass fraction condition, the large
diameter of the serpentine pipe helped improve the energy performance of the PV/T module.
However, considering the increased cost caused by the increased piping size, an adequate
10
pipe size should be selected by taking into account both the economic and energy
performance aspects in relation to the module.
55
450
50
7mm
Pressure drop, ∆P/ 104Pa
PVcell's temperature, tPV/℃
6mm
8mm
45
40
35
30
400
6mm
350
7mm
300
8mm
250
200
150
100
50
0
0
25
0
5
10
15
20
5
10
15
20
Particle mass fraction, W/%
Particle mass fraction, W/%
Fig. 16. The PV cell's temperature as a function
of particle mass fraction
and internal diameter
Fig. 17. The pressure drop as a function
of particle mass fraction
and internal diameter
50
Thermal efficiency, ηth/%
Electrical efficiency, ηel/%
16.5
16
15.5
15
6mm
7mm
8mm
14.5
14
0
5
10
15
45
40
6mm
7mm
8mm
35
30
20
0
Particle mass fraction, W/%
10
15
20
Particle mass fraction, W/%
Fig. 18. The electrical efficiency as a function
of particle mass fraction
and internal diameter
Fig. 19. The thermal efficiency as a function
of particle mass fraction
and internal diameter
65
65
Net efficiency, ηnet/%
Overall efficiency, ηo/%
5
60
55
6mm
7mm
8mm
50
60
55
50
45
6mm
7mm
8mm
40
35
45
0
5
10
15
30
20
0
Particle mass fraction, W/%
Fig. 20. The overall efficiency as a function of
particle mass fraction and internal diameter
11
5
10
15
Particle mass fraction, W/%
20
Fig. 21. The net efficiency as a function of particle
mass fraction and internal diameter
Slurry flow and its interaction with solar radiation within the BIPV façade module were
simulated and analysed. The heat and power generation and conversion processes associated
with the modules were simulated and computed using the classical photo-electronic and
conduction/convection/radiation equations and published experimental data relating to PCM
slurry. Analyses of the above simulation results concluded: (a) Under the three selected
Reynolds numbers and slurry concentrations, the most favourable operational condition is the
one with the Reynolds number of 2600 at the mass fraction 10wt.%. (b) Under the favourable
operational condition, the electrical, thermal, overall, and net efficiency are 15.6%, 43.8%,
59.4%, 57.1% respectively. They are much higher than the average values for BIPV panels
(around 4.76%), the PV panels (around 10–12%) and solar thermal collectors (around 40%);
(c) the module was sized to 1600mm x 800mm, by taking into account the factors of
electrical and thermal output, transportation and installation etc; (d) the conventional baseplate of PV module was replaced by an absorbing-pipes-attained sheet, which helps increase
heat transfer. The layer set-up is thus configured as glazing cover, PV lamination, absorbingpipes-attained cooper sheet, and insulation (e) copper absorbing pipe in serpentine is an
appropriate choice in terms of slurry transportation, phase change and heat absorption from
the PV layer; (f) recommended internal diameter of absorbing pipes is 7 mm; (g) adjacent
modules can be connected through a stainless steel hose with standard pipe thread;
(ii) Simulation of the slurry-to-refrigerant heat exchanger
Plate Heat Exchangers have a high heat transfer rate compared to other types of heat
exchangers due to their larger heat transfer area. They are composed of a number of thin
metal plates stuck together into a ‘plate pack’. Plate Heat Exchangers, having wide range of
applications in pharmaceutical, petrochemical, chemical, power, industrial dairy, and food &
beverage industries, are effective in heat transfer, easy to maintain, compact in size, and low
cost.
The compact plate heat exchanger is considered to be an appropriate unit conveying heat
transfer between the slurry and refrigerant. Heat transfer and fluid flow within an exchanger
were simulated using the developed analytical model under the identified operational
conditions, i.e., slurry inlet temperature: 31℃, slurry mass flow rate 0.02kg/s, refrigerant inlet
condition: 15℃, and refrigerant mass flow rate: around 0.012kg/s. Analysis of the simulation
results indicates that (a) for the specific operational conditions, a 203mm×75 mm ×55 mm
(height × width × thickness) of heat exchanger is appropriate, which contains 20 adjacent
12
channels with the total heat transfer area of 0.3m2; (b) heat transfer rate varies from 200W to
3000W, depending upon the flow state; and (c) flow resistances on slurry and refrigerant
sides are 0 – 206 Pa and 0 – 180 Pa respectively, dependent upon the flow rate, flow state and
PCM mass fraction of the slurry.
(iv) Integrated System
An analytical model for the integrated system was established and used to simulate the
energy performance of the novel PCM-slurry compatible BIPV system. Taking the
efficiency, system COP as the major measures, comparison among these systems was
undertaken under different operational conditions. Analyses of these results indicated that (a)
the overall Coefficient of Performance (COP) of the system was 8.22 under the weather data
of London’s summer typical day, which was nearly fourfold of the conventional air-source
heat pump water heating system (ASHP), and around twice of the integral-type solar assisted
heat pump system (ISAHP) ; (b) the size of the system is flexible to adapt the scale and
function of buildings. During this simulation, only a small system comprising one BIPV
module was considered; while the large scale system is expected to achieve even better
performance, by making the appropriate connection (e.g., in parallel or in series) between the
modules.
Task 3 Construction and Laboratory Testing of the Prototype BIPV-PCM-slurry Energy
System
(i) Construction of the Prototype BIPV-PCM-slurry Energy System
A prototype BIPV-PCM-slurry system and associated test rig were then constructed at the
Energy Technologies Laboratory of University of Hull. The major system components
including the BIPV-MPCM-slurry module, compressor, condenser, evaporator, pump, water
tank were appropriately connected into a system that could effectively convert solar energy
into electricity and hot water, as shown in Figs. 22 (a), (b), and (c). To enable precise
measurement of the system operational parameters, a number of dedicate measurement
instruments were implemented into the system, while the solar simulator is placed against the
BIPV-PCM-Slurry module. Table 3 presents a list of experimental instruments including their
images and technical specifications.
13
Air Vent
Expansion vessel
Solar simulator
Outlet
Module
Inlet
Shelf
(a) The testing rig - front view
Water tank
Compressor
Pump
(b) The testing rig - back view (Compressor/water tank) (c) The testing rig - back view (Pump)
Fig. 22. The testing rig
A steel framework and other associated accessories were also integrated into the test rig, as
shown in Fig. 22 (b) and (c).
Table 3. Experimental instruments used in system measurement
Instrument/Device
Solar simulator
Specification
Atlas(SolarConstant 4000
Radiation unit
Inclusive 4000W lamp and
UV-Filter)
14
Quantity
2
Location
In front of the module
Pyranometer
Power sensor
Pressure Transmitter
Flow sensor
Fowmeter
Thermocouples
Temperature Probes
(RTD)
LP02-TR (Hukseflux)
WB1919B35-S and
WBP112S91 (Weibo, China)
3100R0010G01B000,10bar,
0-5V(Germs Sensors)
200psi Pressure, 0.5-5
(Germs Sensors)
R025S116N (MicroMotion)
T type
PT100 RTD probes
90/00543945(Jumo, UK)
1
2
On the bracket of the module.
module power output (DC),
compressor input (AC)
2
Inlet and outlet of the module
2
Inlet and outlet of the module
1
15
Compressor outlet.
Module’s backplane
8
Heat pump evaporator section,
vapour line, module’s inlet/outlet
(slurry side), liquid line, heat
exchanger inlet/outlet (refrigerant
side), water tank
Rheometer
Paar Physica MCR 300
(Paar Scientific)
1
For measuring viscosity of the
MPCM slurry
Data logger
AGILENT TECHNOLOGIES
- 34972A(2 A3901 modules)
1
Record data with computing unit
(ii)Laboratory testing, results analyses and computer model validation
(a) Impact of solar radiation
By varying the solar radiation from 525 to 825 W/m2, while remaining other parameters
unchanged (i.e., Re – 2930, PCM concentration – 10%, other same as above), impact of solar
radiation to operational performance of the module and associated energy system was
investigated, detailed as below:
The testing results were presented in Figs. 23 to 27, which indicate the impacts of solar
radiation onto the module electrical and thermal efficiencies, module back plane temperature,
system pressure drop, and system total coefficient of performance (COPBIPV/T). Fig. 25 and
Figs 23 to 24 show the back plane temperature increase with the growth in the solar radiation
(I) and consequently, the module’s electrical and thermal efficiency fell accordingly.
Inversely, the pressure drop of the MPCM slurry across the system piping fell with the
increase in the solar radiation (Fig. 26). The system total coefficient of performance
(COPBIPV/T) would grow as a consequence of decrease in pressure drop and increase in back
plane's temperature, but it would fall as a result of decrease in the module electrical and
thermal efficiencies, as the combined effort, the system total coefficient of performance
(COPBIPV/T) grew with the increase in the solar radiation (Fig.27), which indicated that
15
electricity consumption decrease resulted from decrease in pressure drop and increase in back
plane's temperature was dominant in the total system performance.
75
Thermal efficiency, %
Electrical efficiency, %
15
14.5
14
13.5
71
69
67
65
13
500 550 600 650 700 750 800 850
500 550 600 650 700 750 800 850
Solar irradiance/W/m2
Solar irradiance/W/m2
Fig. 23 Module electrical efficiency
as a function of solar radiation
Fig. 24 Module thermal efficiency as
a function of solar radiation
40
30
Pressure drop, ×104
29
35
30
25
28
27
26
25
24
23
20
500 550 600 650 700 750 800 850
500 550 600 650 700 750 800 850
Solar irradiance/W/m2
Sloar irradiance/W/m2
Fig. 26 System pressure drop as a
function of solar radiation
Fig. 25 Module temperature as a
function of solar radiation
9.5
System COPBIPV/T
Back plane's tempearature/℃
73
8.5
7.5
6.5
5.5
500 550 600 650 700 750 800 850
Solar irradiance/W/m2
Fig. 27 System performance (COPBIPV/T) as a function of solar radiation
16
(b) Impact of slurry flow condition (Re)
By varying the slurry flow Reynolds number from 1742 to 3389, while remaining other
parameters unchanged (i.e. I – 625 W/m2, PCM concentration – 10%, others same as above),
impact of slurry flow condition (Re)to the operational performance of the module and
associated energy system was investigated, detailed as below:
The testing results were presented in Figs. 28 to 32, which indicate the impacts of flow
condition, Reynolds number (Re) onto the module electrical and thermal efficiencies, module
back plane temperature, system pressure drop, and system total coefficient of performance
(COPBIPV/T). Figs. 30 and Figs 28 to 29 show the back plane temperature fell with the growth
in the Reynolds number (Re) and consequently, the module’s electrical and thermal
efficiency grew accordingly, because growth in the Reynolds number would enhance heat
transfer. Inversely, the pressure drop of the MPCM slurry across the system piping grew with
the increase in the Reynolds number (Fig.31). The system total coefficient of performance
(COPBIPV/T) would grow as a result of increase in the module electrical and thermal
efficiencies, but it would fall as a consequence of growth in pressure drop and fall in back
plane's temperature, as the combined effort, the system total coefficient of performance
(COPBIPV/T) grew with the increase in Reynolds number (Fig.32), which indicated that the
growth in electrical and thermal efficiency resulted from the heat transfer enhancement was
dominant in the total system performance.
15
75
Electrical efficiency, %
Thermal efficiency, %
80
70
65
60
55
1500
2000
2500
3000
14.5
14
13.5
13
1500
3500
Re
2000
2500
3000
3500
Re
Fig. 28 Module electrical efficiency
as a function of Reynolds number
Fig. 29 Module thermal efficiency as
a function of Reynolds number
17
50
45
40
Pressure drop, ×104
The absorb plate's temperature, ℃
45
35
30
25
40
35
30
25
20
15
10
5
20
1500
2000
2500
3000
0
1500
3500
2000
Re
2500
3000
3500
Re
Fig. 30 Module temperature as a
function of Reynolds number
Fig. 31 System pressure drop as a
function of Reynolds number
System COPBIPV/T
9.5
8.5
7.5
6.5
5.5
1500
2000
2500
3000
3500
Re
Fig. 32 System performance (COPBIPV/T) as a function of Reynolds number
(c) Impact of PCM concentration (w)
By varying the MPCM mass fraction in the slurry from 0wt.% to 10wt.%, while remaining
other parameters unchanged (i.e. I – 625 W/m2, Re – 2930%, others same as above), impact
of the PCM mass fraction (w) to the operational performance of the module and associated
energy system was investigated, detailed as below:
The testing results were presented in Figs. 33 to 37, which indicate the impacts of MPCM
particles mass fraction onto the module electrical and thermal efficiencies, module back plane
temperature, system pressure drop, and system total coefficient of performance (COPBIPV/T).
Figs. 35 and Figs 33 to 34 show the back plane temperature fell with the growth in the mass
fraction and consequently, the module’s electrical and thermal efficiency grew accordingly,
because growth in the mass fraction would result in increase in heat transfer rate. Inversely,
the pressure drop of the MPCM slurry across the system piping grew with the increase in the
concentration ratio (Fig. 36), because growth in the mass fraction would result in increase in
18
viscosity of the slurry. The system total coefficient of performance (COPBIPV/T) would grow
as a result of increase in the module electrical and thermal efficiencies, but it would fall as a
consequence of decrease in pressure drop and back plane's temperature, as the combined
effort, the system total coefficient of performance (COPBIPV/T) grew with the increase in the
mass fraction (Fig. 37), which indicated that the growth in electrical and thermal efficiency
was dominant in the total system performance.
75
14.5
Thermal efficiency, %
Electrical efficiency, %
14.4
14.3
14.2
14.1
14
13.9
13.8
13.7
70
13.6
65
13.5
0
5
0
10
Mass fraction/wt.%
10
Mass fraction/wt.%
Fig. 33 Module electrical efficiency
as a function of mass fraction
Fig. 34 Module thermal efficiency as
a function of mass fraction
50
45
45
Pressure drop, ×104
Back plane's temperature/℃
5
40
35
30
40
35
30
25
20
15
10
5
0
25
0
5
0
10
Mass fraction/wt.%
5
10
Mass fraction/wt.%
Fig. 36 System pressure drop as a
function of mass fraction
Fig. 35 Module temperature as a
function of mass fraction
19
System COPBIPV/T
9.5
8.5
7.5
6.5
5.5
0
5
10
Mass fraction/wt.%
Fig. 37 System performance (COPBIPV/T) as a function of mass fraction
(d) Computer model validation
To validate the computer model, the laboratory testing of the constructed system was
conducted under the equivalent conditions to the simulation. The measurement results were
recorded, analyzed and compared with the results of the simulations under the equivalent
operational condition (same as the above experimental condition), thus giving a set of
diagrams containing both experimental and simulation data, detailed as below.
Fig. 38 shows the comparison of the simulated and the measured module electrical efficiency
at varied Reynolds numbers (Re) in range 1742 to 3389. A good agreement was found
between the modelling and experimental data with the average error scale of 0.56%. Fig. 39
shows the comparison of the simulated and the measured module thermal efficiency at varied
Reynolds numbers (Re) in range 1742 to 3389. A good agreement was found between the
modelling and experimental data with the average error scale of 1.63%.
80
15
simulated
Thermal efficiency, %
Electrical efficiency, %
measured
14.5
14
13.5
13
1500
2000
2500
3000
75
70
65
60
55
1500
3500
Re
measured
simulated
2000
2500
3000
3500
Re
Fig. 38 Comparison of module electrical
efficiency between measurement and simulation
20
Fig. 38 Comparison of module thermal
efficiency between measurement and simulation
Fig. 40 shows the comparison of the simulated and the measured back plane’s temperature at
varied Reynolds numbers (Re) in range 1742 to 3389. A good agreement was found between
the simulated and experimental data with the average error scale of 2.86%. Fig. 41 shows the
comparison of the simulated and the measured pressure drop at varied Reynolds numbers
(Re) in range 1742 to 3389. An acceptable agreement was found between the modelling and
45
50
40
measured
45
simulated
40
Pressure drop, ×104
Back plane's temperature, ℃
experimental data with the average error scale of 5.59%.
35
30
25
measured
simulated
35
30
25
20
15
10
5
20
1500
2000
2500
3000
0
1500
3500
Re
2000
2500
3000
3500
Re
Fig. 40 Comparison of back plane’s temperature
between measurement and simulation
between measurement and simulation
Fig. 41 Comparison of pressure drop between
measurement and simulation
Fig. 42 shows the comparison of the simulated and the measured system total coefficient of
performance (COPBIPV/T) at varied Reynolds numbers (Re) in range 1742 to 3389. A good
agreement was found between the simulated and experimental data with the average error
scale of 2.31%.
9.5
measured
9
simulated
System COPBIPV/T
8.5
8
7.5
7
6.5
6
5.5
1500
2000
2500
3000
3500
Re
Fig. 42 Comparison of system performance (COPBIPV/T) between measurement and simulation
21
(e) Conclusions of Task 3
The experimental prototype was constructed and tested under the laboratory condition with
the aim of examining the operational performance of the prototype BIPV-PCM-slurry system.
The pre-defined testing conditions are: solar radiation in the range 525 to 825 W/m2, ambient
temperature of 29.5oC, heat-pump evaporation and condensation temperatures of 15 and
70oC, refrigerant flow rate of 0.012kg/s, water inlet temperature of 24.75oC and water flow
rate of 0.0042 kg/s. Under the above condition, the system could provide 585-895W of heat
in form of hot water of 60oC, 97-150 W of electricity. The average overall COP of the system
is 8.14; while the solar efficiency of the BIPV-PVM-slurry module is 83.8%. The impacts of
solar radiation, flow state (represented by Reynolds number, Re), MPCM particles mass
fraction on operational performance of the module and associated energy system were
experimentally investigated under the selected operational conditions. The testing results
indicated, the module’s electrical and thermal efficiency decrease and system’s coefficient of
performance (COPBIPV/T) increase when increasing solar radiation from 525 W/m2 to
825W/m2; The module’s electrical and thermal efficiency and system’s coefficient of
performance (COPBIPV/T) increase when increasing Reynolds number (Re) from 1742 to 3389.
The module’s electrical and thermal efficiency and system’s coefficient of performance
(COPBIPV/T) increase when increasing the MPCM particles mass fraction from 0wt.% to
10wt.%. Comparisons between the modelling and the experimental results suggested that the
model could achieve the acceptable accuracy in predicting the system’s operational
performance, with the error scale in the range 0.37% to 8.8%.
Task 4 Economic and environmental analyses of the BIPV-PCM-slurry energy system
In this task, the economic & environmental benefits of the new BIPV-PCM-slurry energy
system for use in European buildings were investigated. This involved (1) analyses of the
capital and operational cost of the BIPV-MPCM-slurry energy system; (2) calculation of
increase in the capital cost and saving in operational cost of the system relative to the
conventional BIPV, PV/water and conventional heat & power systems; and (3) estimation of
the payback period and life cycle cost saving of the system relative to the conventional ones.
Furthermore, the carbon emission reduction potential of the system for the use as a
replacement of the conventional heat and power systems, BIPV or BIPV/water systems
across the European regions was analysed. Through detailed economic and environmental
analyses, the conclusions were drawn as below:
22
Feasibility: The new BIPV-PCM-slurry system is more suitable for southern European
region than northern. The energy output of the system in the northern part is much less than
that in southern part. Taking the Madrid and Stockholm as the examples that can represent
the typical southern and northern European climatic conditions respectively, the annual
electricity and heat yields of the system in Madrid are 367.4 kWh and 1986.3 kWh
respectively; while the system yields in Stockholm are only 202.7 kWh and 1034.8 kWh.
This indicates that the system is more energy productive in southern Europe than that in
northern Europe, mainly owing to the higher solar radiation and ambient temperature of
southern part relative to the northern part.
Economic and environmental benefits: For a Madrid building with the potential to install
the BIPV, BIPV/water and BIPV-PCM-slurry systems, the relevant payback periods are 41.3,
7.6 and 4.7 years respectively. For a Stockholm building with the potential to install the BIPV,
BIPV/water and BIPV-PCM-slurry systems, the relevant payback periods are 41.3, 7.6 and
4.7 years respectively. Both cases in combination indicated that the BIPV-PCM-slurry system
demonstrated that greater economic benefits than the other two systems.
The life cycle costs (LCCs) per kWhe output in the three systems varied with the climatic
conditions. In Madrid which has a typical southern European climatic condition, the LCCs
per kWhe output for the BIPV, BIPV/water and BIPV-PCM-Slurry systems are 0.39 €, 0.15 €,
and 0.34 € respectively. In Stockholm which has a typical northern European climatic
condition, the LCCs per kWhe output for the three systems are 0.85 €, 0.23 €, and 0.05 €
respectively. Compared to the other two systems, the BIPV-PCM-slurry system can obtain
the greater benefits in terms of return-for-investment.
The CO2 Emission Reductions potentials of the three systems are also climatic dependent.
For the southern European climatic condition represented by Madrid, the carbon emission
reduction values of the three systems relative to the conventional heat and power systems are
1.6 tons, 14.2 tons, and 26.3 tons per annum respectively. For the northern climatic condition
represented by Stockholm, the carbon emission reduction values of the three systems relative
to the conventional heat and power systems are 0.8 tons, 7.5 tons, and 13.2 tons per annum
respectively, which are much smaller than that in Madrid. Of the three comparable systems,
the BIPV-PCM-slurry system presents the greatest potential in cutting the carbon emission to
the environment.
23
Summary of the progress of the researcher training activities/transfer of knowledge
activities/integration activities
22th Jan 2013:
Attending Endnote Training course
Dr. Zhongzhu Qiu attended Endnote Training course. Endnote is becoming the global standard
referencing software and is important for anyone who writes journal or conference papers, theses or
dissertations, Mr Paul Chin from Skills gave a talk to the staff and students in Hull including the
researcher.
10th April 2013:
Attending a seminar
Dr. Zhongzhu Qiu attended an EESE seminar presented by Steve Clarke from Smart Wind, who is
also the visiting professor at Hull University. He involved in a discussion on the research and funding
issues relating to the offshore wind energy.
9th May 2013:
Involving in the Hull University’s showcase affair.
Dr. Zhongzhu Qiu (MC fellow) involved a University showcase affair for scientific researches. This
provided him with an opportunity to demonstrate his research to the local people in HULL, including
technical and non-technical personnel. Through the exhibition of poster and experimental
interpretation, the visitors would be able to understand the general knowledge of the renewable energy
technologies and their applications in day-to-day life.
26th August 2013:
Attending an international conference (SET 2013)
Dr. Zhongzhu Qiu attended an international conference entitled ‘The 12 th International Conference
on Sustainable Energy Technologies (SET 2013)’ hosted by Hong Kong Polytechnic University. He
gave a technical presentation introducing the preliminary findings of the project and attended several
sessions to discuss the project related questions.
5th-6th Sept 2013:
Involving a technological and business opportunity seminar.
Dr Zhongzhu Qiu participated in a seminar involving discussion of the technological and business
development with a group of professionals from the UK, Germany, France, Switzerland, Sweden,
24
Denmark, USA, Hong Kong, and Chinese mainland; he made effort to introduce the research concept
into the participants.
Aug-Sept 2013:
Giving lectures and supervising doctoral and master students.
Dr Zhongzhu Qiu gave lectures in Shanghai University of Electric Power (SUEP) and participated in
several seminars held in China and supervised 2 PhD and 8 MSc students in SUEP in the subjects of
sustainable energy technologies and their applications in buildings; these activities helped disseminate
the project findings to his original country, China.
9th December 2013:
Attending an Inaugural Lecture
Dr. Zhongzhu Qiu attended the Inaugural Lecture presented by Professor Xudong Zhao; during which,
he made useful communication with the Lord Mayor of Kingston upon Hull, Councillor Nadine
Fudge, as well as many academic staff, and PhD/Msc students within the Hull University and beyond.
His research formed part of Professor Xudong Zhao's presentation context.
2th Feb 2014
Workshop Training
Dr Zhongzhu Qiu attended a workshop training programme organised by the University of Hull,
which is designed for the staff involving laboratory activities, addressing health and safety related
issues. This helped him to proceed the laboratory work in relation to the project
14th Apr 2014
Attending a Lecture
Dr. Zhongzhu Qiu attended the lecture presented by Professor Henggen Shen, Donghua University,
China, where he made useful discussion with Professor Shen and other attendee in relation to solar
energy usage and thermal energy storage by use of microencapsulated phase change material slurries,
which is part of his research work under the EU Marie Curie Programme.
20th May 2014
Attending a Lecture
Dr. Zhongzhu Qiu attended the lecture presented by Professor Jie Ji, University of Science and
Technology of China, who is one of the most famous researchers in the area solar energy utilization;
during which, Dr Qiu made useful communication with Professor Jie Ji and other attendee on the
issues associated with solar energy utilization and the feasibility of thermal energy storage by use of
25
microencapsulated phase change material slurries, which helped disseminate the research results
delivered from this project.
5th July 2014
Attending a Lecture
Dr. Zhongzhu Qiu attended the lecture presented by Professor Jihuan Xu, Tongji University of China;
during discussion, Dr Qiu disseminated the idea about the feasibility of solar thermal energy storage
by use of microencapsulated phase change material slurries. Again this helped disseminate the
research results delivered from this project.
16th Oct 2014
Involving in a site inspection on building energy conservation retrofit
Dr. Zhongzhu Qiu involved in a site inspection on building energy conservation retrofit at History
Centre of Hull; Dr Qiu prepared a preliminary proposal on the feasibility of building energy saving
retrofit and application of solar energy. He intended to apply part of the research outcomes from this
project into the practical engineering project in Hull.
December 2012-November 2014:
Supervising both PhD and MSc students
Dr. Zhongzhu Qiu involved in both PhD and MSc students supervision within Hull and beyond: To
maximise the impact of this fellowship project, a PhD student and a MSc student have been brought
into the project working with the fellow. As the students' study topics are in line with the overall
objective of this fellowship project, these students are jointly supervised by Prof. Zhao and Dr. Qiu.
Dr Qiu also gave lectures to his home university (Shanghai University of Electric Power) at a regular
base, at roughly every 6 month. This helped transfer the knowledge and expertise he obtained from
the project to the educated youths in China.
ADDITIONAL INFORMATION
Based on the project, several refereed research papers have been published or submitted, detailed as
follows:
1.
Zhongzhu Qiu, Xudong Zhao, Samira A. Ali, Peng Li, Microencapsulated Phase Change Material
(MPCM) Suspension: Newtonian or non-Newtonian fluid? Proceedings of 12th International
Conference on Sustainable Energy technologies (SET-2013), Hong Kong, Aug 26-29th, 10141019
26
2.
Zhongzhu Qiu, Xudong Zhao, Samira A. Ali, Peng Li, " Theoretical Investigation of the Energy
Performance of a Novel MPCM Slurry Based PV/T Module ", Energy, accepted with minor
correction.
3.
Zhongzhu Qiu, Xudong Zhao, Samira A. Ali, Peng Li, " experimental Investigation of the Energy
Performance of a Novel MPCM Slurry Based PV/T Module ", to be submitted to 'Energy'.
PROJECT MANAGEMENT
Over the two years project duration, the incoming researcher had a very good cooperation with host
institution that has generated significant outcomes, including 3 papers, 2 EU proposals, 1 PhD and 1
MSc training, and numerous public presentations.
The progress of project went very well in line with the proposed project plan. By the end of the
project, all tasks have been successfully completed.
27