- freely available
- re-usable
Energies 2014, 7(5), 3319-3338; doi:10.3390/en7053319
Published: 20 May 2014
Abstract
: This paper presents the design, modelling and performance evaluation of a photovoltaic/thermal-assisted heat pump water heating (PVTA-HPWH) system. The cooling effect of a refrigerant simultaneously enhances the PVT efficiency and effectively improves the coefficient of performance (COP) of the HPWH system. The proposed model was built in the MATLAB/Simulink environment by considering the reciprocal energy exchange between a PVT evaporator and a HPWH system. In addition, the power consumption needs of the HPWH are provided by the PV electricity using a model-based control methodology. System performance is evaluated through a real field test. The results have demonstrated the power autarchy of the proposed PVTA-HPWH system with better PVT efficiency and COP. In addition, the good agreement between the model simulation and the experimental measurements demonstrate the proposed model with sufficient confidence.1. Introduction
With increasing attention being paid to the issue of global warming and the soaring cost of fuel, energy-efficient and environment-friendly heating and cooling applications ranging from domestic and commercial to industrial sectors are a promising development. Most residential water heating systems are equipped with conventional water heaters that utilize fossil fuels or electricity to generate heat and thus have a negative impact on the environment and offer low-efficiency energy conversion. With the characteristics of ubiquity, abundance, and sustainability, solar energy is currently considered the most sustainable resource among the various renewable energy alternatives with the growing increase of environmental awareness. Photovoltaic/thermal (PVT) solar collectors that simultaneously produce electricity and heat are currently considered the most efficient devices to harness the available solar energy. Research and development on this topic has been promising during the last three decades. Some reviews on PVT collectors have recently been published [1–5]. On the other hand, heat pump (HP) systems can extract low-grade thermal energy from the environment and waste heat for use in water/space heating applications, therefore, they are currently considered as renewable energy sources in the EU [6] and UK [7]. In theory, the coefficient of performance (COP) of solar-assisted HP (SAHP) systems depends significantly on the temperature of the condenser and the temperature difference between the condenser and the evaporator [8]. Therefore, the waste heat recovery from solar cells for the evaporation of SAHP for water/space heating would mutually improve the PVT efficiency and the COP of SAHPs. Kern and Russel [9] revealed the high COP value of a PVT-SAHP system with the assistance of solar electricity and thermal energy. Ito and his team [10,11] have carried out continuous experimental studies on PVT-SAHP systems. Ji and his team have conducted some experimental evaluations of PVT-SAHP systems and validated them with a mathematical model [12–14]. Some improvements in the evaporator of PVT-SAHP systems based on theoretical simulation have been reported [15,16]. So far, the electrical characteristics of PV devices were not considered in the previous mathematical models of PVT-SAHP systems, when in fact, the thermodynamics of the PV module can directly integrate with the energy exchange of the PV output power [17]. It is found that the accuracy of the operating temperature estimation of the solar collector is the most important parameter in both PV electricity generation and reciprocal energy exchange. With the direct interaction of both PV electricity generation and the thermodynamics of the PVT collector, the concerted energy exchange between the PVT evaporator and HPWH system could be evaluated well and with better precision. Comparisons of the various literature approaches are listed in Table 1.
Refrigerant-based PVT devices feature the best conversion efficiency of solar energy compared to air- or water-based PVT technologies. The PVT evaporator has advantages such as less area, higher performance, and cogeneration of solar electricity and thermal heat. They have the potential to activate and promote the Million Rooftop PVs project in Taiwan [18] as a suitable solution to the problem of limited residential space, therefore, a prototype of a PVT-assisted HPWH (PVTA-HPWH) system was implemented and studied. First, a rooftop PVT module is developed as a solar collector/evaporator and the PVT array is integrated with a HPWH system for solar assisted HPWH applications. Then the mathematical model for the dynamics of PVTA-HPWH system, including both electrical characteristics and thermodynamics of the PVT evaporator and HPWH system, and their energy exchange interaction were built using Simulink software. Having both a derivation of a mathematical model and after building a simulation model, the control system of a HPWH system is designed using model-based methodology subjected to optimal performance considerations. The system performance isfinally evaluated through the field test of a prototype PVTA-HPWH system.
2. System Description
The utility model patent of the novel PVTA-HPWH system was issued 21 June 2013 in Taiwan [19]. A rooftop PVT evaporator integrated with a commercial HPWH system was implemented for evaluating the performance of the PVT device and the COP of the HPWH system.
2.1. PVT Evaporator/Collector
A pre-coated steel sheet is folded using a CNC folder in the form of a troughed roof profile. As depicted in Figure 1, a rough PVT evaporator prototype with a rated power of 200 Wp was developed as a supporting structure, with multi-port cooper tubes adhered to the rear as thermal absorber, and polystyrene (PS) foam laid beneath as insulator.
Forty-eight 6” 4.186 Wp polycrystalline silicon solar cells (Solartech Energy Corp., Hukou, Hsinchu, Taiwan) were arranged in two rows of twenty-four solar cells in series. The solar cells were sandwiched between ETFT and PET that were directly laminated in a steel coating like a PV module. A PT1000 (J-type thermocouple) sensor was laminated between the solar cells and steel sheet in the PV module encapsulation process. Based on the electrical characteristics of the solar cells under the standard test conditions (STC), i.e., cell temperature of 25 °C and solar irradiance of 1 kW/m^{2}, the electrical characteristics can be estimated and are depicted in Figure 2. The associated electrical parameters are listed in Table 2, in which the temperature coefficients K_{I} and K_{V} are the rate of change (derivative) with respect to temperature of the short-circuit current I_{SC} and open-circuit voltage V_{OC}. The PVT evaporator/collector with R134a refrigerant fluid is the solar electricity converter and thermal energy collector.
2.2. PVTA-HPWH System
The PVT evaporator is connected with a 1 kW HPWH system that is commercially available and works with environmentally friendly R134a refrigerant. The outside view of the PVT evaporator and a schematic diagram of the prototype system with rated power of 1 kWp is shown in Figure 3.
The PVTA-HPWH consists of a PVT evaporator array (I), a variable-frequency compressor (II, 2P19S3R236A-1A, Panasonic, Secaucus, NJ, USA), a condenser (III) immersed in a water tank, and an electronic expansion value (IV, AKVA, Danfoss, New Taipei City, Taiwan). The thermodynamics data of the refrigerant R134a, which depend on the working pressure and temperature of the PVT evaporator at different working points, are calculated by the Peace software [20] and are listed in Table 3.
Figure 4 depicts the corresponding pressure-enthalpy chart. The PVT evaporator array consists of five rooftop PVT modules that are connected electrically in series and their refrigerant tubes are connected in parallel in the form of an external manifold. While flowing through the PVT evaporator (I), the refrigerant is directly vaporized.
The direct expansion (DX) of refrigerant is expressed as the 4 → 1 process. In addition, the PVT evaporator generates solar electricity that can provide for the consumption of the compressor, electric control unit (ECU) and instruments. The vaporized refrigerant is compressed in the compressor (II) as the 1 → 2 process and is further upgraded to an appropriate temperature for heating purposes. The high-grade heat is then delivered into the condenser (III) to reject the useful heat into water (2 → 3 process). After being condensed, the high-pressure refrigerant is sent to an electric-controlled expansion value (IV) where undergoes a throttling process and collects as low-pressure liquid. This is expressed as the 3 → 4 process. Lowering the working temperature of the PVT evaporator not only increases PV efficiency due to the lower cell temperature but also enhances high the thermal efficiency with the heat recovery of ambient air. The rated power of PV electricity is designed enough to address the power consumption of the HPWH system.
3. System Modelling
There are three energy transfer mechanisms involved in the PVT evaporator: the PV effect that converts solar energy into solar electricity, thermal transportation that conveys solar radiation into the PVT collector and interchanges with the ambient environment, and heat recovery that evaporates the refrigerant within the coil for the evaporation of HPWH system. Its dynamic equation is given by:
Solar cells are arranged in the PVT evaporator with a series-parallel configuration for electricity generation applications. PV devices naturally exhibit nonlinear I − V and P − V characteristics that vary with radiant intensity and cell temperature. The I − V output characteristic of the PVT evaporator with solar cells in N_{P} parallel and N_{S} series is given by:
In the evaporation procedure, the low-grade heat of solar collector is obtained as:
Based on the mathematical formulation of PVTA-HPWH system, a simulation model is built in the MATLAB/Simulink environment. The proposed PVTA-HPWH model having direct interaction of PV electricity with the thermodynamics is built. First, the overall PVTA-HPWH system is decomposed into the PVT evaporator and HPWT subsystems that are created as subsystem blocks. The PVTA-HPWH block is masked with a user-friendly icon as shown in Figure 5a. Then the block diagram of the subsystem is built to mathematically characterize both the thermodynamics and electricity of the PVT evaporator and HPWH system as shown in Figure 5b.
In the subsystem, the thermal dynamical equation and its associate solar radiation, long-wavelength radiation, forced convection of wind and convection of refrigerant are implemented using the built-in Fcn blocks in Simulink. The PV electrical characteristics such as I − V characteristic equation, photovoltaic current, cell's saturation current and reverse saturation current are implemented in the same way.
Model-based methodology is one kind of optimal control design technology. Based on the mathematical/simulation model, the predicted control system is designed subject to optimal performance considerations. Having a well-validated PVTA-HPWH model, the control gain can be found with the increase in solar irradiance from 0 to 1000 W/m^{2} at the interval of 200 W/m^{2}, and the ambient temperature from 20 °C to 40 °C at a 5 °C step. The control gains for the mass flow rate of refrigerant are listed in Table 4 and are built in Figure 4b. The control gain is a function of solar irradiance and PVT temperature.
4. Experimental Evaluation
4.1. Experimental Rig
As illustrated in Figure 3b, the experiment setup consists of the PVT array, a commercial PV inverter with a rated power of 1.5 kW, a HPWH system with a rated power of 1 kWp and water tank capacity of 200 L, and some instruments. The PVT array was mounted on rooftop and placed in a south-facing position with an inclination angle of 23.5°. A pyrameter (Fronious Mono-Crystalline Si-Sensor, Tullamarine, Austria) was mounted at the same inclination of the PVT device to measure incident solar irradiation on the PVT plate. A temperature sensor (PT1000, J-type thermocouple) sensor laminated between the solar cell and steel sheet in the encapsulation process of the PV module was used to measured the lump PVT temperature parameter. The PV inverter has a good MPP tracker and PV electricity is fed into the utility grid through a distribution box. Its SolarPower software provides information about working voltage, output current and PV electricity power. Each sensor has its own relative error as listed in Table 5. The electric control unit (ECU) in the HPWH system is designed to monitor and control the system operation according to its thermodynamic data, In addition, the ECU controls the input current and power consumption for autonomous operation based on the energy balance equation. A LabVIEW-based automated measurement system has been designed to automatically visualize the electric and thermal data of the PVT, the parameters of HPWH system, and surrounding conditions such as solar irradiance, ambient temperature, and wind speed. The sampling period is set at an interval of 1-minute. The overall experiment rig was set up in the Energy Research and Development Center (ERDC) of Da-Yeh University in Taiwan.
4.2. Experimental Results
A one-hour measurement of the experiment rig was conducted from 12:00 to 13:00 for each day during June 2013. All observations of the physical parameters were automatically recorded at 1-min intervals. The results for two typical days with blue-sky and mostly sunny weather conditions are presented. The solar irradiance and ambient temperature for a typical sunny day (18 June 2013) are depicted in Figure 6a,b.
For easy comparison, the measured and simulated operating temperatures of PVT module are shown in Figure 6b. The results reveal that temperature difference is less than ±0.35 °C and its root mean square (RMS) value is 0.1339 °C. Considering the ±0.8 °C accuracy (in the range of −40 °C to 100 °C) of the PT1000 sensor, the prediction accuracy of PVT temperature is ±1.15 °C. Therefore, the simulated and measured results of the output current and power the PVT collector are almost close to each other as represented in Figure 6c. The maximal difference between the measured and simulated output current is 0.3 A and the RMS of difference is 0.1076 A. In addition, the maximal difference between the measured and simulated output power is 1.2 W and the associated RMS is 0.6305 W. Figure 6d shows the power consumption of the compressor of HPWH system and the result reveals PV electricity is enough to afford the compressor operation. The water temperature and energy in the water tank are depicted in Figure 6e. The results of the difference and RMS analyses are listed in Table 6.
For a mostly sunny day (12 June 2013), the solar irradiance and ambient temperature are depicted in Figure 7a,b. The average of wind speed is 3 m/s for the duration of the experiment. There are fluctuations in solar irradiance and ambient temperature near 12:10. Both measured and simulated operating temperatures of PVT module are shown in Figure 7b and the maximal difference is less than ±0.4 °C that occurs near the falling and rising duration of the climate fluctuation. The associated RMS of the temperature difference is 0.1744 °C. Both simulated and measured output current and power the PVT collector are depicted in Figure 7c. The maximal difference between the measured and simulated output current is also 0.3 A and the RMS of difference is 0.1636 A. In addition, the maximal difference between the measured and simulated output power is 1.5 W and the associated RMS is 0.9277 W. The power consumption of the compressor of HPWH system is also lower than the PV electricity as shown in Figure 7d. The water temperature and energy in the water tank are depicted in Figure 7e. The difference and RMS analyses for such a mostly sunshine day are also listed in Table 6.
From above analysis, it is seen that the proposed PVTA-HPWH model has a sufficient degree of accuracy under real sunny and mostly sunshine weather conditions. Even in face of the fluctuations of weather conditions, the model confidence is enough to predict the operation situations of overall PVTA-HPWH system. It should be noted that the proposed model slightly underestimates the output current and power posed to the overestimation of PVT temperature.
4.3. Performance Evaluation
From the viewpoint of energy utilization, the energy efficiency of the PVTA-HPWH is the summation of the efficiency of PV electricity generation and the thermal efficiency of water heating:
On the other hand, the comprehensive coefficient of thermal-to-electrical performance (COP) for the PVTA-HPWH system is defined as [3]:
Figure 8 demonstrates the corresponding efficiencies of the PVT device, including electrical, thermal, and the total efficiencies, for the sunny day (18 June 2013). The associated COP of the overall PVTA-HPWH system is also represented in Figure 8.
The solar electricity efficiency is in the range of 12.2%–12.5% with an average of 12.43% and the solar thermal efficiency is in the range of 73.70%–74.00% with an average of 73.80%. The total efficiency of the PVT device is in the range of 86.18%–86.27% with an average of 86.23%. It should be noted that some thermal energy is recovered from the surroundings because the PVT temperature is lower than the ambient one. On the other hand, the COP of the integrated PVTA-HPWH system is in the range of 7.01–7.10 with an average of 7.09. With the temperature upgrade of PVT evaporator, the power consumption of compressor is relieved. In addition, the PV efficiency is enhanced due to the cooling effect of refrigerant. The mean results of the efficiency of PVT evaporators and the COP of overall system are listed in Table 7.
For a mostly sunny day (12 June 2013), the electrical, thermal, and the total efficiencies of PVT device as well as the associated COP of the overall PVTA-HPWH system are depicted in Figure 9.
The solar electricity efficiency is in the range of 12.2%–12.5% with an average of 12.37% and the solar thermal efficiency is in the range of 73.70%–74.00% with an average of 73.90%. The total efficiency of the PVT device is in the range of 86.0%–86.5% with an average of 86.29%. On the other hand, the COP of the integrated PVTA-HPWH system is in the range of 7.07–7.10 with an average of 7.09. It should be pointed out that the fluctuation of solar irradiance does have a negative effect on the efficiency of the PVT device and the COP of PVTA-HPWH system. The mean results of both PVT efficiency and overall COP are also listed in Table 7.
5. Conclusions
In this paper a self-sufficient design for a PVTA-HPWT system was represented and validated with the proposed model and an experimental test rig under real weather conditions during June 2013. The swift changes of weather conditions have little negative effect on the performance of the PVTA-HPWH system. It does not affect the normal operation of the overall system from the viewpoint of dynamics. The solar electricity of rooftop PVT devices can provide the power consumption needs of compressor in the HPWH system. The following conclusions can be drawn:
- (1)
With a well-validated PVTA-HPWH model and the mass flow rate of refrigerant from the model-based prediction control, the results show that the proposed PVTA-HPWT model has sufficient confidence even in face of sunshine fluctuations. Swift changes of weather conditions have a small negative effect on the performance of the PVTA-HPWH system, but it does not affect the normal operation of the overall system from the viewpoint of dynamics;
- (2)
With the self-sufficient operation design for the PVTA-HPWT system, the solar electricity of PVT array is able to provide the power needed by the compressor in the HPWH system based on the model-based prediction control methodology;
- (3)
With the cooling effect of refrigerant on PVT devices, the PV efficiency can be improved. In addition, low-temperature refrigerant can directly extract ambient heat through the PVT array. This obviously enhances the thermal efficiency of PVT devices. The total PVT efficiency and the COP of the PVTA-HPWH system reach up to 86% and 7.09, respectively.
The author gratefully acknowledges the financial support by the projects NSC 101-2212-E-212-016 and NSC 102-2221-E-212-017 from Ministry of Science and Technology of the Republic of China.
Conflicts of Interest
The author declares no conflict of interest.
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Nomenclature
A | ideal factor |
A_{PVT} | PVT area (m^{2}) |
C_{PVT} | PVT heat capacity [J/kg·K] |
E_{BG} | band gap of cell (in eV). |
G | solar irradiance (kW/m^{2}) |
G^{STC} | standard test irradiance of 1 kW/m^{2} |
h_{Conv} | convection coefficient [W/(m^{2} · K)] |
h_{PVT2RF} | heat transfer coefficient [W/(m^{2} · K)] |
H_{i} | enthalpy of refrigerant in i state (J/kg) |
i | i state of HPWH operation |
I_{MPP} | rated output current at MPP in ampere (A) |
I_{PH} | photocurrent in ampere (A) |
I_{RS} | reverse saturation current in ampere (A) |
I_{S} | dark current in ampere (A) |
${I}_{\text{SC}}^{\text{STC}}$ | PV short circuit current at STC in ampere (A) |
k | Boltzmann's constant (= 1.38 × 10^{−23}J/K) |
K_{I} | short circuit current temperature coefficient (A/°C) |
K_{V} | open circuit voltage temperature coefficient (V/°C) |
m_{PVT} | PVT mass (kg) |
N_{P} (N_{S}) | parallel (series) number of cells |
P_{MPP} | maximum power rating at MPP in watt (W) |
P_{CP} (P_{PVT}) | compressor (PVT) power in watt (W) |
q | electron charge (= 1.6 × 10^{−19}C) |
Q_{Conv} | convective heat loss in watt (W) |
Q_{Rad} | long-wave radiation heat exchange in watt (W) |
Q_{RF} | heat removed by refrigerant in watt (W) |
Q_{Solar} | solar irradiation in watt (W) |
R_{S} (R_{SH}) | series (shunt) resistance in ohm (Ω) |
T_{Amb} | ambient temperature in Kelvin (K) |
${T}_{\text{PVT}}({T}_{\text{PVT}}^{\text{STC}})$ | PVT cell temperature (at STC) in Kelvin (K) |
v_{Wind} | wind speed (m/s) |
V_{MPP} | rated operating voltage at MPP in voltage (V) |
V_{OC} | open circuit voltage in voltage (V) |
x | vapor quality |
Greek Letters | |
---|---|
α | PVT absorptivity |
ε_{PVT} | PVT emissivity |
η | efficiency |
σ | Stefan-Boltzmann's constant |
Abbreviations | |
---|---|
Amb | ambient |
BG | band gap |
Conv | convection |
CD | condenser |
COP | coefficient of performance |
CP | compressor |
HPWH | heat pump water heating |
MPP | maximum power point |
OC | open circuit |
P | parallel |
PV | photovoltaic |
PVT | PVT device |
PVTA | PVT assisted |
Rad | long-wave radiation |
RF | refrigerant |
RS | reverse saturation |
S | series |
SAHP | solar-assisted heat pump |
Solar | Solar irradiance |
SC | short circuit |
SH | shunt |
STC | standard test condition |
TH | thermal |
Table 1. Comparisons among PVT mathematical models. |
Model types | Thermal characteristics | Electrical characteristics | References |
---|---|---|---|
Energy balance equation | ${\rho}_{\text{p}}{C}_{\text{p}}{\delta}_{\text{p}}\frac{\partial {T}_{\text{p}}}{\partial t}=[G{(\alpha \tau )}_{\text{p}}(1-{\beta}_{\text{c}})+G{(\alpha \tau )}_{\text{c}}{\beta}_{\text{c}}-E-S]-{h}_{\text{a}}({T}_{\text{p}}-{T}_{\text{a}})-{\mathit{\varepsilon}}_{\text{p}}\sigma ({T}_{\text{p}}^{4}-{T}_{\text{sky}}^{4})$ | E = Gη_{rc}[1 − β(T_{c} − T_{rc})]β_{c}(ατ)_{p} | Ji et al. [13] |
Heat balance equation | ${l}_{\text{pv}}{\rho}_{\text{pv}}{C}_{\text{pv}}\frac{\partial {T}_{\text{pv}}}{\partial t}=G{(\tau \beta )}_{\text{pv}}-E+{\alpha}_{\text{a}-\text{pv}}({T}_{\text{a}}-{T}_{\text{pv}})+{\alpha}_{r,\text{a}-\text{pv}}({T}_{\text{sky}}-{T}_{\text{pv}})+\frac{{T}_{\text{c}}-{T}_{\text{pv}}}{{R}_{\text{pv}-\text{c}}}$ | E = Gτ_{eva}η_{ref}[1 − 0.0045(T_{pv} − 298.15)] | Ji et al. [14] |
Steady-state energy transfer equation | ${l}_{\text{pv}}{\rho}_{\text{pv}}{C}_{\text{pv}}\frac{\partial {T}_{\text{pv}}}{\partial t}=G{(\tau \beta )}_{\text{pv}}-E+{\alpha}_{\text{a}-\text{pv}}({T}_{\text{a}}-{T}_{\text{pv}})+{\alpha}_{r,\text{a}-\text{pv}}({T}_{\text{sky}}-{T}_{\text{pv}})+\frac{{T}_{\text{c}}-{T}_{\text{pv}}}{{R}_{\text{pv}-\text{c}}}$ | N_{pv} = Iτ_{pv}η_{0}[1 − C_{T}(t_{p} − 25)]A_{pv} | Xu et al. [15] |
Quasi-steady state energy balance equation | Q_{t} = Q_{abs} − Q_{l} − Q_{e} = Q_{r} | Q_{e} = IA_{g,eff}η_{rc}[1 − β_{p}(t_{abs} − t_{rc})] | Zhao et al. [16] |
Thermodynamics equation | ${m}_{\text{PVT}}{C}_{\text{PVT}}\frac{d{T}_{\text{PVT}}}{dt}={Q}_{\text{Solar}}-{Q}_{\text{Rad}}-{Q}_{\text{Conv}}-{P}_{\text{PV}}-{Q}_{\text{RE}}$ | ${P}_{\text{PV}}={N}_{\text{P}}{I}_{\text{PH}}V-{N}_{\text{P}}{L}_{\text{S}}\left\{exp\left[\frac{q}{k{T}_{\text{PVT}}A}\left(\frac{V}{{N}_{\text{S}}}+\frac{I{R}_{\text{S}}}{{N}_{\text{P}}}\right)\right]-1\right\}V-\frac{1}{{R}_{\text{SH}}}\left(\frac{{N}_{\text{P}}V}{{N}_{\text{S}}}+I{R}_{\text{S}}\right)V$ | Proposed model |
Table 2. PVT Specifications (1 kW/m^{2}, 25 °C). |
Characteristics | Specifications |
---|---|
Maximum power rating (P_{MPP}) | 200.9 W |
Rated voltage (V_{MPP}) | 25.3 V |
Rated current (I_{MPP}) | 7.94 A |
Short circuit current (I_{SC}) | 8.41 A |
Open circuit voltage (V_{OC}) | 29.8 V |
Temperature coefficient of open-circuit voltage (K_{V}) | −95 mV/°C |
Temperature coefficient of short-circuit current (K_{I}) | 6.7 mA/°C |
Nominal operating cell temperature (NOCT) | 46 °C |
Table 3. Thermodynamics data of the R134a refrigerant at different points of the PVTA-HPWH system. |
Point | Phase | Pressure (bar) | Temperature (°C) | Enthalpy (kJ/kg) |
---|---|---|---|---|
1 | Vapor | 4.146 | 25 | 418.1 |
2 | Vapor | 14.915 | 65 | 437.5 |
3 | Liquid | 16.822 | 60 | 287.4 |
4 | Liquid/Vapor (x = 0.3876) | 4.146 | 10 | 287.5 |
Table 4. Control gains for mass flow rate of refrigerant (unit: g). |
Irradiance(W/m^{2}) | Temperature (°C) | ||||
---|---|---|---|---|---|
20 | 25 | 30 | 35 | 40 | |
0 | 0 | 0 | 0 | 0 | 0 |
200 | 10.38 | 10.65 | 10.97 | 11.34 | 11.79 |
400 | 20.98 | 21.26 | 21.58 | 21.96 | 22.41 |
600 | 31.59 | 31.87 | 32.30 | 32.58 | 33.04 |
800 | 42.20 | 42.48 | 42.81 | 43.20 | 43.66 |
1000 | 52.80 | 53.09 | 53.43 | 53.82 | 54.28 |
Table 5. Relative errors of the sensors. |
Sensor | Accuracy | Operating temperature |
---|---|---|
Irradiance | ±5% | −40 °C–80 °C |
Temperature | ±0.8 °C | −40 °C–100 °C |
Wind speed | ±5% | −20 °C–65 °C |
Electricity | ±5% | −20 °C–50 °C |
Table 6. Difference analysis for both a typical sunny day (18 June 2013) and a mostly sunny day (12 June 2013). |
Weather type | Items | PVT temperature | Output current | Output current |
---|---|---|---|---|
Typical sunny day | difference | ±0.35 °C | 0–0.3 A | 0–1.2 W |
RMS | 0.1339 °C | 0.1076 A | 0.6305 W | |
Mostly sunshine day | difference | ±0.4 °C | 0–0.3 A | 0–1.5 W |
RMS | 0.1744 °C | 0.1636 A | 0.9277 W |
Table 7. Mean analysis of efficiency and performance for both a typical sunny day (18 June 2013) and a mostly sunny day (12 June 2013). |
PV efficiency | Thermal efficiency | Total efficiency | COP | |
---|---|---|---|---|
Typical blue-sky day (18 June 2013) | 12.43% | 73.80% | 86.23% | 7.09 |
Mostly sunshine day (12 June 2013) | 12.37% | 73.90 | 86.29 | 7.09 |
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