Repositorio Institucional de Documentos

ANEXO 1 Institut für Wärme- und Brennstofftechnik TECHNISCHE UNIVERSITÄT BRAUNSCHWEIG MASTER THESIS “Simulation of the power and heat demand of a building in Soller and the solution with solar-thermal collector and photovoltaic generator” WS 2010/2011 Andrés Gil Cladera Regist. number: 4043520 Tutors: Dipl-Ing. Shaofei Chen Prof. Dr. techn. Reinhard Leithner Braunschweig, November 2010 \\Herbert\sun40\users\shaofei\Documents\Organisation\DASA\Gil\Aufgabestellung\Aufgabenstellung_DA_Solar_Gil2010.doc Starting date: : Submission date: References: Argudo Perez, Ignacio: Wassererwärmung und Heizungsunterstützung für ein Einfamilienhaus mit Solarflachkollektor und Wärmetauscher, Diplomarbeit, IWBT, TU Braunschweig, 2006 Logosu-Teko, Adama: Optimierung der Speicheranbindung und der Regelung eines Systems zur solarunterstützten Nahwärmeversorgung, Studienarbeit, IWBT, TU Braunschweig, 2001 Strelow, Martin: Optimierung des Kollektorkreisregelung der solar unterstützten Nahwärmeversorgung, Diplomarbeit, IWBT, TU Braunschweig, 2004 Chen, T.Y.: Real-time predictive supervisory operation of building thermal systems with thermal mass, Energy and Buildings, Volume 33, Issue 2, Jan. 2001, p141-150. Fang, G. Y. et al.: Experimental investigation on the photovoltaic–thermal solar heat pump air-conditioning system on water-heating mode, Experimental Thermal and Fluid Science, Volume 34, Issue 6, September 2010, p736-743 DIN 4701: Regeln für die Berechnung des Wärmebedarfs von Gebäuden: Teil 1: Grundlagen der Berechnung, März 1983 Teil 2: Tabellen, Bilder Algorithmen, März 1983 Teil 3: Auslegung von Raumheizeinrichtungen, August 1989 Deutsches Institut für Normung e.V., Beuth Verlag GmbH, Berlin, Wien, Zürich DIN 4701-10: Energetische Bewertung heiz- und raumlufttechnischer Anlagen – Heizung, Trinkwassererwärmung, Lüftung. Deutsches Institut für Normung e.V., Beuth Verlag GmbH, Berlin, August, 2003 DIN 4108-6: Wärmeschutz und Energieeinspeisung in Gebäuden – Berechnung des Jahreswärme – und des Jahresenergiebedarfs. Deutsches Institut für Normung e.V., Beuth Verlag GmbH, Berlin, Juni, 2003 Eidesstattliche Erklärung Hiermit versichere ich, dass ich die vorliegende Bachelor-Arbeit selbstständig angefertigt, keine anderen als die angegebenen Hilfsmittel benutzt habe. Braunschweig, den 12. November 2010 Andres Gil Cladera *** Abstract *** In this Thesis, a simulation of the energy demand of a building in Soller is made according to the characteristics of the building and the climatic variables in this locality. Two different regenerative generator systems are developed to meet the power, heat, cooling and hot sanitary water demand of the building. The first installation covers the heat and cooling demand by means of a photovoltaic generator in combination with a reversible heat pump. The hot sanitary water demand is covered in this case through a thermal collectors installation. The second developed installation uses a thermal collectors installation to cover the heat and hot sanitary water demand. Cooling is also supply by the same thermal collectors installation in combination with an adsorption machine. The electrical grid is considered as backup power source for both installations for case of too high power demand. The performance of both installations is simulated and compared one another. CONTENTS 1 Contents Symbol list 1. INTRODUCTION..........................................................................10 1.1. Motivation..............................................................................................10 1.2. Objectives..............................................................................................10 1.2.1. General Objectives.............................................................................10 1.2.2. Specific Objectives.............................................................................10 1.3. Description of the project.......................................................................11 1.3.1. Fundamentals....................................................................................11 1.4. Solar Resources .....................................................................................11 1.4.1. The Sun.............................................................................................11 1.4.2. Composition of Solar Irradiance.........................................................12 1.4.3. Position of the sun.............................................................................13 1.4.4. Calculation of shadows......................................................................14 1.4.5. Inclination of collectors......................................................................15 2. DESCRIPTION OF THE HOUSE......................................................18 2.1. Location.................................................................................................18 2.2. Climatic Data..........................................................................................18 2.3. Geometric Description............................................................................19 2.4. Building envelope ..................................................................................20 2.4.1. External walls....................................................................................21 2.4.2. Roof..................................................................................................22 2.4.3. Floor..................................................................................................22 2.5. Hollows on building envelope..................................................................23 2.5.1. Glazed surfaces.................................................................................23 2.6. Internal Walls.........................................................................................24 CONTENTS 2 3. LOAD CALCULATION..................................................................26 3.1. Design Conditions..................................................................................26 3.1.1. Heating and Air Conditioning.............................................................26 3.1.2. Electrical Appliances..........................................................................28 3.1.3. Hot sanitary water..............................................................................29 3.2. Calculation of Solar Radiation Loads........................................................30 3.2.1. Solar radiation on any orientation.......................................................30 3.2.2. Solar radiation on opaque surfaces.....................................................30 3.2.3. Solar radiation trough transparent surfaces .......................................31 3.3. Heat convection transfer Loads 32 3.4. Air filtration and ventilation flow loads.....................................................32 3.4.1. Design parameters.............................................................................32 3.4.2. Sensible and latent heat.....................................................................33 3.5. Human Heat, Lighting and Electrical Appliances Loads..............................34 3.6. Energetic Balance – Finite Difference Method............................................34 3.6.1. Simplifying Assumptions....................................................................35 3.6.2. Heat and Moisture Transfer at Interior Nodes.....................................35 3.6.3. Heat and Moisture Transfer at Surface Nodes.....................................36 3.6.4. Space air temperature........................................................................37 3.7. Control of temperature...........................................................................37 3.7.1. Ziegler-Nichols Method......................................................................38 3.8. Results of the simulation.........................................................................40 4. SOLAR INSTALLATIONS...............................................................42 4.1. Photovoltaic Installations........................................................................42 4.1.1. Introduction.......................................................................................42 4.1.2. Design Conditions.............................................................................42 4.1.3. Photovoltaic Panels............................................................................43 4.1.4. Batteries............................................................................................46 4.1.5. Charge controller...............................................................................47 4.1.6. DC/AC Inverter..................................................................................48 4.2. Hot sanitary water installation.................................................................48 4.2.1. Introduction.......................................................................................48 CONTENTS 3 4.2.2. Design Conditions.............................................................................49 4.2.3. Thermal Collectors.............................................................................50 4.2.4. Storage Tank.....................................................................................51 4.2.5. Expansion Tank.................................................................................52 4.2.6. Auxiliary Heating...............................................................................52 4.3. Adsorption Machine Installation..............................................................53 4.3.1. Introduction.......................................................................................53 4.3.2. Description of the installation............................................................53 4.3.3. Thermal Collectors.............................................................................54 4.3.4. Storage Tank.....................................................................................54 4.3.5. Adsorption Machine...........................................................................54 4.3.6. Dissipater..........................................................................................58 5. INSTALLATION SIZING.................................................................59 5.1. CASE 1: HEAT PUMP INSTALLATION: AIR CONDITIONING AND HEATING THERMAL COLLECTORS INSTALLATION: HOT SANITARY WATER........60 5.1.1. Design Conditions for the heat pump installation...............................60 5.1.2. Selection of Equipments.....................................................................61 5.1.2.1. photovoltaic panels....................................................................61 5.1.2.2. charge controller........................................................................62 5.1.2.3. Batteries.....................................................................................63 5.1.2.4. DC/AC Inverter...........................................................................64 5.1.2.5. Heat pump.................................................................................65 5.1.3. Results of the Simulation for the heat pump.......................................66 5.1.4. Design conditions for thermal collectors installations.........................68 5.1.5. Selection of equipments....................................................................69 5.1.5.1. Thermal Collectors.....................................................................69 5.1.5.2. Accumulator...............................................................................69 5.1.5.3. Expansion Tank..........................................................................70 5.1.5.4. Auxiliary Heating........................................................................70 5.1.6. Results of the simulation....................................................................71 5.2. CASE 2: ADSORPTION MACHINE INSTALLATION: AIR CONDITIONING, HEATING & HOT SANITARY WATER............................................73 5.2.1. Design Conditions for adsorption machine.........................................73 5.2.1.1. Heating and cooling...................................................................73 5.2.1.2. Hot sanitary water......................................................................74 5.2.1.3. Appliances.................................................................................74 5.2.2. Selection of equipments.....................................................................75 5.2.2.1. Thermal Collectors.....................................................................75 5.2.2.2. Accumulator...............................................................................76 CHAPTER ONE 10 1. INTRODUCTION 1.1. Motivation In opposition to the growing problems that are being caused by the traditional forms of energy production, renewable energies have undergone a great development during the last years including solar technologies. Nowadays, solar technologies are able to supply energy in remote places where no other kinds of energy are available. It is also possible today connecting installations to the electric grid in order to get profit from the reduction of the electrical bill, certainty in energy supply and for using environment friendly technologies. 1.2. Objectives 1.2.1. General Objectives The main objective of the project is to calculate the necessities of power, heat and warm water of a building. In the present study the equations which govern the transfer of heat will be implemented to make a simulation of the energy balance in a building. 1.2.2. Specific Objectives The building in which the simulation will be made is located in Soller (Mallorca) where a regenerative generator system with solar-thermal and photovoltaic technology should be developed to provide with the power, heat, cooling and warm water demand of the building. The climatic dates from a reference year and the design conditions established by the Spanish current legislation will be used to solve the equations. CHAPTER ONE 11 Likewise, the installation covering the energy demand will be sized and calculated. In a first part of this study, warm water will be provided by a thermo-solar collector. Heat and cool for heating and air conditioning will be provided by a reversible heat pump. Electricity to feed the heat pump will be provided by a photovoltaic generator. In the second part, the study of viability of an absorption machine to provide heating and air conditioning will be made in order to compare with the heat pump installation from the first part and to chose the best technology for this case. The solar collectors will provide hot water to feed the absorption machine as well as hot sanitary water. 1.3. Description of the project 1.3.1. Fundamentals The basis of conduction heat exchange are the equations of heat transfer from Fourier ˙ Q=−⋅A⋅∂T ∂x (1.1) and the variation of internal energy ˙ Q=⋅cp ⋅A⋅∂T ∂t⋅dx (1.2) Some simplifying assumptions are going to be accepted •Heat and moisture flow are one-dimensional •Thermal properties of the building materials are homogeneous •The properties of the air-stream flowing over the surface of the building structures are homogeneous. •The surface temperature differences between the partition walls, ceiling, and floors are small; therefore, the radiative exchange between these surfaces can be ignored. The finite difference method will be used to solve the energy balance in the building. The complete description of it will be made in chapter 3. 1.4. Solar Resources 1.4.1. The Sun The Sun is a giant sphere of very high temperature gases with a 1.39 x 109 m diameter and placed about 1.5 x 1011 m from the Earth. The Earth receives on its external atmosphere about 1.73 x 1014 kW power from the Sun. The irradiance, Gsurf , is the radiative energy that arrives per square meter on a surface perpendicular to the beams. It is in W.m-2 measured. It is also defined the Solar Constant, CSolar , as the irradiation that arrives at the external surface of the atmosphere. Its value is given by the NASA as 1353 W.m-2 ( ± 1.6%). Nevertheless, the temporal distribution of the irradiance which arrives at the surface of the CHAPTER ONE 12 Earth is lower and very irregular according to the instantaneous composition of the atmosphere. This fact is observed in figure 1.1 Figure 1.1 – Solar irradiance on the Earth surface 1.4.2. Composition of Solar Irradiance As result of the interaction between the solar radiation with the atmosphere, the energy which arrive at a surface has several components: Direct irradiance, GBh ( W.m-2), whose direction has not been modified by the atmosphere; Diffuse irradiance , GDh ( W.m-2), which came from all over the vault of heaven because of multiples reflections on the atmosphere; and the radiation which has been previously reflected on the floor. The reflectance on the floor depends on the Albeldo , that is a property of the surface of the floor. Some examples are shown in table 1.1. Surface Albeldo Snow 0.95 Water (big incidence angles) 0.07 Grass 0.26 Gravel 0.13 Table 1.1 – Albeldo of different surfaces (source: [12]) The composition of these radiations is called Global irradiance , GGh ( W.m-2). The proportion between one type or other depends on the meteorological conditions as shown in table 1.2 CHAPTER ONE 13 Climatic conditions Irradiance ( W.m-2) Diffuse component (%) Clear sky 700 - 1000 10 - 20 Partially cloudy 200 - 500 20 - 90 Totally cloudy 50 - 150 90 - 100 Table 1.2 – Diffuse irradiance on several conditions (source [10]) The diffuse irradiance is not isotropic. Also in very cloudy days, the diffuse irradiance is clearly anisotropic. In this project, the value of diffuse irradiance on the horizontal surface, given by METEONORM, (see Appendix A), will be considered constant in all directions for each instant. This assumption is acceptable because mostly days of the year in the place where the project is located are very sunny, and global irradiance involve a low percentage of the diffuse component . Detailed information about the calculation of diffuse irradiance on inclined planes is given in [16]. 1.4.3. Position of the sun. The position of the sun for an observer placed on the surface of the Earth is defined by two angles: 1) Azimuth, φ (º): Is the angle between the horizontal projection of the line that links the observer with the Sun, and the South direction. The Azimuth is 0º if the projection of solar radiation on an horizontal plane follows the axis North-South. Azimuth angles are negatives from the South direction to the East. Azimuth angles are positives from South direction to the West. 2) Solar altitude, ϕ (º): Is the angle between an horizontal surface and the line that links the observer with the Sun. On the other hand, for mostly of problems involving solar technologies, the surfaces where the solar radiation arrives are defined also with two angles δ (º): inclination of the main plane of the surface respect the horizontal. θ (º): angle between the horizontal projection of the normal vector of the surface, and the axis North-South. The relation between these angles is shown in figure 1.2 CHAPTER ONE 14 Figure 1.2 – Position of the sun. 1.4.4. Calculation of shadows The looses of solar radiation suffered by a surface due to projected shadows from surrounding obstacles are variables during a day and depend on the latitude, the date and the time. They must be considered in order to get the maximum profit from a solar installation. The basis relation between the length of the shadow, Lshadow , the height of the obstacle, Hobst , and the solar altitude is tg hs= Hobst Lshadow (1.3) Solar installations expose great surfaces to the sun by means of thermal or photovoltaic collectors depending the used technology to catch the energy from the sun. In the present study it is generally used the name “collector” for any surface catching the solar radiation to get profit of it; it is used the name “photovoltaic panel” if the solar radiation is directly transformed into electrical power; and “thermal collector” if the solar radiation is transformed into heat power. The purpose of this discussion is avoiding that any shadow is projected over a panel or collector. Therefore, the minimum distance in which the collectors must be placed, according the figure 1.3, will be Lmin=Lcollector⋅ [ sen tg  cos ] (1.4) CHAPTER ONE 15 Figure 1.3 - Minimum distance between collectors 1.4.5. Inclination of collectors The radiation that arrives at a surface is given by the equation (1.5) – see also chapter 3 – for each orientation an inclination of the surface and each position of the sun. Gsurf =GBh ⋅[cos⋅sen⋅cos−sen⋅cos]GDh [W/m2 ] (1.5) Solar installations have usually mechanical systems to orient the collectors into the sun called solar trackers . Its function is to ensure that the surface of collectors remains perpendicular to solar beams. There are two main groups, according to the degrees of freedom: Dual axis tracker They have two degrees of freedom. Therefore, the surface remains always perpendicular to the sun. They are divided into Tilt Dual Axis Tracker : The axes of rotation are typically aligned either along a true North meridian or an east west line of latitude. Azimuth – Altitude Dual Axis Tracker : Its primary axis is vertical to the ground. The secondary axis is then typically normal to the primary axis. Single axis tracker There is one degree of freedom. They are divided into Horizontal single axis tracker : The axis of rotation is horizontal with respect to the ground. CHAPTER ONE 16 Vertical Single Axis Trackers : The axis of rotation is vertical with respect to the ground. These trackers rotate from East to West over the course of the day. Tilted Single Axis Trackers : They are so considered all trackers with axes of rotation between horizontal and vertical. A particular implementation of this type of tracker is the Polar Aligned Single Axis Trackers, in which the tilt angle is equal to the latitude of the installation. Fixed installation The collectors of these installation have not any degree of freedom. The collectors should be oriented to the South, if the installation is placed on North hemisphere; and to the North, if the installation is placed in South hemisphere, in order get the greatest profit of solar irradiance. The optimal angle of collectors δ (º) depends on the use of the installation during a year If it is desired an optimal efficiency for all the year, the tilt of the panels should be equal to the latitude of the place. This tilt will be 15º bigger if it is needed a best use in winter, and 15º smaller for a best use in summer. The relation between the tilt of the panels and the energy which arrive at them is shown in figure 1.3 Figure 1.3 – Received energy in Baleares according to the tilt of the panels CHAPTER ONE 17 CHAPTER TWO 18 2. DESCRIPTION OF THE HOUSE 2.1. Location The building is located in Soller, in Mallorca (Spain). The coordinates of this place are 39º 47' Latitude North and 2º 4” Longitude East [1]. Exact location of this locality is shown in figure 2.1. Figure 2.1 – Location of the building (source: National Geographic Institute [1]) 2.2. Climatic Data The climatic data in this place have been calculated with the software METEONORM [2] from the measurements of 2005, every hour, by interpolating from the real data from the nearest meteorological stations [3]. A summary of results is described in the Appendix A. The assumption of 2005 as a reference year is accepted and the measurements are considered representative enough for this locality. The main obtained data are shown in table 2.1. CHAPTER TWO 19 Symbol Description Units GGh Global solar radiation measured in horizontal surface [W.m-2] GBh Direct solar radiation measured in horizontal surface [W.m-2] GDh Diffuse solar radiation measured in horizontal surface [W.m-2] φ Azimuth [º] ϕ Solar Altitude [º] vwind Speed of the wind [m.s-1] DD Direction of the wind respect North direction [º] Tamb Temperature of the air [ºC] RHamb Relative Humidity of air [%] Table 2.1 - Obtained parameters with software METEONORM Figure 2.2 shows the different climatic zones in which the land is divided. Figure 2.2 – Climatic zones in Spain according to [4] According to [4], there is 12 climatic zones in function of climatic severity of winter (A, B, C, D y E), and summer (1, 2, 3, 4). Impossible combinations for Spanish climatology are excluded. Knowing to which climatic zone belong the installation is required to set some design parameters in next sections. The location where this project is placed corresponds with the climatic zone B-IV. 2.3. Geometric Description A plane of the building is shown in the figure 2.3 CHAPTER THREE 26 3. LOAD CALCULATION 3.1. Design Conditions 3.1.1. Heating and Air Conditioning The design conditions for Air Conditioning and Heating are established according to the valuation of thermal comfort. Thermal comfort can be defined like a subjective perception of conformity with existing thermal ambiance. There is six parameters which influence on the thermal comfort. Environmental parameters Air Temperature inside the room, T0 Relative Humidity inside the room, RH0 Medium Radiative Temperature inside the room, Tm,rad,0 Medium speed of air inside the room, vm,0 Personal parameters Metabolism Thermal Resistance of Clothes The design conditions for air conditioning installations are regulated by the [5] (RITE - Regulations of Thermal Installations of Buildings, according its initials in Spanish), on the basis of Fanger's method about heat exchange between human body and the environment. Fanger's method is detailed explained in the norm UNE-EN ISO 7730 [7], and the inform CR 1742-1998 [8], about quality of air. In absence of more details, the values given in [11] are going to be accepted. Four parameters should be studied to satisfy this regulations: –Exigence of environmental thermal quality –Exigence of internal air quality –Exigence of hygiene CHAPTER THREE 27 –Exigence of acoustic environmental quality The design values of these parameters are shown in table 3.1 Parameters Winter Summer Operative Temperature 21 – 23 23 – 25 Speed of air < 0.15 m/s < 0.25 m/s Relative Humidity 40 – 50 45 – 60 Thermal resistance of clothes 1 clo 0.5 clo Metabolic activity 1.2 Met 1.2 Met Table 3.1 – Parameters of thermal comfort inside the room The velocity of air inside the room, for a PPD = 15%, is set in reference [5] as v0=T0 100−0.07 [m/s] (3.1) where T0 = Dry temperature of the air inside the room PPD = Predictable percentage of dissatisfied. The operative Temperature is also in [5] defined as Toperative=T0Tm, rad 2 [ºC] (3.2) where Tm,rad = Medium radiative temperature of building envelope. In relation with the quality of air there is four categories according to the use of the building. For each category there is a minimum external flow of ventilation. For this project the quality IDA 2 will be set. All the space in the building are considered habitable space with low internal heat dissipation, according to the classification made in [4], where the amount of heat dissipated from illuminating or equipment will be low. In absence of more detailed dates, the hygrometric rate will be 3, according to the norm UNE-EN ISO 13788: 2002 [9]. The values of ventilation flow are shown in the table 3.2. CHAPTER THREE 28 Category Use of the building Ventilation flow (dm3/s per person) IDA 1 (excellent quality air) Hospitals, clinics, laboratories, nurseries 20 IDA 2 (good quality air) Offices, residences, libraries, museums, schools 12.5 IDA 3 (medium quality air) Magazines, cinemas, theaters, hotel rooms, bars, cafeterias, computer rooms... 8 IDA 4 (bad quality air) - 5 Table 3.2 – Quality of air and external flow of ventilation [5] 3.1.2. Electrical Appliances. In absence of more details, the installation of table 3.3 is assumed to be placed in the building. Units Description Power per unit (W) Subtotal (W) Time of use (hours/day) Energy (Wh/day) 2 Fluorescent kitchen 36 72 4 288 7 Compact fluorescent lamp 11 77 4 308 1 Wash machine 1000 1000 1 1000 1 Refrigerator 200 200 6 1200 1 Electric cooker 1500 1500 1 1500 1 TV 75 75 2 150 1 Computer 100 100 2 200 1 Iron 1500 1500 0.5 750 1 Hair dryer 800 800 0.5 400 1 Toaster 800 800 0.5 400 TOTAL 6124 (W) 6196 (Wh/day) Table 3.3 – Installed Power and times of use It is imposed a 0.3 coefficient of simultaneity, Ksimult , as design condition for the current study, according to the planned use of the building. The highest instantaneous power demanded by the building by accepting Pinstalled ≈ 6200 (W) is given as: Pmax , appliances = Pinstalled * Ksimult = 6200 * 0.3 = 1860 W The energy consumed by the appliances, in I.S. Units and by accepting 6196 ≈ 6200 (Wh) , is: CHAPTER THREE 29 Eappliances = 6200.3600 (J) = 22.32 106 (J) 3.1.3. Hot sanitary water Table 3.4 is an extract from reference [4]. It shows the needed flow of hot sanitary water, ˙ VHSW [liters/day.person], according to the use of the building. Use of the building Flow [liters of HSW/day] ( 60°C) Single family house 30 Per person Multi family building 22 Per person Hospitals and clinics 55 Per bed Hotels (four star) 70 Per bed Hotels (three star) 55 Per bed Hostel/Hotel (two star) 40 Per bed Camping 40 Per place Pension/Hotel (one star) 35 Per bed Residence (old people, students...) 55 Per bed Schools 3 Per student Factories 15 Per person Gymnasium 20 to 25 Per person Laundry 3 to 5 Per kilogram of clothes Restaurants 5 to 10 Per meal Cafeterias 1 Per lunch Table 3.4 – Consumption of Hot sanitary water (HSW) according the use of the building According to [4], the temperature of storage will be 60 °C If the installation is designed with a different storage temperature, Tacc , the required flow ˙ VHSW Tacc  must to be modified every month like follows, according the equation given in [4]. ˙ VHSW Tacc ºC =˙ VHSW 60ºC ⋅60−Tw ,net Tacc−Tw ,net [liters/day.person] (3.3) where ˙ VHSW Tacc  = Flow of HSW at temperature T ˙ VHSW 60  = Flow of HSW at temperature 60 ºC (given in table 3.4) Tw,net = Median temperature of water in public net every month (ºC) CHAPTER THREE 30 3.2. Calculation of Solar Radiation Loads 3.2.1. Solar radiation on any orientation In the locality of Soller, the value of solar radiation can be very important in order to calculate the load of heating and air conditioning. A difference is make between the radiation which arrives at opaque surfaces – walls, roof and doors – and the radiation which arrives at windows (transparent hollows) From the dates of solar radiation of the software METEONORM, the values of solar radiation on an horizontal surface are known, as well as the position of sun, which is given by the Azimuth, φ , and the solar altitude, ϕ (see also chapter 1 – Position of the Sun) The criterion for Azimuth angle is the following 0° for South orientation positive angles for East orientation negatives angles for West orientation. With those parameters it is possible to calculate the radiation of sun on any orientation and inclination surface, by using the relation of Fariña (1990) [22]: Gsurf =GBh ⋅[cos⋅sen⋅cos−sen⋅cos]GDh (3.4) where GBh = direct radiation on an horizontal surface (W/m2 ) GDh = diffuse radiation on an horizontal surface (W/m2 ) φ = Azimuth (º) ϕ = solar altitude (°) δ = inclination of the surface respect the horizontal (º) θ = orientation of the surface (º) In this project it is assumed that the diffuse radiation is constant in every direction. Detailed information about the calculation of diffuse irradiance on inclined planes is given in [16]. 3.2.2. Solar radiation on opaque surfaces The value of solar radiation is taken in this section to calculate the temperature equivalent on the surface, Teq [24] as following: Teq=Tamb0 ⋅Gsurf hamb (3.5) where: CHAPTER THREE 31 α0 = absorptivity coefficient of the surface, given in table 3.3 hamb = convection coefficient in external surface To calculate hamb the assumption of forced convection is accepted. According to [12](chapter 3), it is given for a normal range of air velocities as hamb=10.224.47⋅vwind [W/m2.K] (3.6) where vwind = speed of wind over the surface (m/s) The temperature equivalent on the surface, Teq , is used on section 3.3 to calculate the conduction heat. 3.2.3. Solar radiation trough transparent surfaces The solar radiation which arrives at the surface of the window is given by (3.4). But not all this radiation is able to go trough the window. It's needed to know the solar factor Fsolar of the window, given like a % of radiation able to go inside the building through the window. The modified solar factor is given in reference [4] as Fsolar =Fshadow⋅[1−Fframe⋅gFframe ⋅0.04⋅0 ⋅Uframe ] [%] (3.7) where Fframe = percentage of surface covered by the frame (including the box for the blind) Uframe = heat transfer coefficient of the frame α0 = absorptance of the surface, according the color of the material given in table 3.5 Fshadow = fraction of window surface receiving the solar radiation g = transmittance of the glasses given in [15] Colour Claire Medium Dark White 0,20 0,30 0,00 Yellow 0,30 0,50 0,70 Beige 0,35 0,55 0,75 Brown 0,50 0,75 0,92 Red 0,65 0,80 0,90 Green 0,40 0,70 0,88 Blue 0,50 0,80 0,85 Grease 0,40 0,65 -- Black -- 0,96 -- Table 3.5. Absorptance coefficient of the frame according its colour CHAPTER THREE 32 The effect of curtains or drapes is not considered in a first approximation. 3.3. Heat convection transfer Loads During the insolation time, the convection on external walls is already considered as indicated in chapter 3.2.2. When solar radiation is equal zero, forced convection is considered on external walls, in which the parameter hamb is given by the equation (3.6) On internal walls, natural convection is considered with the coefficients of heat transfer given in the table 3.6, which has been extracted from [4]. Position of the wall and direction of heat flow h0 [W/m2.K] Vertical enclosures – or pitch over horizontal > 60° – and horizontal heat flow 7,69 Horizontal enclosures – or pitch over horizontal ≤ 60° – and ascending heat flow 10 Horizontal enclosures – or pitch over horizontal ≤ 60° – and descending heat flow 5,88 Table 3.6 – Heat transfer coefficient for natural convection The equation for convection heat transfer is given for each surface of the building as ˙ Qsurf =Asurf⋅h0, surf⋅Tsurf −T0 [W] (3.8) where h0,surface = natural convection heat transfer coefficient, given in table 3.6 T0 = air temperature inside the building (ºC) Tsurf = temperature on the internal surface of the building (ºC) Asurf = area of considered surface [m2] 3.4. Air filtration and ventilation flow loads 3.4.1. Design parameters In reference [4] are set the maximum values of permeability to the air for woodwork or metalwork, in the building envelope, with an overpressure of 100 Mpa, according to the climatic zone where the building is placed. The values are the followings: a) Climatic zones A y B : 50 m3 / h.m2 . CHAPTER THREE 33 b) Climatic zones C, D and E : 27 m3 /h.m2 . In the absence of more information, the maximum value for the climatic zone B is going to be used for the loads in this section. On other hand, the [4], sets the minimum values of ventilation flow, in l/s, as shown in table 3.7 Per occupant Per m2Per room Type of local Bedroom 5 Living room 3 Bath room 15 Kitchen 2 Table 3.7 – Minimum ventilation flow l/s 3.4.2. Sensible and latent heat The loads of air filtration and ventilation have one component of sensible heat and one component of latent heat. The component of sensible heat is due to the difference of temperatures between the exterior and the design temperature, and its value is given as ˙ Qamb ,sens=amb ⋅cp , amb ⋅˙ Vventilation ⋅Tdesign−Tamb  [W] (3.9) The latent heat is due to the difference of humidity, and given as ˙ Qamb ,lat=2442⋅˙ m⋅wamb−w0 [W] (3.10) where 2442 kJ/kg = enthalpy of vaporization of water at 25 ºC ([3]) (design temperature in Summer) wamb = specific humidity of external air (kg water/kg dry air) w0 = air specific humidity inside the building (kg water/kg dry air) w=0.622⋅psteam p−psteam [kg water/kg dry air] (3.11) where psteam = partial pressure of vapour (Pa) pamb = atmospheric pressure (Pa) The next relation is needed to calculate psteam RH amb=100⋅psteam psat [%] (3.12) CHAPTER THREE 34 where psat = saturation pressure (Pa) RHamb = relative humidity of the ambiance, given in climatic data according to appendix G of [4], psat is given as if Tamb > 0° → psat=610.5⋅exp  17.269⋅Tamb 237.3Tamb  (3.13) if Tamb < 0° → psat=610.5⋅exp  21.875⋅Tamb 265.5Tamb  (3.14) Note that equations 3.13 and 3.14 are just valid if temperatures are given in Kelvin [K], and not in Celsius degrees. 3.5. Human Heat, Lighting and Electrical Appliances Loads The gains due to Human Heat, Lighting and Electrical Appliances are going to be ignored in this study because they are considered to have a very low influence compared with the other gains. 3.6. Energetic Balance – Finite Difference Method This section is an extract of reference [9]. To make the simulation of heat flows, the finite difference method is used. Each surface composing external walls and roof is divided in small layers each one with the same length ∆x. Each layer corresponds with a node. The subscript i makes reference to the number of the node. Interior nodes are located at the center of the layer and surface nodes are located on the surface, as shown in figure 3.1. An energy balance or a mass balance at each node at selected time intervals results in a system of algebraic equations that can be employed to determine the temperature and moisture for each node in terms of neighbouring nodal temperatures or moisture contents, nodal geometry, and the thermal and moisture properties of the building structure. The amounts of stored heat and moisture are expressed as an increase of internal energy and moisture content at the nodes. Heat conduction can be approximated by using the finite difference form of the Fourier law, as ˙ Qi1i=i ⋅AiTi1 t−Ti t x [W] (3.15) CHAPTER THREE 35 where λi = thermal conductivity of node i (W.K-1.m-1) Ai = surface of layer i (m2) Ti1 t = Temperature of node i+1, at time t (K) Ti t = Temperature of node i, at time t (K) ∆x = spacing between the nodal points (m) Figure 3.1 – selection of nodes 3.6.1. Simplifying Assumptions When the finite difference method is used to calculate space cooling loads, simplifications are often required to reduce the number of computer calculations and to solve the problem more easily. The errors due to simplification should be within acceptable limits. For a typical room in the building, as shown in figure. 3.1, the following are the simplifying assumptions: •Heat and moisture flow are one-dimensional. •Thermal properties of the building materials are homogeneous. •The properties of the air stream flowing over the surface of the building structures are homogeneous. •The surface temperature differences between the partition walls, ceiling, and floors are small; therefore, the radiative exchange between these surfaces can be ignored. 3.6.2. Heat and Moisture Transfer at Interior Nodes An interior node i is considered as shown in the left part of figure. 3.1. For a onedimensional heat flow, if there is no internal energy generation and according to the principle of heat balance, the energy balance of node i is ˙ Qi−1i˙ Qi1i=∂Ei ∂t≈b ⋅cp, b ⋅Ai ⋅ x⋅Ti t−t−Ti t t (3.16) Substituting (3.15) into (3.16) and solving for Ti t t , we have Ti t t=Foi ⋅Ti−1 tTi1 t1−2⋅Foi⋅Ti t (3.17) CHAPTER FOUR 42 4. SOLAR INSTALLATIONS 4.1. Photovoltaic Installations 4.1.1. Introduction A photovoltaic installation takes the energy from the solar radiation and transforms it directly into electric energy by means of the photovoltaic panels. A basis schema of an isolated installation is shown in figure 4.1. The description of each element is made below. Figure 4.1 - Photovoltaic isolated installation elements 4.1.2. Design Conditions The maximal power and the energy consumed by the appliances was calculated in chapter 3.1.2. as Pmax,appliances = Pinstalled . Ksimult = 6200 * 0.3 = 1860 W Eappliances = 6200.3600 (J) = 22.32 106 (J) CHAPTER FOUR 43 If the energy needed to feed the heat pump, Eheatpump is included, the theoretical electric energy consumed by the photovoltaic installation, ET,photo (W) will be ET , photo=EheatpumpEappliances [ J ] (4.1) The electrical energy consumed by the heat pump depends on the concret equipments chosen for this application. Therefore, the variable Eheatpump is calculated in chapter 5.2.2. The energy required by the installation is affected by a general efficiency factor of the installation, ηphoto . This factor involves some looses for Joule's effect or looses in the batteries. Therefore, the energy needed by the installation is Ephoto=ET , photo photo [ J ] (4.2) This value will allow to size correctly the installation. The parameter ηphoto is also needed to size the batteries installation. The method to calculate ηphoto is described in the chapter 4.1.4. 4.1.3. Photovoltaic Panels The photovoltaic panels transform the solar radiation into direct current (DC) through the photoelectric effect which was described the first time in 1905 by Albert Einstein. Although the efficiency of the panels is nowadays not very high (around 15 %), its use allows to get electrical energy in remote locations where other sources are not available. The chosen panels for this installation are the SolvisPico PI-AE/210 Wp, whose characteristics are shown in tables 4.1 , 4.2, 4.3 and 4.4. See also Appendix D. Table 4.1 – Dimension and Weight CHAPTER FOUR 44 Table 4.2 – Cell characteristics Table 4.3 – Operating limits The next development and its equations is an extract from reference [10]. NOCT (nominal operating cell temperature) is the cell temperature with 800 W/m² irradiance, perpendicular to the module, when the ambient temperature is 20°C and the wind speed is 1 m/s. The value of NOCT is used to determine the operating cell temperature. It is assumed, according to [10], that the difference between the temperature of the cell, Tcell and the temperature of the air, Tamb , depends linearly on the irradiation on the panel Gpanel (W/m2), according to: Tcell−Tamb=NOCT −20° C 800 ⋅Gpanel [°C] (4.3) Table 4.4 – Electrical Specifications These electrical specifications are valid under the standard test conditions (STC) (airmass 1.5; irradiation 1,000 W/m²; cell temperature 25°C). CHAPTER FOUR 45 In this conditions, the power of the panel is called peak power and is expressed in peak watts (Wp). This characteristics are modified according the irradiation on the panel. The Open Circuit Voltage, Vel,OC (V), is the voltage produced by the panel when there is no charges connected. It is affected by the temperature which is affected by the irradiation, as shown in the following relation dV el ,OC , panel dT =−0.0023⋅NS , cell [V/°C] (4.4) where NSeries,cell = number of cell in series connection The Short Circuit Current , Iel,SC (A), is also proportional to the irradiation and is given like Iel , SC , panel=Iel , SC ,1000W/m2 ⋅Gpanel 1000 [A] (4.5) where Iel,SC,(1000 W/m2) = Short Circuit Current when the panel receives 1000 W/m2 (see table 4.2) To characterize the cell it is also needed to know its Form Factor, FF , which is a measure of the rectangularity of the Vel,OC – Iel,SC curve. FF =Iel , MPP , panel ⋅Vel , MPP , panel Iel ,SC , panel ⋅Vel ,OC , panel [dimensionless] (4.6) where Iel,MPP,panel and Vel,MPP,panel are given in table 4.4 The bigger is this factor, the nearer are the two curves shown in figure 4.2 and bigger is the quality of the cell. It is now possible to know the power generated by the panel and its efficiency as P panel = FF . Vel,OC,panel .Iel,SC,panel [W] (4.7) panel =Ppanel Gpanel ⋅Apanel (4.8) CHAPTER FOUR 46 Figure 4.2 - Open Circuit voltage VOC – Short Circuit current ISC On the other hand, the energy produced by the photovoltaic panels installation will be EP , panel =Ppanel ⋅t⋅Npanel [ J ] (4.9) where Ppanel = Power given by one panel (W) Npanel = number of panels 4.1.4. Batteries The mathematical procedure here explained to size the batteries installation is an extract from reference [10]. 4.1.4.1. Autonomy Days This parameter ( Nday ) sets the number of days in which the energy stored in the batteries is able to provide all the energy consumed by the installation. In cloudy regions it is desired until 10 days of autonomy [10]. The region of Baleares enjoy a very sunny wetter almost all the year. According the climatic dates of 2005 [2], the longest period with the minimum of solar radiation is two days (40 hours). 4.1.4.2. Depth of discharge (DOD) A full discharge of the batteries could damage its storage capacity and reduce its operating life. Therefore it is defined the parameter depth of discharge , as the percentage of the stored energy that the battery is able to provide. According to the use of this installation, the depth of discharge is considered like 80% in relation with the nominal capacity of the battery. This is the typical value for Pb batteries with a long ratio of discharge used in photovoltaic applications [10]. VMPP , IMPP CHAPTER FOUR 47 That means that the battery will not be able to give the 100% of the kept energy but only the 80%. 4.1.4.3. Accumulated energy The energy provided by the accumulation system, Ebatt is defined as Ebatt=ET , photo ⋅Nday photo ⋅DOD [ J ] (4.10) where ηphoto = global efficiency factor of the installation. photo=regulator⋅1−kbatt−kconvert −kv⋅1−ka⋅Nday DOD  [dimensionless] (4.11) where ηregulator = efficiency of the charge controller (or regulator), given by the manufacturer. ka = daily self-discharge coefficient, normally defined by the manufacturer 0.002 days → batteries with low self-discharge, Ni-Cd or Pb-Cd, without maintenance. 0.005 days → stationary batteries Pb (normally used in solar installations) 0.012 days → high self-discharge batteries (automobiles) kbatt = loss factor due to the efficiency of the batteries. In absence of more information, it is taken 0.05 for this factor kconvert = loss factor in DC/AC converter, normally defined by the manufacturer. kv = this factor groups another losses (efficiency of the Net, Joule losses...). Reference values are set between 0.05 and 0.15. 4.1.4.4. Capacity of batteries Cbatt=Ebatt 3600⋅Vel ,batt [A.h] (4.12) where Vel,batt = working voltage of the batteries [V] 4.1.5. Charge controller The function of the charge controller is to drive the energy that comes from the panels into the batteries or into the inverter to be consumed, according to necessity. It regulates the voltage and the current according to the state of charge of the battery. Its objective is also to ensure that the battery will be charged without suffering dangerous overloads. The charge controller will also protect the batteries against excessive discharges. CHAPTER FOUR 48 The charge controller is chosen among the current offer by taking in consideration the characteristics of the installation, the working voltage of the batteries and the maximum operating current. The operating current is given as the product of the operating current of one panel for the number of panels connected in parallel, NPanel,parallel . Iel,regulator = Iel,MPP . Npanel, parallel [A] (4.13) 4.1.6. DC/AC Inverter The function of this equipments is to convert the direct current (DC), from the photovoltaic panels or the batteries into alternating current, needed for most of electrical appliances. The election of the inverter depends on the maximum of power required by the installation. The smallest inverter able to meet this power will be chosen because the efficiency of this kind of equipments decrease quickly for lower working loads. 4.2. Hot sanitary water installation 4.2.1. Introduction The hot sanitary water (HSW) installation should supply hot sanitary water for domestic applications. The main elements of this kind of installation are shown in figure 4.3. According to the Spanish recent legislation [4], all new buildings must to cover a percentage of its consumption of HSW by means of a solar installation. The value of this percentage depends on the climatic zone where the installation is located and the used system of auxiliary heating. The tables 4.5 and 4.6 are an extract of [4], (section HE 4). Figure 4.3 – Elements of a hot sanitary water Installation CHAPTER FOUR 49 Consumption of HSW (liters/day) Climatic zone I II III IV V 50 – 5000 30 30 50 60 70 5000 – 6000 30 30 55 65 70 6000 – 7000 30 35 61 70 70 7000 – 8000 30 45 63 70 70 Table 4.5 - Minimal solar contribution (%) – General case Consumption of HSW (liters/day) Climatic zone I II III IV V 50 – 5000 50 60 70 70 70 5000 – 6000 50 63 70 70 70 6000 – 7000 50 66 70 70 70 7000 – 8000 51 69 70 70 70 Table 4.6 - Minimal solar contribution (%) – Auxiliary heating with Joule's effect 4.2.2. Design Conditions The installation is located in Soller (Mallorca). It is planned for a domestic use for 4 persons. Table 3.4 (see section 3.1.3 of the present project), showed the needed flow of hot sanitary water, ˙ VHSW (liters/day.person), for each application of the building. According to [4] the temperature of storage will be 60 °C If the installation is designed with a different storage temperature, Tacc , the required flow, ˙ VHSW Tacc  must be modified, every month, using the equation (3.3) The daily energy needed to increase the temperature of water from the temperature of the net to the storage temperature is given as following QHSW=˙ Vw ⋅w ⋅cp ,w ⋅NPersons ⋅Tacc−Tw [ J/day] (4.14) where ˙ VHSW = Flow of Hot Sanitary Water (l/s) ρ W = density of water (kg/l) NPersons = number of persons Tacc = Temperature of storage in the accumulator (°C) TW = Temperature of water from the public net (ºC) It is evident that it will be related with the temperature of water in public net. CHAPTER FOUR 50 4.2.3. Thermal Collectors The thermal collector receives the energy from the sun and converts it into thermal energy by means of a thermal fluid (water with antifreeze). The chosen collector is the SolvisCala C-253-I. The most important properties are shown in the table 4.7. For more details, see Appendix D Magnitude Measurement Units Dimensions 2170 x 1168 x 93 mm Absorber area 2.378 m2 Gross area 2.535 m2 Solar absortance 95 % Stagnation temperature 209 ºC Maximum pressure 4 bar Table 4.7 – Properties of solar collector. The energy that arrives to the collector, Gcollector , is given by the equation (3.4), for the same inclination and orientation of the roof. But not all this energy takes advantage on the collector. The real energy that arrives to the installation depends on the efficiency of the collector. The efficiency of the collector is given by the manufacturer by means of experimental test in laboratories. The mathematical expression for the efficiency is given in Appendix D like collector=0−a1 ⋅Tm ,collector−Tamb Gcollector −a2 ⋅Tm , collector−Tamb2 Gcollector (4.15) where η0 = optic factor = 0.798 a1 = first order loss coefficient = 3.42 (W/m2.K) a2 = second order loss coefficient =0.016 (W/m2.K) Tamb = Temperature of the air (ºC) Tm,collector = Medium temperature in the collector (°C) Gcollector = Irradiance who arrives to the collector (W/m2 ) Tm ,collector =Tout ,collectorTin , collector 2 [ºC] (4.16) A solar collector works very similarly to a heat exchanger in which the primary circuit is the solar radiation whereas the secondary is the circuit across the collector. To calculate the efficiency of the collector every instant of time it is also needed a thermal balance between CHAPTER FOUR 51 the two circuits. See [15] for more information about the efficiency of thermal collectors. QP ,collector=collector⋅QS , collector ˙ mw ⋅cp , w ⋅Tout−Tin=collector ⋅Gcollector⋅Ncollector⋅Acollector (4.17) where QP,collector = energy produced by the collector QS,collector = solar energy arriving at the collector ˙mwater = mass flow of heat transfer fluid (kg/s) cP,water = specific heat of heat transfer fluid (J/kg.°C) Tout , collector = output temperature of the collector (°C) Tin , collector = intput temperature of the collector (°C) Gcollector = irradiance that arrives to the collector (W/m2 ) NCollector = number of collectors ACollector = surface of each collector (m2) ηcollector = efficiency of the collector 4.2.4. Storage Tank The sizing of the storage tank or accumulator is a decisive factor in the designing of the solar installation. It depends basically on three factors –Surface of the collectors –Working temperature. –Gap of time between the production and the consumption of the HSW. The storage tank must agree with the current legislation [4]. This one set the next relation between the volume of storage and the surface of the collectors: 50Vacc Acollector 180 (4.18) where Vacc = volume of the storage tank (liters) Acollector = surface of the collectors (m2 ) With this criterion the storage tank will be chosen among the current offer of the manufacturers. Some authors [10], set the next orientations to chose a correct volume of storage according to the gap of time between the production and the consumption: 1) Coincidence between the caption and the consumption. The specific volume of the accumulator will be from 35 to 50 liters/m2 of collector. CHAPTER FOUR 58 4.3.6. Dissipater The steam leaving the adsorption chamber is driven into the condenser, where will transfer the liquefaction heat into the environment. The dissipater is provided of two ventilators and a fresh water atomizer, which will enhance the energy dissipation. The minimal theoretic reachable temperature would be the wet-bulb temperature Figure 4.9 shows a dissipater from Solvis. Figure 4.9 – Dissipater. Source: SOLVIS CHAPTER FIVE 59 5. INSTALLATION SIZING In this chapter the design of installations which will provide hot sanitary water, electricity for appliances and energy for heating and air conditioning is made taking into account what has previously been stated in relation with solar installations. Basically two cases are going to be studied: In the first one warm water will be produced by thermal collectors. Heat and cooling for heating and air conditioning respectively will be provided by a reversible heat pump. Electricity to feed the heat pump will be produced by a photovoltaic generator. Heating (or cooling) distribution inside the rooms is made by means of fan coils. In the second case, the study of viability for the absorption machine SolvisCool 08 providing air conditioning will be made in order to compare it with the heat pump solution. The solar collectors will provide hot water in summer to feed the adsorption machine as well as hot sanitary water. Heating distribution in winter is made by means of hot water coming directly from thermal collectors to fan coils. The adsorption machine is not used in winter. The thermal collectors installation will provide hot sanitary water as well. As established in chapter 4, the variations during a day in electric consumption for appliances or in hot water consumption are not known. It is either not possible to know the variations in electrical consumptions between summer and winter. In summer, the number of sunny hours is higher and the use of lighting inside the building decrease respect its value in winter. Likewise, it is possible to think that the required temperature of hot water is smaller in summer than in winter. Nevertheless, it is only possible to suppose the consumption in one day according to the obtained information and extend this value for all the year. This fact doesn't take place in the load calculation of air conditioning because it is direct related with the climatic information likewise the energy produced by the installation (see also chapter 4). Therefore, they are hourly known during all the year. That means that there is a great difference between the precision in the energy requirements and the energy CHAPTER FIVE 60 production which must be accepted in this work. 5.1. CASE 1: HEAT PUMP INSTALLATION: AIR CONDITIONING AND HEATING THERMAL COLLECTORS INSTALLATION: HOT SANITARY WATER The main resource of energy should be the solar radiations. Heat pump for heating and air conditioning likewise the electrical appliances will be fed by photovoltaic panels. On the other hand, the thermal collectors will provide warm water. In cases where the solar radiation is not enough to feed the installation, the lack of energy will be taken from the electric grid. The photovoltaic panels and the thermal collectors will be placed on the roof. The surface of the roof is 45 m2 and it is all on principle usable. A scheme of the installation is shown in figure 5.1. 5.1.1. Design Conditions for the heat pump installation The starting point for this section is the evolution on power consumption for heating and air-conditioning and the variations of the temperature inside the building. They were shown in figures 3.2 and 3.3 respectively. On the other hand, the energy needed for the electrical appliances, set in chapter 3.1.2. is also considered. The addition of the two variables gives the variation of theoretic electrical consumed energy by the building during all the year called ET ET,photo = EAppliances + EHeatPump [ J ] (5.1) where Eappliances = Energy consumed by the electrical appliances (calculated on chapter 3) [ J ] EheatPump = Energy consumed by the heat pump (calculated in chapter 5.2.2) [ J ] The energy produced by the installation is affected by the efficiency of the regulator, the efficiency of the inverter and the looses by keeping energy in the batteries. Therefore, the energy consumed by the building, coming from the photovoltaic installation, is given like Ephoto=ET , photo photo [ J ] (5.2) where ηphoto = global efficiency of the photovoltaic installation. CHAPTER FIVE 61 Figure 5.1 – Photovoltaic and HSW installation. Case 1 5.1.2. Selection of Equipments 5.1.2.1. photovoltaic panels. The chosen panels for this installation are the SolvisPico PI-AE/210 Wp, whose the characteristics were shown in tables 4.1 , 4.2, 4.3 and 4.4. (see chapter 4 and Appendix D). 24 photovoltaic panels are going to be placed on the roof in series of 4. To get the maximum profit of the available surface of the roof, a total of 24 panels will be installed on the roof. The covered surface is: Covered Surface = Surface of one panel ( Apanel ) x number of panels ( Npanel ) 1.65 x 24 = 39.6 m2 The rest of the surface will be used to place the thermal collectors. CHAPTER FIVE 62 The inclination (δ) and orientation (θ) of the panels will be the same as the roof. In that case there will be no shadow projected from one panel to the other. δpanel = 12.41° θpanel = 0° The energy which arrives to the panels, ES,panel [ J ], coming from the solar radiation is given as ES , panel =Npanel ⋅Gpanel ⋅t [ J ] (5.5) where Npanel = number of panels Gpanel = solar irradiance over the panel (W/m2), given by the equation 3.4 The energy produced by the panels will be EP , panel =Ppanel ⋅t⋅Npanel [ J ] (5.6) where Ppanel = Power given by one panel (or module) (W), given by equation 4.5 Npanel = number of panels In Appendix C is shown the arrangement of the panels on the roof. 5.1.2.2. charge controller The charge controller or regulator will be chosen according the short circuit current in the panels field. There is 4 panels in series, each one with ISC = 8.30 A (see Appendix D). The evolution of the maximal power raised in field panels every day is shown in figure 5.2. In this installation 6 charge controllers Tarom 235 are going to be connected in parallel, each one with 35 A maximal working current. The efficiency of each one is >95 % See Appendix D for more information about the charge controller. CHAPTER FIVE 63 Figure 5.2 – Maximal Power produced by the photovoltaic panels field 5.1.2.3. Batteries Figure 5.3 shows the evolution during a year of the energy that the batteries should accumulate, Ebatt (J) , in order to supply completely the necessities of the building, and the energy really produced by the photovoltaic installation, EP,photo (J). The capacity of the batteries will not be higher than the energy which the installation is able to produce in one day. In summer the solar production raise the maximum of energy, and the most of this energy is consumed during the solar hours. Therefore, the capacity of the batteries will be calculated with the equation 4.12, for Ebatt equal to the maximal difference between the produced and the consumed energy, Ebatt = 0.4 108 [ J ]. C=Ebatt 3600⋅Vbatt = 0.53⋅108J 3600 s h⋅12V = 926 [Ah] This capacity will be provided for a pack of four batteries Monoblock Power 12 V, 250 Ah , connected in parallel in groups of two, with a capacity of 250 Ah each one. The deep of discharge, DOD, is 80 % for this kind of battery. See also the characteristics of the product in Appendix D. 0 5 0 1 0 0 1 5 0 2 0 0 2 5 0 3 0 0 3 5 0 4 0 0 0 5 0 0 1 0 0 0 1 5 0 0 2 0 0 0 2 5 0 0 3 0 0 0 3 5 0 0 4 0 0 0 4 5 0 0 D a y o f t h e y e a r P o w e r ( W a t t ) CHAPTER FIVE 64 Figure 5.3 – Stored energy and Produced energy 5.1.2.4. DC/AC Inverter The DC/AC inverter is chosen is chosen according to the maximal power consumption of a day. Figure 5.4 shows the maximal power consumed by the installation every day including the auxiliary energy for Hot sanitary water. The chosen inverter is therefore Inversor Senoidal Solener ISC 4000 24V , (see also the characteristics of the product in Appendix D), with a working power of 4000 W and the possibility to increase it during short intervals of time. Figure 5.4 – Maximal values of required power 0 5 0 1 0 0 1 5 0 2 0 0 2 5 0 3 0 0 3 5 0 4 0 0 2000 2500 3000 3500 4000 4500 D a y o f t h e y e a r P o w e r ( W a t t) 0 1 0 0 2 0 0 3 0 0 4 0 0 0 5 0 100 150 200 250 300 350 D a y o f t h e y e a r E n e r g y ( M J ) E a c c E P , p a n e l CHAPTER FIVE 65 5.1.2.5. Heat pump In chapter 3 where calculated the maximal consumption of energy needed to maintain a constant temperature inside the building. From this data it is possible to chose a heat pump from a manufacturer catalogue. The chosen equipment is the heat pump SAP – CMRV 2446 EH, which characteristics are shown in table 5.2. (see also Appendix D for more information). Table 5.2 – Technical Characteristics of the heat pump The electrical consumption of heat pump, EHeatPump , will be Eheatpump=PHeatPump ⋅t COP [ J ] (5.3) where COP = Coefficient of performance (given by the manufacturer) PHeatPump = working power of the heat pump The spin of the compressor of the heat pump is adjusted to provide the energy needed each moment. In that case it is possible to receive from the heat pump the energy qH calculated on chapter 3. In that case, the energy consumed by the heat pump will be Eheatpump=˙ QH⋅t COP [ J ] (5.4) where ˙ QH≤PHeatPump On the other hand, three internal units (fan-coil) are chosen to distribute the energy for heating or air conditioning in the three main rooms of the house. The characteristic of fancoils are given in table 5.3. (see more details in Appendix D). CHAPTER FIVE 66 Table 5.3 – Characteristic of fan coils The chosen units are 2 x SAP-KMRV76EH for the sleeping rooms. And 1 x SAP-KMRV96EH for the main room. This combination shows a good correspondence between the operating power of the heat pump and the operating power of the three elements together, for summer and for winter. 5.1.3. Results of the Simulation for the heat pump. In figure 5.5 are represented the electrical energy needed by the building, Ephoto ( MJ ) , the solar radiative energy which arrives to the installation, QS,panel ( MJ ) , and the electrical energy produced by the photovoltaic installation, EP,panel ( MJ ) every day through all the year. It is interesting to observe that the net energy which arrives at the installation is much higher than the electrical energy demand of all the building almost during all the year. But due to the short efficiency of the photovoltaic panels not all this energy is available. The difference between Ephoto and EP,panel is the auxiliary energy Eaux, panel that the installation must to take from the grid. Figure 5.6 represents Ephoto ( MJ ) , EP , panel ( MJ ) and Eaux , panel (MJ ). The solar radiative energy which arrives at the photovoltaic panels field is not any more represented in the figure. Figure 5.5 - Energy received – Energy produced – Energy consumed 0 1 0 0 2 0 0 3 0 0 4 0 0 0 200 400 600 800 1 0 0 0 1 2 0 0 D a y o f t h e y e a r E n e r g y ( M J ) E p h o t o , d a y E P , p a n e l, d a y E S , p a n e l, d a y CHAPTER FIVE 67 Figure 5.6 - Auxiliary energy – Energy produced – Energy consumed As observed, in summer, from day 140 to day 196, auxiliary energy consumption is needed only in shorts periods of time or not needed at all. It is also interesting to study the relationship between the two curves, Ephoto and EP , panel , to obtain the fraction of energy, Fphoto (%), which describes the coverage of the photovoltaic installation of the whole year Fphoto=100⋅ ∑ i=1 365 EP , panel ∑ i=1 365 Ephoto [%] (5.7) where Ephoto = Electrical energy required by the building in one day [ J ] EP,panel = Electrical energy produced by the photovoltaic installation [ J ] in one day. If the equation (5.7) is applied for all the year (i=365) the fraction of covered energy with the solar installation results. Fphoto , year = 40.34 % In figure 5.7 are showed the values of Fphoto for each day and for each month. 0 1 0 0 2 0 0 3 0 0 4 0 0 0 5 0 1 0 0 1 5 0 2 0 0 2 5 0 3 0 0 D a y o f t h e y e a r E n e r g y ( M J ) E P , p a n e l, d a y E p h o t o , d a y E a u x , p a n e l, d a y CHAPTER FIVE 74 chosen to be the design temperature of storage. The loads for heating and air conditioning are calculated from the estimation of loads made in chapter 3. In this case, the energy supply for air conditioning will be made from the adsorption machine. But the energy supply for heating will be made directly from stored hot water into the fan-coils. Therefore the loads for heating and for air conditioning are going to be treated separately. Qheating = ˙ QH . ∆t if ˙ QH > 0 (5.13) Qcooling = ˙ QH . ∆t if ˙ QH < 0 (5.14) where ˙ QH = needed power (W) to meet the design temperature , calculated in chapter 3. 5.2.1.2. Hot sanitary water The values of flows estimated in chapter 5.3.1 for domestic hot water were given for a 60 °C storage temperature. The new temperature of storage is 75 °C for the adsorption installation. Therefore those values must be modified as seen in equation (3.3), and according to the temperature of water in public net in Mallorca, given in table 5.4. The needed flow of hot sanitary water every month is shown in table 5.5 Month January February March April May June July August Sept Oct Nov Dec Year l/pax.day 23,3 23,2 23 22,7 22,6 22,5 22,4 22,5 22,6 22,7 23 23,3 22,8 Table 5.5. Flow design (litters/day) of Hot sanitary water every month The value of ˙ VHSW = 23 l/person.day is chosen for this application during all the year. The power to provide hot sanitary water, according to explained in chapter 4.2.2 is given in MJ/month in table 5.6. January February March April May June July August Sept Oct Nov Dec 809.93 717.48 763.21 708.44 716.48 678.29 685.33 700.9 693.37 732.06 738.59 809.93 Table 5.6 - Energy requirements (MJ) for HSW every month 5.2.1.3. Appliances Power for electrical appliances is not taken in consideration in this chapter since it will be provided directly from the electrical grid. It will be included in chapter 6 for making a comparison with the case 1. The energy consumed by the installation will be CHAPTER FIVE 75 Qads = Qheating + Qcooling + QHSW (5.15) 5.2.2. Selection of equipments 5.2.2.1. Thermal Collectors The used solar collectors for this application are the SolvisCala C-253-I, whose properties are in great detail described in Appendix D. To get the maximum profit of the available surface, a total of 16 thermal collectors will be installed on the roof. The covered surface is: Covered Surface = Surface of thermal collector ( Acollector ) x number of thermal collector ( Ncollectors ) 2.378 x 16 = 38.05 m2 The collectors will be connected in series of two. This arrangement will allow a grater temperature of storage. See Appendix C for more details about the arrangement and connection of collectors. The involved equations and the method to calculate the energy generated by the thermal collectors were described in chapter 5.3.2. It is important to note that in this case, are two collectors connected in series. That means that the output temperature for the first one is the input temperature for the second one. Tin2 , ads=Tout1, ads (5.16) The used notation is the next one: QP,ads1 = thermal energy produced by one of first collectors in series in the adsorption machine installation QP,ads2 = thermal energy produced by one of second collectors in series in the adsorption machine installation QP,ads = thermal energy produced in each branch of the adsorption machine installation QP,ads = QP,ads1 + QP,ads2 [ J ] (5.17) The energy which will be stored in the accumulator,Qacc,ads , will be Qacc , ads=transfer⋅Ncollector Nseries ⋅QP, ads [ J ] (5.18) where ηtransfer = 0.8 heat transfer efficiency in accumulator Ncollector = 16 number of collectors in the installation CHAPTER FIVE 76 Nseries = 2 number of collectors connected in series The input temperature on the first collector is here also considered constant and equal to 20 ºC. The efficiency factor of collectors will not be the same. First collectors of the series have a input temperature lower than second ones. Therefore the medium temperature is lower, there is lower losses into the environment and its efficiency is greater. This effect can be better observed by examining the equations 4.15 and 4.16 about thermal collector efficiency. 1=0−a1 ⋅Tm1 , ads−Tamb  Gads −a2 ⋅Tm1 ,ads−Tamb 2 Gads → Tm1 ,ads=Tout1 ,adsTin1 , ads 2 [ºC] 2=0−a1 ⋅Tm2 ,ads−Tamb Gads −a2 ⋅Tm2, ads−Tamb2 Gads → Tm2 ,ads=Tout2 ,adsTin2 ,ads 2 [ºC] Finally, the energy produced by each collector will be also different between the first and the second one collector of the series QP ,ads1=˙ mw ⋅cpw ⋅t⋅Tout1−Tin1 [ J ] (5.18) QP ,ads2=˙ mw ⋅cpw ⋅t⋅Tout2−Tin2 [ J ] (5.19) 5.2.2.2. Accumulator Since the installation is planned to supply the heating and air conditioning necessities, the production of energy and its consumption will take place at the same time or with smaller gaps of time. Therefore, the storage volume will be ranged from 35 to 50 litters/m2 of collector surface according to the recommendations given in reference [10]. For this installation it is chosen the accumulator SolvisMax, with 950 litters capacity. 5.2.2.3. Adsorption Machine The chosen adsorption machine is the SolvisCool SC 08, whose characteristics are shown in table 5.7. See also Appendix D for more information. CHAPTER FIVE 77 Type SC 08 Maximal cooling power 11 kW COPmax 0.65 Operating cooling power 8 kW Electrical consumption 7 W Working parameters Temperature of cooling circuit 6 – 20 ºC Temperature of dissipater circuit 22 – 37 ºC Temperature of heating circuit 55 – 95 ºC Cooling power 5 – 11 kW Table 5.7 – Technical Characteristics of the adsorption machine. Source: SOLVIS 5.2.2.4. Condenser The chosen condenser is the SolvisCool RCS 08, whose main characteristics are shown in tables 5.8 and 5.9. See also Appendix D for more information. PARAMETER Unit RCS 08 Energy dissipation power kW 21 Noise level at 10 meters distance Db (A) 43 Water consumption m3 / year 20 Working flow m3 / h 3.7 Operating pressure of the atomizers bar min. 3 - 6 Table 5.8 – Working characteristics of SolvisCool RCS 08. Source: SOLVIS PARAMETER Unit RCS 08 Width mm 2000 High mm 1145 Depth mm 950 Empty Weight kg ca. 188 Table 5.9 – SolvisCool RCS 08 Dimensions. Source: SOLVIS The efficiency of the adsorption machine is strongly affected by climatic conditions around the condenser . This effect is shown in figure 5.13 provided by the manufacturer where the COP and the working power, Pcooling (dQ_NT, according the nomenclature of the CHAPTER FIVE 78 manufacturer), change with the external temperature for the two possible operating modes of the machine: ECO Mode and Power Mode. In this study it is only considered the Power Mode. Figure 5.13 – Experimental measurement in variation of efficiency in adsorption machine. Source: SOLVIS These curves have been approximated to several equations to be implemented in the simulation. The results are given in table 5.10. Power Mode 75ºC COP = -0.00145 T2amb + 0.0715 Tamb – 0.33 ECO Mode 75 ºC COP = -0.00145 T2amb + 0.0638 Tamb – 0.0435 Power Mode 75 ºC Pcooling = 23.2 – 0.53 Tamb (kW) ECO Mode 75 ºC Pcooling = 17.2 – 0.4 Tamb (kW) Table 5.10 – Mathematical approximation of efficiency curves in the adsorption machine 5.2.2.5. Expansion Tank The expansion tank is placed inside the accumulator. It is already sized by the manufacturer to agree the specifications. 5.2.2.6. Auxiliary heater It is recommended a maximum of 300 W installed power for the heater per square meter of solar collector (recommended value in reference [10]). In this installation there is 16 panels ( NCollector = 16), with a surface AC = 2.378 m2 ( properties in Appendix D ) The maximal power of heater will be. CHAPTER FIVE 79 PauxHeater,max = 300 x 16 x 2.378 = 11414 W For this application, it is imposed as design condition a working power of the heater as PauxHeater = 8000 W 5.2.3. Results of the simulation In figure 5.14 are shown: incident solar energy QS,ads , energy stored in the accumulator Qacc,ads and consumed energy for heating and air conditioning in the adsorption machine installation Qads . The consumption of appliances is not included in this graphic. Figure 5.14– Variations in energy for the adsorption machine installation As shown in figure 5.14 thermal collectors technology requires in cold months much more energy than incident energy to provide heating if compared with case 1. On the other hand, the fraction of usable solar energy is quite bigger than photovoltaic panels technology. To cite just one fact, the day 146 the thermal collectors field receives 965 MJ, that is a little bit less than the 1004 MJ received by the photovoltaic installation (see chapter 5.3.3), because the surface of panels in case 1 is bigger. The energy produced by the installation in case 2 is 484 MJ. This is a 50.2 %. This fact allows to get an overproduction in summer months. In figure 5.15 is shown the evolution of auxiliary energy needed for heating and air conditioning, as the difference between needed and produced energy. The consumption of appliances is not included in this graphic. 0 1 0 0 2 0 0 3 0 0 4 0 0 0 2 0 0 4 0 0 6 0 0 8 0 0 1 0 0 0 1 2 0 0 D a y o f th e y e a r E n e r g y ( M J ) Q a d s , d a y Q a c c , a d s , d a y Q S , a d s , d a y CHAPTER FIVE 80 Figure 5.15 – Auxiliary energy in relation with the production and the consumption. Figure 5.15 does not consider the efficiency variation effect in the adsorption machine due to external air temperature, as shown in figures 5.13 and table 5.10 during summer months. This effect is shown in figure 5.16. As shown, the available energy during the summer months, Qmachine is much greater than the consumed energy for cooling, Qcooling . Figure 5.16 – Consumed energy for air conditioning and in relation with the energy produced in the adsorption machine The fraction of energy for all the year is also calculated like the relation between the energy produced and the energy consumed during all the year. It gives 0 1 0 0 2 0 0 3 0 0 4 0 0 0 2 0 0 0 4 0 0 0 6 0 0 0 8 0 0 0 1 0 0 0 0 1 2 0 0 0 d a y o f t h e y e a r P o w e r ( W ) Q cooling,ads,day Q machine,day 0 1 0 0 2 0 0 3 0 0 4 0 0 0 2 0 0 4 0 0 6 0 0 8 0 0 1 0 0 0 1 2 0 0 d a y o f t h e y e a r E n e r g y ( M J ) Q a d s , d a y Q a c c , a d s , d a y Q a u x , a d s , d a y CHAPTER FIVE 81 Fads=100⋅ ∑ month ,day Qacc , ads ∑ month , day Qads =8.957⋅1010 J 1.638⋅1011 J⋅100 =54.67 [%] (5.20) The fraction of produced energy with the solar installation, in relation with the consumption for heating or air conditioning, is shown in figure 5.17. The consumption of appliances is not included in this graphic. Figure 5.17 – Fraction of consumed energy covered with the solar installation. If we include the consumption of electrical appliances in equation 5.20 , the value of Fads decreases: Fads=QP , ads , year QEconsumed , year ⋅100=8.957⋅1010 1.708⋅10118.147⋅109⋅100 = 50.08 % Finally, the efficiency of collectors placed on the same file is shown in figure 5.18. As explained in chapter 5.2.2.1 - Thermal collectors - note that the efficiency of first collector of the series is higher than the second one because its input temperature is lower. 0 2 4 6 8 1 0 x 1 0 4 0 1 0 0 2 0 0 3 0 0 4 0 0 5 0 0 6 0 0 7 0 0 8 0 0 9 0 0 1 0 0 0 d a y o f t h e y e a r E n e r g y f r a c t i o n ( % ) F a d s , d a y F a d s , m o n t h Hour of the year 103 CHAPTER FIVE 82 Figure 5.18 – Efficiency of thermal collectors from the same series 0 5 0 1 0 0 1 5 0 2 0 0 2 5 0 3 0 0 3 5 0 4 0 0 0 1 0 2 0 3 0 4 0 5 0 6 0 7 0 8 0 D a y o f t h e y e a r E f f i c i e n c y ( % ) F i r s t C o l le c t o r o f t h e s e r i e s S e c o n d c o ll e c t o r o f t h e s e r i e s CHAPTER SIX 83 6. COMPARATIVE STUDY FOCUSING ON CASE 1 AND CASE 2 In chapter 5 were analysed and calculated the main installation elements according to the proposed alternatives given in case 1 and case 2. The purpose of each installation is to obtain heating, air conditioning, hot sanitary water and electrical power supply from solar resources. In situations where that was not possible, the lack of energy was supply with electrical power from the net. The objective of present chapter is to make a comparative between the two alternatives considering the produced energy, the efficiency and the economical cost. Until said otherwise, the expression of energies or prices are referenced to square meter of collector surface. All the comparisons are made from case 1 to the case 2, both described in last chapter. 6.1. Criterion of energy production The energy produced in each concreted proposed installation, case 1 and case 2, will be compared. In both cases,the energy received (MJ/m2 ) by the panels or collectors, respectively, placed on the roof is always the same because the inclination and orientation of all them is the same in each case. The thermal energy produced by the installations in case 1 and case 2 is shown in figure 6.1. To obtain the curve of case 1, it is needed to consider the COP of the chosen heat pump. In this curve it is also included the thermal energy provided by the single thermal collector of the installation. The curve of case 2 is directly the representation of the thermal energy produced by the field of thermal collectors and stored in the accumulator. The represented curves are mathematically given by equations 6.1 and 6.2 CHAPTER SIX 90 cost of the installations. On the other hand, it is supposed a granted loan from a bank to cover the investment cost, with an interest, j , of 5 %. j = 5 % 6.3.2. Investment Costs Prices of equipments are shown in tables 6.2 and 6.3, for case 1 and case 2 respectively, extracted from references [30] and [31]. Units Description € / ud subtotal 24 Photov Panel SolvisPico PI – AE / 210 Wp 1470 35280 6 Regulator Tarom 235 261 522 4 Battery Monoblock Power 12V, 250 Ah 299 1196 1 Senoidal inverter Solener ISC 4000, 24 V 1430 1430 24 Panels structure 79.41 1905.84 1 heat pump SAP – CMRV 2446 EH 2200 2200 1 Fan coil SAP-KMRV96EH 415 415 2 Fan coil SAP-KMRV76EH 400 800 1 Kit Hot Sanitary Water 4 persons 3000 3000 TOTAL 47792.84 Table 6.2 – Price of equipments for case 1 Units Description € / ud subtotal 16 Thermal Collector Solvis Cala C-235-I 880 14080 16 Collector structures 150 2400 1 Accumulator SolvisMaxFutur 950 6000 6000 1 Adsorption Machine SolvisCool ACS 08 10000 10000 1 Fan coil SAP-KMRV96EH 415 415 2 Fan coil SAP-KMRV76EH 400 800 TOTAL 33695 Table 6.3 – Price of equipments for case 2 CHAPTER SIX 91 6.3.3. Total Cost The installations are planned for a 20 years life. The calculation of total cost at the end of their life must consider investment costs, operating costs and maintenance costs. It is considered that the efficiency of equipments does not decreases with the time. The cost for the year zero, B0 , is the investment cost. Operating cost for following years are given as a geometric progression of energy prices and bank interest, according to the rates estimated in chapter 6.4.1. Maintenance cost for solar installations, BM , could be ignored in this analysis. Nevertheless, the price of electrical batteries, Bbatt , will be also included in case 1 since its replacement every 8-10 years is recommended by the manufacturer. The total cost for the operating life of the installations can be calculated as B0 ⋅1j 100  20 ∑ n=1 20 [ Bop ⋅1i 100  n ] BM € (6.8) where B0 = Investment cost (€) Bop = Operating cost (€) BM=Bbatt⋅1i 100  10 (€) . Maintenance cost in 10th year (6.9) Bbatt = current cost of the batteries [€] Figures 6.8. and 6.9. show the annual payment and the total amount at the end of the installations life for case 1 and case 2 respectively. The arrows size is not done to scale. Figure 6.8 - Annual payment and total amount in 20 years in case 1 CHAPTER SIX 92 Figure 6.9 - Annual payment and total amount in 20 years in case 2 Figure 6.10 is a graphic representation of these values. As shown, the investment cost for case 2 is lower than for case 1. On the other hand, the operating cost are much greater. The reason for that can be found in the huge electrical consumption in winter months shown in figure 6.3. Figure 6.10 – comparative in operating costs for case 1 and 2 It is necessary to include the interest j in calculation of operating cost if it is planned to pay it with the loan from the bank. Equation 6.8 must be rewritten as B0 ⋅  1j 100  20 ∑ n=1 20 [ Bop ⋅  1i 100  n ⋅  1j 100  20−n ] BM € (6.10) where 0 5 10 15 20 25 0 50000 100000 150000 200000 250000 Total cost CASE 1 CASE 2 Year Euros CHAPTER SIX 93 BM=Bbatt⋅1i 100  10 ⋅1j 100  10 (€) (6.11) Figure 6.11 shows the annual payment of the installations for case 1 and case 2 respectively. Figure 6.11 – comparative in operating costs for case 1 and 2 if operating costs are included in the banking loan 0 5 10 15 20 25 0 20000 40000 60000 80000 100000 120000 140000 160000 180000 200000 Total cost CASE 1 CASE 2 Year Euros CHAPTER SEVEN 94 7. CONCLUSIONS The main objective of this study is to calculate the necessities of power, heat and warm water of a building. The used method to tackle this problem – finite differences – has proved to be appropriate for this purpose. It is relatively easy to be implemented in the simulation software MATLAB (see Appendix E), and allows a high precision in calculations. This method requires a huge number of iterations, but it is not any more a problem with current computers. The implemented code takes around 30 minutes for a whole year. A best knowledge of energy consumptions rates and loads cycles would be necessary to improve the simulation. For example, it is supposed in this study that the ventilation flow is constant during all the year. But it depends strongly from human decisions and is clearly inconstant. Likewise, the consumption in electrical power and in HSW are also supposed constants each day. The second objective of this study is the design of regenerative generator systems with solar-thermal and photovoltaic technology to provide the power, heat, cooling and warm water demanded of the building. It have been also reached in this project with proposed installations in case 1 and case2. There is however some important considerations which are commented in following chapters. 7.1. Efficiency of the Installations The proposed solar installations studied in this project present a great limitation providing energy supply in winter for the normal use of the house. Two factors contribute mainly to this fact: Irradiance in summer is about four times bigger than irradiance in winter for this latitude. CHAPTER SEVEN 95 The power demand in winter is more than two times higher than in summer. Therefore, it is very difficult with the current technology to cover 100 % of the necessities from solar resources without using a huge collectors surface. The design criterions are more restrictive in winter and therefore the installations for both cases are oversized in summer. A better design of the house could improve the use of available space by using bio climatic architecture techniques like Trombe walls or greenhouses built onto the house (see references [20] and [21] for more information about bio climatic architecture). In principle there is no problem to satisfy the energy needs in summer. However, loads in summer could be likewise reduced by using parasol elements on top of the windows at the south side or by controlling the ventilation flow during the hottest hours of the day. On the other hand, the proposed installations have another handicap, because the low tilt of panels favors the solar energy collection in summer and penalizes it in winter when the energy need is the highest. To cite just one fact, energy production in winter months would be of 28 % more if the tilt of the panels were 50º, according to the results of the simulation made in this project. The current tilt of the panels of 12.41º was chosen in accordance to architectonic and aesthetic conditions. In relation with the adsorption machine installation, the results show a very good correspondence between the solar resources and energy demand in the summer period. As a result of this simulation, the technology is appropriate as an air conditioning system with a very low operating cost and very good results in summer months. On the other hand, in this case the proposed 8 kW power machine is oversized for the energy requirements of the house as shown in figure 5.16. 7.2. Auxiliary System The need of an auxiliary power system is proven to be evident through the simulation. Only electrical energy from the electric grid has been proposed in this project as auxiliary power. Other energy resources like any combustible should be compared in subsequent studies. For example, the price of natural gas for 2010 is 0,041307 €/kWh (source: IBERDROLA [33]). This price is less than a half of the price of electricity. In case 2, the use of a thermal collectors installation for heating and air conditioning combined with an adsorption machine, allows a great number of solutions to get an auxiliary energy supply from different resources. Some different types of boilers or heaters can be placed inside the main accumulator favoring the flexibility and the safety of the energy supply. Contrarily, the use of a heat pump allows just the use of electricity from the grid as auxiliary resource. CHAPTER SEVEN 96 7.3. Economical Considerations The use of solar technologies can yield large profits if they are placed in sunny areas and correctly planned for one specific application. However, it is also evident that the investment costs can be a handicap and dissuade people from the use of this technology. It would be possible to get profit from state subsidies for this kind of installations. The Government of Baleares offers every year several incentives as shown on its web site www.caib.es, [27] On the other hand, since both proposed installations have an energy storage system ( batteries and an accumulator with capacity for 150 litters in case 1; and one accumulator with capacity for 950 litters in case 2 ), it would be possible to contract a night rate in which the day is divided in two different periods, peak period and off-peak period, according to reference [23]. The night rate would allow to charge the batteries or to “charge” the water accumulator during the off-peak period to be used in peak hours. In that case the storage capacity of the batteries in case 1 and of the water accumulator in case 2 should be higher because of the gap of time between the production and the consumption of energy. For the photovoltaic installation in case 1, the following possibility could be interesting within the framework of current Spanish law (see reference [19]). It could be possible to drive the produced electrical energy from the photovoltaic installation to the electric grid. Electricity companies are bound to buy the produced energy for 0.321967 €/kWh (price for 2010 for installations smaller than 20 kW power and placed on the roof from website www.mityc.es [29]), whereas a parallel traditional installation could provide the house with power supply for a cheaper price (see chapter 6 for energy prices). The photovoltaic installation will inject the energy into the grid independently of the use of the building and generating profits for that. Moreover, the installation of batteries wouldn't be necessary any more, reducing the investment costs. The energy requirements to inject electricity into the electric grid are set by the electricity company that manages the local grid (see reference [32]). 7.4. General conclusion From results of this project, the best solution for this application could probably come from a combination of the two proposed installations. As shown in tables 6.1 and 6.5, the thermal installation from case 2 can provide more energy and presents a better efficiency compared with case 1. Current photovoltaic panels have a poor efficiency which damage the efficiency of the whole installation. Moreover, the investment cost in case 2 are much lower than in case 1. On the other hand, the use of the heat pump in case 1 to provide heat in winter lead to very low electrical consumption and operating cost, compared with case 2. A way to take advantage of both installations could be a thermal collectors installation CHAPTER SEVEN 97 producing hot water for heating and domestic use, and a heat pump as auxiliary heater. The batteries installation would be not necessary either. The use of combustibles as auxiliary heaters and the use of a night rate would be also possible. REFERENCES 98 REFERENCES [1] Instituto Geográfico Nacional - Servidor de Imágenes y Mapas del IGN como Centro Nacional de Referencia en Ocupación de Suelo para España . April 2010 - Ministerio de Fomento, España [2] Software METEONORM version 6.0 - Handbook part II: Theory – version 6.114, 20 October 2009 [3] Richard C. Dorf, Handbook of Engineering Tables – 1st Edition, CRC Press LLC – United States, 2004. ISBN 0-8493-1587-5 [4] Norm Código Técnico de la Edificación , 28 March 2006 – Boletín oficial del Estado, España. [5] Norm Reglamento de Instalaciones Térmicas en los Edificios – 29 August 2007 – Boletín oficial del Estado, España. [6] Norm UNE EN ISO 10456, Materiales y productos para la edificación. Procedimientos para la determinación de los valores térmicos declarados y de diseño - 2001 [7] Norm UNE-EN ISO 7730 , Ergonomía del ambiente térmico - 2006 [8] Fanger, P.O., Inform CR 1742 – thermal comfort - 1998 [9] Norm UNE-EN ISO 13788, Características higrotérmicas de los elementos y componentes de edificación. Temperatura superficial interior para evitar la humedad superficial crítica y la condensación intersticial. Métodos de cálculo. (ISO 13788:2001) – 30 October 2002 [10] M. Ibañez Plan, J.R. Rossell Polo, J.I. Rosell Urrutia, Tecnología Solar . Mundi-Prensa – 1st Edition, Madrid 2004. ISBN 84-8476-199-1 [11] ANSI/ASHRAE Standard 55- Thermal Environmental Conditions for Human Occupancy - 1992 [12] Shan K. Wang, Handboock of Air Conditioning and Refrigeration – 2nd Edition, McGraw-Hill. Unite States, 1993. ISBN 0-07-068167-8 [13] Norm UNE EN 410, Vidrio para edificacion. Determinacion de las caracteristicas luminosas y solares de los acristalamientos - 1988 [14] Norm UNE EN ISO 10077-1, Cálculo del coeficiente de transmisión térmica - 2001 [15] Norm EN 12975, part 2 , Thermal solar systems and components. Solar collectors. Test methods – 4 September 2001 [16] Norm CIE DS 011.2/E:2002 Standard distribution of daylight , February 2002 [18] Katsuhiko Ogata, Ingeniería de control moderna – 3rd Edition, PRENTICE HALL PANAMERICANA, S.A. México, 1998. ISBN 0-13-227307-1 [19] Norm Real Decreto 661/2007, Regulación de la actividad de producción de energía en régimen especial , de 25 de mayo 2007 - Boletín oficial del Estado, España. [20] Iñaki Urkia, Energía Renovable Práctica – 1st Edition, Pamiela – España, 2003 [21] Edward Mazria, The Passive Solar Energy Book – 1st Edition, Rodale Press , 1979 [22] Carlos Monné Bailo, Luis Ignacion Díez Pinilla, Prácticas de Energías Renovables – 2ª Edición, Prensas universitarias de Zaragoza , 2007. ISBN 84-7733-943-4 [23] Norm ORDEN ITC/1857/2008 por la que se revisan las tarifas eléctricas a partir del 1 de julio de 2008. 2008 - 26 Juny 2008. Boletín oficial del Estado, España. [24] Jose Manuel Pinazo Ojer, E. Torrella, Comportamiento térmico de edificios en régimen variable. Obtención de las funciones de transferencia en muros de contención . II jornadas nacionales de REFERENCES 99 calefacción y climatización eléctrica. Zaragoza, España1986. Visited Websites [25] www.ign.es – Instituto Geográfico Nacional , Spain, May 2010 [26] www.ree.es – Red Eléctrica Española , Spain, October 2010 [27] www.caib.es - Govern de les Illes Balears , Spain (Baleares) August 2010 [28] www.ine.es – Instituto Nacional de Estadística , Spain, October 2010 [29] www.mityc.es – Ministerio de industria, comercio y turismo , Spain, October 2010 [30] www.solvis.de – SOLVIS GmbH & Co KG , June 2010 [31] http://www.preoc.es – Precios de edificación y obra civil , Spain, October 2010 [32] www.endesaonline.es – ENDESA , Spain, October 2010 [33] www.iberdrola.es – IBERDROLA , Spain, October 2010 0.901.10 2.00 0.901.10 1.00 1.00 Figure B.2 – South side view 0.30 0.33 2.00 0.40 0.44 2.00 0.83 0.63 Figure B.4 – West side view Figure B.3 – East side view 2.00 0.40 0.44 2.19 Figure B.5 – North side view Appendix C: Arrangement and connection of panels and collectors on the roof Figure C.1 Arrangement of photovoltaic panels and thermal collector on the roof – CASE 1 Cool water Hot water N S E W Appendix C – Arrangement of panels and collectors Hot water Cool water Figure C.2 Arrangement of thermal collectors on the roof – CASE 2 N S E W Appendix D: Technical sheets of products SolvisPico Premium DE Technische Informationen EN Technlcallnformation IT Informazionl tecniche 2 5 8 11111111111111111111111111111111111 Art. Nr.: 14611 D 10-M Technische Änderungen vorbehalten 03.10/ 14611-2e 1 Description EN 1 Description SolvisPico Premium - The Power Package This high-quality module is manufactured in Eurape and designed to deliver particularly high yields. Solvis, with its 20 years of expertise in the solar industry, has designed a perfectly-tailored system: fram the highquality module with anti-reflective glass to the snow-safe stainless steel and aluminium support structure designed using Solvis's tried and tested structural calculations and the high-efficiency Sunny Boy inverter. Fig. 4: SolvisPico Premium Quallty without compromlse The SolvisPico Premium praduct se ries consists of highquality, high-efficiency solar modules that each measure up to the highest standards of quality. The entire praduction process - fram the silicon all the way to the finished module - complies with the strictest quality contral standards. The solar ceus have been optimised to increase light absorption, even under poor üghting conditions. The high-quality modules have an innovative design that reduces shadows while improving performance. The power output tolerance of +3 % minimises mismatch losses. Envlronmentally friendly products and processes The Premium series generates reliable, environrnentally friendly power. The process of producing cells and rnodules is designed to allow for a high degree of recycling and prevent darnage to the environment. Features • Superb efficiency with apower tolerance with exclusively positive sorting • 25-year warranty at 80 % of the output power • 10-year warranty at 90 % of the output power • 10-year warranty on materials and workmanship • High max. permitted system voltage (1,000 V) • Measuring log: Each individual module is measured electrically (documentation available upon request) • Seamless quality contral • Minimum manufacturing tolerances • Simple installation • Finished cabling, fitted with MC-3 plugs. Simple Installation The superb module performance and the minimal weight allow for an efficient and economical installation. The solar cables are fitted with Me plugs and pre-connected. CE marking SolvisPico PV modules comply with the requirements of the applicable EU directives. You may request the declarations of conformity. SOLVIS SolvisPico Premium· Technische Änderungen vorbehalten 03.10·0 10-M 5 EN 2 Technical Data 2 Technical Data 2.1 SolvisPicoPremiumPI-AEj...Wp + 6 991 mm!2,5 f .. Fig. 5: SolvisPico Premium PI-AE/... Wp - Dimensions General specifications Dimensions and weight Unit All modules Surface m 2 1.65 Length mm 1,655.00 Width mm 991.00 Thickness with frame mm 43.00 Diameter of frame hole mm 6.50 Weight (approx.) kg 22.00 Cell size (square) mm 156x 156 Umitvalues Unit All modules Max. permitted system vottage V 1,000 Max. compressive loading Pa 5,400 Max. tensile loading Pa 2,400 Permitted module temperature °C -40 - +80 Characteristics All modules Number of cells 60 NOCT(·) [OC) 49.5 ± 2 Aluminium frame, colour Bright anodised Connection MC type 3 Cable length +/- [cm) 94/94 Number of bypass diodes 3 Structure of the front side (glass/foil) Solar glass/EVA Qualifications and certificates CE marking • Protection class 11 • ISPRA CEC 503/IEC 61215 for hail, temperature, wind and snow load protection • RAL quality mark Solar P1 Electrical specifications (1) (.)NOCT = 'Nominal operating cell temperature' = cell temperature with irradiation of 800 W/m 2 (ambient temperature 20°C and wind speed 1m/s). Designation Abbrevia- Unit Modules (2) SolvisPico PI-AE/ ... tion 210Wp 215Wp 220Wp 225Wp Rated output (STC) PMPP Wp 210.00 215.00 220.00 225.00 Max. deviation from PMPP - % +2.00 +2.00 +2.00 +2.00 Voltage for PMPP VMPP V 27.60 28.00 28.40 28.80 Current at PMPP IMPp A 7.60 7.70 7.80 7.80 Open circuit voltage Voe V 36.10 36.30 36.40 36.60 Short circuit current Ise A8.30 8.30 8.40 8.40 Temperature coefficient for PMPP TcPMPP %j"C -0.452 -0.452 -0.452 -0.452 Temperature coefficient for Voc TcVoc %j"C -0.340 -0.340 -0.340 -0.340 Temperature coefficient for Ise Telse %j"C 0.074 0.074 0.074 0.074 Module efficiency (STC) 11 % 12.70 13.00 13.30 13.60 Max. proteetion at serial vottage - A 15.00 15.00 15.00 15.00 Manufacturer - - REC REC REC REC (1) Theseelectrical specifications are valid under the standard test conditions (STC)(airmass 1.5; irradiation 1,000 W/m 2; cell temperature 25°C). (2) Sizesand availability: The modules are available in the sizes listed above, pending availability based on the manufacturing tolerance of the production. Make sure to enquire about the availability of different sizes before placing an order. SolvisPico Premium- Technische Änderungen vorbehalten 03.10· D 10-M SOlVIS Kit solar SolvisMini 1malij::::~~~~~~~S~O~,v~isTherm 300 ~ SolvisTherm 500 Su especlallsta en calefacclön eflclente: SOLVISGmbH & Co KG Grotrian-Steinweg-Straße 12 D-38112 Braunschweig, Germany Internet www.solvis.com Mural Súper Inverter. Bomba de Calor ................................................................................ 10 Mural Inverter. Bomba de Calor .......................................................................................... 12 Mural velocidad constante. Bomba de Calor .................................................................... 14 Equipo suelo, suelo-techo Inverter. Bomba de Calor .......................................................... 16 Equipo Cassette, inverter 60X60. Bomba de Calor ............................................................. 18 Equipo de conductos. Inverter Bomba de Calor ................................................................ 20 Equipo de conductos, velocidad constante. Bomba de Calor .......................................... 22 Unidades exteriores DC Multi-Inverter. Bomba de Calor ..................................................... 24 Unidades interiores DC Multi-Inverter. Bomba de Calor ...................................................... 26 Dimensiones interiores DC Multi-Inverter. Bomba de Calor ................................................. 28 Tablas de combinaciones ..............................................................................................30 Índice de contenidos 24 Doméstico Distancias frigoríficas Rango de funcionamiento Secciones eléctricas Conexionado eléctrico Características generales Rango de potencia de 4,0 kW a 10 kW Unidad Exterior SAP-CMRV1426EH SAP-CMRV1926EH SAP-CMRV1936EH SAP-CMRV2446EH SAP-CMRV3146EH SAP-CMRV3656EH Función Frío Calor Frío Calor Frío Calor Frío Calor Frío Calor Frío Calor Nº de Uds. Interiores 2 2 3 4 4 5 Capacidad kW 2,0/4,0/5,0 2,2/4,5/5,5 2,1/5,6/6,8 2,4/7,3/8,4 2,9/5,6/6,8 3,4/7,3/8,4 2,9/6,8/8,1 3,4/8,6/9,0 2,9/8,0/9,2 3,4/9,4/9,8 1,6/10,0/11,5 1,6/12,0/14,5 Consumo W 925 925 1.695 1.735 1.550 1.735 2.000 2.000 1.805 2.040 2.860 2.860 E.E.R/C.O.P. W/W 4,32 4,86 3,30 4,21 3,61 4,21 3,40 4,30 4,62 4,61 3,50 4,20 Clase energética A A A A A A A A A A A A Intensidad Nominal A 4,10 4,10 7,52 7,70 6,88 7,70 8,87 8,87 7,58 8,96 12,6 12,6 Nivel Sonoro dB-A 47 48 46 47 46 47 47 49 48 49 53/57(modositec) Conexión Líq/Gas mm(p) 2x 6,4(1/4)/2x 9,5(3/8) 2x 6,4(1/4)/2x 9,5(3/8) 3x 6,4(1/4)/3x 9,5(3/8) 4x6,4(1/4)/3x9,5(3/8)/12,7(1/2) 4x6,4(1/4)/2x9,5(3/8)/2x12,7(1/2) 5x6,35(1/4)/3x9,52(3/8)/2x12,7(1/2) Long. de tubería TOTAL m 30 45 45 60 70 80 Long. de tubería Ud. Int m 20 25 25 25 30 30 Elevación m 15 15 15 15 15 15 Precarga válida para m 30 45 45 45* 45** 45 Dimensiones AlxAxP m 569x790x285 740x900x320 740x900x320 740x900x320 890x900x320 910x940x340 Peso neto kg 42 65 65 65 82 97 Fuente de alimentación V, F, Hz 230, 1+N, 50 Condiciones nominales Refrigeración: Temperatura aire interior 27°C DB/19°C WB; Temperatura aire exterior 35°C DB / 24°C WB Calefacción: Temperatura aire interior 20°C DB; Temperatura aire exterior 7°C DB / 6°C WB Especificaciones sujetas a cambios sin previo aviso SAP-CMRV1426EH · SAP-CMRV1926EH · SAP-CMRV1936EH SAP-CMRV2446EH · SAP-CMRV3146EH · SAP-CMRV3656EH Notas: Al menos dos o más unidades interiores deben conectarse a la unidad exterior multi Conexión (5/8) para unidad de potencia 7 kw con rosca adaptable (1/2) * Para llegar a los 60m. habrá que añadir 20 gr/m adicional. ** Para llegar a los 70m. habrá que añadir 20 gr/m adicional. *** Para llegar a los 90m. habrá que añadir 20 gr/m adicional. Exterior 43ºCDB Interior 32ºCDB 19ºCDB Exterior 18ºCDB -15ºCWB Interior 27ºCDB 16ºCDB Refrigeración Calefacción -5ºCDB Protección Modelo Unidades Sección A Sección B Sección C de línea SAP-CMRV1426EH 2,5 mm2 1,0 mm2 1,0 mm2 16 A SAP-CMRV1926EH 4,0 mm2 1,0 mm2 1,0 mm2 20 A SAP-CMRV1936EH 4,0 mm2 1,0 mm2 1,0 mm2 20 A SAP-CMRV2446EH 4,0 mm2 1,0 mm2 1,0 mm2 20 A SAP-CMRV3146EH 4,0 mm2 1,0 mm2 1,0 mm2 20 A SAP-CMRV3656EH 4,0 mm2 1,0 mm2 1,0 mm2 20 A * Secciones calculadas para aproximadamente 30 m. de distancia. * Para otras distancias, por favor rogamos consulten al departamento técnico. Flexi Multi (2x1, 3x1, 4x1, 5x1) Inverter Bomba de calor Unidad interior (1) Unidad interior (4) Unidad interior (3) Unidad interior (2) Unidad interior (5) Longitud de tubos (L1) L2 L3 L4 H2 H3 H4 Unidad exterior Diferencia de elevación (H1) Longitud máxima Longitud máxima total de los tubos en el envío Límite de longitud total de los tubos Límite de diferencia de elevación (H1, H2, H3, H4) (m) de tubos por cada unidad interior (m) Modelo (L1+L2) o (L1+L2+L3 o (L1+L2+L3+L4) (m) (L1+L2) o (L1+L2+L3 o (L1+L2+L3+L4) (m) 51)2L+1L( 03)2L+1L( 03026241VRMC 51)2L+1L( 54)2L+1L( 54526291VRMC 51)3L+2L+1L( 54)3L+2L+1L( 54526391VRMC 51)4L+3L+2L+1L( 06)4L+3L+2L+1L( 54526442VRMC 51)4L+3L+2L+1L( 07)4L+3L+2L+1L( 54036413VRMC CMRV3656 30 45(L1+L2+L3+L4+L5) 80(L1+L2+L3+L4+L5) 15 -10ºCDB modelo 3656 nuevo 25 SAP 293 608 136 12 35 369 345 320 ID:18 5-ID:23.6 58009 890 18 295 58806 07097 46 336 310 285 4-ID:23.6 ID:18 2-ID:12 569 15 293 608 136 12 58009 35 369 345 320 ID:18 5-ID:23.6 740 18 293 608 136 12 35 369 345 320 ID:18 5-ID:23.6 58009 740 18 293 608 136 12 35 369 345 320 ID:18 5-ID:23.6 58009 740 18 SAP-CMRV..EH Precios Modelo Frío(kW) Calor(kW) Precio (€) SAP-CMRV1426EH 4,0 4,5 1.250 € SAP-CMRV1926EH 5,6 7,3 1.500 € SAP-CMRV1936EH 5,6 7,3 1.650 € SAP-CMRV2446EH 6,8 8,6 2.200 € SAP-CMRV3146EH 8,0 9,4 2.970 € SAP-CMRV3656EH 10 12 3.800 € Dimensiones Control remoto • Datos técnicos y precios de unidades interiores en la página siguiente * Suministraremos unidades de la serie 4 publicada en nuestra tarifa de precios Ref. 0801 hasta finalización de existencias. CMRV1426EH CMRV1926EH CMRV1936EH CMRV3656EHCMRV3146EHCMRV2446EH * Los precios arriba indicados no incluyen IVA. 293 608 136 12 35 369 345 320 ID:18 5-ID:23.6 58009 890 18 295 58806 07097 46 336 310 285 4-ID:23.6 ID:18 2-ID:12 569 15 293 608 136 12 58009 35 369 345 320 ID:18 5-ID:23.6 740 18 293 608 136 12 35 369 345 320 ID:18 5-ID:23.6 58009 740 18 293 608 136 12 35 369 345 320 ID:18 5-ID:23.6 58009 740 18 293 608 136 12 35 369 345 320 ID:18 5-ID:23.6 58009 890 18 295 58806 07097 46 336 310 285 4-ID:23.6 ID:18 2-ID:12 569 15 293 608 136 12 58009 35 369 345 320 ID:18 5-ID:23.6 740 18 293 608 136 12 35 369 345 320 ID:18 5-ID:23.6 58009 740 18 293 608 136 12 35 369 345 320 ID:18 5-ID:23.6 58009 740 18 26 Doméstico SAP-KRV96EHDS SAP-KRV126EHDS Frío Calor Frío Calor 2,65 3,6 3,5 4,8 480 500 510 560 22/28/35/41 22/28/35/41 22/28/35/42 22/28/35/42 6.35(1/4) / 9.5(3/8) 1/4 3/8 265x789x180 265x789x180 9,5 9,5 230, 1+N, 50 Unidades interiores Rango de potencia de 2,2 kW a 7,1 kW Unidad Mural SAP-KMRV76EH SAP-KMRV96EH SAP-KMRV126EH SAP-KRV186EH SAP-KRV246EH Función Frío Calor Frío Calor Frío Calor Frío Calor Frío Calor Capacidad kW 2.2 2.5 2.65 3.6 3.5 4.2 5,15 6,0 7,1 8,5 Circulación de aire (A) m3/h 440 480 460 480 480 500 840 880 890 930 Nivel de presión de sonido (Silencioso/B/M/A) dB-A 23/27/30/33 23/27/30/33 22/30/35/38 22/30/35/38 25/29/33/36 25/29/31/34 28/34/38/41 28/34/37/40 30/38/41/44 30/37/40/43 Diam. de Tubos Estr./Ancho mm 6.35(1/4) / 9.5(3/8) 6.35(1/4) / 9.52(3/8) 6.35(1/4) / 9.52(3/8) (1/4) (1/2) (1/4) (1/8) Dimensiones AlxAxP m 285x825x213 285x825x213 285x825x213 298x1065x234 298x1065x234 Peso neto kg 10 10 10 12 12 Fuente de alimentación V, F, Hz 230, 1+N, 50 SAP-KMRV..EH · SAP-FTRV..EH SAP-XMRV..EH · SAP-UMRV..EH Condiciones nominales Refrigeración: Temperatura aire interior 27°C DB/19°C WB; Temperatura aire exterior 35°C DB / 24°C WB Calefacción: Temperatura aire interior 20°C DB; Temperatura aire exterior 7°C DB / 6°C WB Especificaciones sujetas a cambios sin previo aviso Unidad Suelo y Suelo/Techo SAP-FMRV94EH SAP-FTMRV124EH SAP-FTRV184EH SAP-FTRV244EH Función Frío Calor Frío Calor Frío Calor Frío Calor Capacidad kW 2,65 3,6 3,5 4,2 5,15 6,0 7,1 8,5 Circulación de aire (A) m3/h 425 700 720 900 Nivel de presión de sonido (B/M/A) dB-A 31/37/40 35/40/44 36/41/45 41/44/47 Diam. de Tubos Estr./Ancho mm 6.35(1/4)/9.52(3/8) 6.35(1/4)/9.52(3/8) 6.35(1/4)/12.7(1/2) 6.35(1/4)/15.88(5/8) Dimensiones AlxAxP m 700x560x200 680x900x190 680x900x190 680x900x190 Peso neto kg 18.6 23.5 23.5 23.5 Fuente de alimentación V, F, Hz 230, 1+N, 50 Unidad Tipo Cassette de 4 vías SAP-XMRV94EH SAP-XMRV124EH SAP-XRV186EH Función Frío Calor Frío Calor Frío Calor Capacidad kW 2,65 3,6 3,5 4,2 5,15 6,0 Circulación de aire (A) m3/h 700 700 790 Nivel de presión de sonido (B/M/A) dB-A 37/40/44 37/40/44 35/38/43 Diam. de Tubos Estr./Ancho mm 6.35(1/4)/9.52(3/8) 6.35(1/4)/9.52(3/8) 6.35(1/4)/12.7(1/2) Dimensiones AlxAxP - Panel m 64x730x730 64x730x730 64x730x730 Dimensiones AlxAxP - Unidad m 296x575x575 296x575x575 296x575x575 Peso neto - Panel kg 16.5 16.5 16.5 Peso neto - Unidad kg 2.5 2.5 2.5 Fuente de alimentación V, F, Hz 230, 1+N, 50 Unidad de Conductos ocultos SAP-URV96EH SAP-URV126EH SAP-URV186EH SAP-URV246EH Función Frío Calor Frío Calor Frío Calor Frío Calor Capacidad kW 2,65 3,6 3,5 4,2 5,15 6,0 7,1 8,5 Circulación de aire (A) m3/h 620 620 865 985 Presión estática ext. (estándar/impulsor) Pa 49/69 49/69 49/69 49/69 Nivel de presión de sonido (B/M/A) dB-A 38/41/43 33/41/43 35/42/46 39/43/46 Diam. de Tubos Estr./Ancho mm 6.35(1/4)/9.52(3/8) 6.35(1/4)/9.52(3/8) 6.35(1/4)/12.7(1/2) 6.35(1/4)/15.88(5/8) Dimensiones AlxAxP m 266x852x571 266x852x571 266x1058x571 266x1058x571 Peso neto kg 30 30 35 35 Fuente de alimentación V, F, Hz 230, 1+N, 50 Unidad Mural SAP-KRV184EH SAP-KRV224EH Función Frío Calor Frío Calor Capacidad kW 5.15 6.0 7.1 8.5 Circulación de aire (A) m3/h 850 850 920 920 Nivel de presión de sonido (Silencioso/B/M/A) dB-A 28/34/41/44 28/34/37/40 30/38/41/44 30/37/40/43 Diam. de Tubos Estr./Ancho mm 6.35(1/4) / 12.7(1/2) 6.35(1/4) / 15.88(5/8) Dimensiones AlxAxP m 298x1065x231 298x1065x231 Peso neto kg 12 12 Fuente de alimentación V, F, Hz 230, 1+N, 50 SPN-DS (N) SPN-DS (L) SPN-DSUV (K) SPN-DSUV (R) SPN-DS (W) DC Multi - Inverter (2x1, 3x1 4x1) Unidades interiores para combinar con unidades exteriores de página anterior SPN-DS (G) 27 SAP SPN-DS (N) SPN-DS (L) SPN-DS (G) SPN-DS (W) SPN-DSUV (K) SPN-DSUV (R) Dimensiones (3) SAP-FTRV..EH (4) SAP-XMRV..EH (5) SAP-UMRV..EH (1) - (2) SAP-KMRV..EH Precios Modelo Frío(kW) Calor(kW) Precio (€) SAP-KMRV76EH 2,2 2,5 400 € SAP-KMRV96EH 2,65 3,6 415 € SAP-KMRV126EH 3,5 4,2 450 € SAP-KRV186EH 5,15 6,0 500 € SAP-KRV246EH 7,1 8,5 900 € Modelo Frío(kW) Calor(kW) Precio (€) SAP-KRV184EH 5,15 6,0 350 € SAP-KRV224EH 7,1 8,5 400 € Modelo Frío(kW) Calor(kW) Precio (€) SAP-FMRV94EH 2,65 3,6 850 € SAP-FMRV124EH 3,5 4,2 890 € SAP-FTRV184EH 5,15 6,0 940 € SAP-FTRV244EH 7,1 8,5 1.060 € Modelo Frío(kW) Calor(kW) Precio (€) SAP-XMRV94EH 2,65 3,6 1.000 € SAP-XMRV124EH 3,5 4,2 1.050 € SAP-XRV186EH 5,15 6,0 1.070 € Modelo Frío(kW) Calor(kW) Precio (€) SAP-URV96EH 2,65 3,6 800 € SAP-URV126EH 3,5 4,2 810 € SAP-URV186EH 5,15 6,0 820 € SAP-URV246EH 7,1 8,5 950 € * En el precio se incluye el panel decorativo modelo PNR-XMRV93EHAA (185) Modelo Frío(kW) Calor(kW) Precio (€) SAP-KRV96EHDS 2,65 3,6 420 € SAP-KRV126EHDS 3,5 4,8 460 € SPN (Panel decorativo) 150 € * Datos dimensionales en páginas 28 y 29. (6) SAP-KRV..EHDS * Los precios arriba indicados no incluyen IVA. * La serie 6 de unidades multi irá sustituyendo durante 2009 a la serie 4. * La unidad KRV...EHDS incorpora de serie el panel en color plata. 12 ON/OFF Programador 12 h. Sensor en Mando DC inverter DC Inverter 24H PROGRAM Programador 24 h. Microprocesador DRY Deshumidificación AUTO F. Aire Automatico C. Deflector Reinicio Automático NIGHT SET BACK Función Nocturna AUTO Ventilador Auto OPERATION WIDE Amplio Rango Operación Menor Espacio S Ahorro Energía F. Antiolores y Antibacterias COOLING HEATING Cambio Aut. Rer-cal. Rápida Calefacción APATITA F.ApatitaP.Lavable Alta Potencia M. Multifunción DEFROST NON REVERSE Defrost con Bypass ION Ionizador 1H TIMER Programador 1/2/3/5 h. B. Condensados Panel Retráctil Panel Multicolor 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-61-3-6 1-2-3-4-5-6 1-2-3-4-5-6 1-2-3-4-5-6 4-5 66 1-2-3-4-5-6 Inversor senoidal SOLÉNER Manual del usuario Versión 1.5 Septiembre de 2008 Soluciones Energéticas S.A. Avenida Real de Pinto, 146 28021 Villaverde alto, Madrid Teléfono: 91-5050062 Fax: 91-5050079 www.solener.com [email protected] Manual del usuario del inversor Versión 1.5, septiembre de 2008 10 12.- CARACTERÍSTICAS TÉCNICAS Tipo de onda....................................................................................................Senoidal pura Voltaje nominal de salida............................................................................................230 Vca Frecuencia nominal de salida.........................................................................................50 Hz Variaciones en la frecuencia de salida..........................................................................<0,1% Variaciones en la tensión de salida..................................................................................<5% Voltaje mínimo de entrada........................................................................................5/6 Vnom Voltaje máximo de entrada.......................................................................................4/3 Vnom Rendimiento.................................................................................................................85-97% Rendimiento con carga nominal.....................................................................................>85% Autoconsumo (en búsqueda)......................................................................................<70 mA Distorsión armónica..........................................................................................................<5% Potencia nominal (W) 800 1000 1500 1800 2000 3600 4000 7000 Tensión nominal (V) 12 24/36 12 24/36/48 12 24 36/48 48 Sobrecarga 3’’ (W) 1500 2000 2800 3300 3600 7000 7000 12000 Sobrecarga 50’’ (W) 1200 1500 2250 2700 3000 5400 6000 10500 Sobrecarga 6’ (W) 960 1200 1800 2160 2400 4320 4320 8400 Longitud (mm) 315 315 460 460 535 535 535 647 Altura (mm) 118 118 157 157 178 178 178 210 Anchura (mm) 192 192 255 255 285 285 285 344 Peso neto (kg) 9 12 20 22 24 36 36 68 Caja de aluminio protegida con pintura epoxy. PROTECCIONES • Contra inversión de polaridad (con diodo inteligente) • Contra sobretensión y baja tensión • Contra cortocircuito y sobrecarga • Contra exceso de temperatura DATOS SUJETOS A VARIACIÓN SIN PREVIO AVISO Reguladores de carga solar Steca Elektronik GmbH | 87700 Memmingen | Germany | Fon +49 (0) 8331 8558-0 | Fax +49 (0) 8331 8558-132 | www.steca.com 128 187 4985 177 20 5 4x ø5 Steca Tarom 235, 245, 440 El Steca Tarom es un regulador de carga solar especialmente indicado para ser aplicado en telecomunicaciones o en sistemas fotovoltaicos híbridos. Un gran número de funciones interesantes permiten al usuario adaptar el regulador a las condiciones especiales de su sistema. Mediante la determinación del estado de carga de la batería, que ha sido de nuevo claramente mejorada, el sistema se regula de forma óptima y las baterías están protegidas. El regulador de carga Steca Tarom es la mejor selección para dimensiones de sistema hasta 2.400 Wp en tres niveles de tensión (12 V, 24 V, 48 V). Opcionalmente cabe la posibilidad de conectar otros dispositivos como un sensor de temperatura, un registrador de datos y un control remoto para configurar y monitorizar el sistema. Un contador de energía integrado (Ah) informa al usuario sobre el presupuesto energético de la aplicación. [áreas de aplicación] 1920 W [35 A ... 45 A] programable Características del producto Regulador híbrido Determinación del estado de carga con Steca AtonIC (SOC) Selección automática de tensión Regulación MAP Tecnología de carga escalonada Desconexión de carga en función de SOC Reconexión automática del consumidor Compensación de temperatura Toma de tierra en uno o varios terminales positivos o sólo en uno de los terminales negativos Registrador de datos integrado Función de luz nocturna con Steca PA 15 Función de autocontrol Carga mensual de mantenimiento Contador de energía integrado Funciones de protección electrónica Protección contra sobrecarga Protección contra descarga total Protección contra polaridad inversa de los módulos solares y de la carga Proteccion contra polaridad inversa por medio de fusible interno Fusible electrónico automático Protección contra cortocircuito de la carga y los módulos solares Protección contra sobretensión en la entrada del módulo Protección contra circuito abierto sin batería Protección contra corriente inversa por la noche Protección contra sobretemperatura y sobrecarga Desconexión por sobretensión en la batería Indicaciones Display LCD para textos para parámetros de funcionamiento, avisos de fallo, autocontrol Manejo Fácil manejo con menús Programación por medio de botones Conmutación manual de carga Interfaces Interfaz RJ45 Opciones Sensor de temperatura externo Contacto de alarma Certificaciones Aprobado por el Banco Mundial para Nepal Conforme a los estándares europeos (CE) Fabricado en Alemania Desarrollado en Alemania Fabricado conforme a ISO 9001 e ISO 14001                           —            235 245 440 Funcionamiento Tensión del sistema 12 V (24 V) 48 V Consumo propio 14 mA Datos de entrada CC Corriente del módulo 35 A 45 A 40 A Datos de salida CC Corriente de consumo 35 A 45 A 40 A Tensión final de carga 13,7 V (27,4 V) 54,8 V Tensión de carga reforzada 14,4 V (28,8 V) 57,6 V Carga de compensación 14,7 V (29,4 V) 58,8 V Tension de reconexión (SOC / LVR) > 50 % / 12,6 V (25,2 V) > 50 % / 50,4 V Protección contra descarga profunda (SOC / LVD) < 30 % / 11,1 V (22,2 V) < 30 % / 44,4 V Condiciones de uso Temperatura ambiente -10 °C … +60 °C Equipamiento y dieseño Terminal (cable fino / único) 16 mm2 / 25 mm2 - AWG 6 / 4 Grado de protección IP 32 Dimensiones (X x Y x Z) 187 x 128 x 49 mm Peso 550 g Datos técnicos a 25 °C / 77 °F Steca PA Tarcom Registrador de datos Steca PA HS200 Shunt Steca PA 15 Control remoto Steca PA TSK10 Sensor de temperatura externo BATERIA MONOBLOC 12 V 250 Ah BATERIA CICLICA PARA ENERGIA SOLAR. La nueva batería Lite Energy Power ofrece una inmejorable combinación de rendimiento en ciclado acompañado de un alto pico de potencia. Específicamente diseñada para aplicaciones que requieren una demanda de larga duración y de suministro de energía eléctrica • Apto para aplicaciones cíclicas. • Homologada en el Departamento de Defensa según EN50342 estándar (1997 Eurobat) • Alta resistencia a descargas profundas y repetidos ciclos de descarga • Larga vida útil Principales características técnicas • Gruesas placas con geometría radial para aumentar la vida y proporcionar mayor CCA. • Soldaduras reforzadas en las placas prueba de choque y vibración. También proporciona una vida útil más larga. • Material activo con composición concreta para reducir al mínimo el estrés cíclico. • Pb/Sb/Sn/As/Se rejillas de aleación para asegurar la resistencia contra la corrosión y realizar el óptimo contacto con los materiales activos. Diseñado para ciclo profundo. • Separador especial tipo industrial PE junto con separador de cristal mat - aumenta la vida Medidas: largo: 518, ancho: 273, alto: 242 mm Peso: 62 kg. Capacidad: 250 Ah a C-100 REF: 277725 Farigola, 20 local 08023 Barcelona Tel. 93 210 83 09 fax: 93 219 01 07 [email protected] www.tiendaelektron.comENERGÍAS RENOVABLES - MEDICIÓN AMBIENTAL The used nomenclature is: T_node_S,N,W,E,roof (i,j) = Tj t = Temperature in node j at time t T_node_S,N,W,E,roof (i,j+1) = Tj1 t = Temperature in node j+1 at time t T_node_S,N,W,E,roof (i,j-1) = Tj−1 t = Temperature in node j-1 at time t T_node_S,N,W,E,roof (i+1,j) = Tj t t = Temperature in node j at time t + ∆t T_0 (i) = T0 t = Temperature inside the building at time t T_0 (i+1) = T0 t t = Temperature inside the building at time t + ∆t The letters S,N,W,E,roof make reference to walls South, North, West, East or roof, respectively. 2.8.1. Thermal Loads Until here, it is only possible to calculate the temperature of nodes from t = 0 to t = 1. Now it is necessary to calculate the air temperature inside the building at t = 1 [T_0 (1)]. In calculation of air temperature are involved thermal loads like solar gains or external air flows, for example. Solar Heat Gain Through Windows Function SolarFactor In this function are defined the size and orientation of windows as well as thermal and optical properties of materials in which they are made according to explained in chapter 3.2. Then, this function calls 'radiation1', in order to know the perpendicular irradiance over each window. The windows are numbered from 1 to 5. 'SolarFactor' returns the solar radiation, q_sun, that goes through the windows inside the building. On the other hand, it is also calculated the conduction heat transfer through the glasses, q_window, by accepting that windows have not thermal inertia. These two loads are added giving q_solar for each ∆t of the simulation. q_solar = q_sun + q_window Convection Heat Transfer Once calculated the temperature of nodes at time t + ∆t , the next step is to calculate the heat transfer from the internal surface of the building to the air inside it. An energy balance is made between the nodes temperature at time t + ∆t and the air temperature T_0 at time t (in previous instant of time). Note that the temperature T_0 at time t + ∆t is not yet calculated. The description of equations is made in chapter 3.3. Air filtration and ventilation flow loads Air filtration and ventilation flow loads are calculated for each iteration in the simulation according to explained in chapter 3.4. They are produced due to the difference of temperature and relative humidity between the internal and the external air. Latent heat loads are only considered in summer according to the recommendations given in reference [4]. The equations that govern the psychrometry of the process have been obtained from reference [4]. 6 2.8.2. Energy Balance Without Heating The temperature inside the building at time t + ∆t [T_0(i+1)] is in this part of the loop finally calculated considering the temperature in the internal surface of the building at time t + ∆t [T_node(1,i+1)] and the different gains at time t + ∆t. Only the solar heat gain through the windows is considered at time t because it is calculated as a function of the temperature inside the room at time t [T_0(i)]. The used algorithms are a result of the analysis made in chapter 3.6 2.8.3.Energy Balance With Heating Controller In this section are set the values of the regulator constants. The regulator must calculate every ∆t the value of energy, Q_dot_H, needed to maintain the design conditions. The method to get this values is explained in chapter 3.7 of this project and calculated by using the function sprung3 Function sprung3 This function is a copy of Walls in which all the climatic variables are eliminated. Its only purpose is to get a graphic which will help to set the controller parameters. sprung3 can be run independently of Walls despite the name of used variables are the same. sprung3 creates a new state in which the air temperature is 0º inside and outside the building, and also in each node of external walls and roof. The external air temperature increases suddenly from 0 to 1 ºC and the answer of temperature of air inside the building is represented in a graphic. It is possible to get the value of parameters of the controller from this graphic by using the theory explained in chapter 3.7. This value is not definitive but it is used as a reference in order to find a better value by means of several simulations. PI controller A Proportional-Integral controller is chosen among the other two possibilities, a proportional controller (K) and a Proportional-Integral-Derivative controller (PID). Proportional controller is not able to satisfy the requirements and the obtained results with the PID-controller are quite similar to obtained with the PI. PI-controller returns the value of Q_dot_H (i+1), that is the energy that the installation has to provide in the next instant of time (t + ∆t) in order to maintain the internal design temperature. Energy balance Once all the variables at time t + ∆t are calculated an energy balance is made according to the equation 3.27. It returns the value of the internal air temperature of the building at time t + ∆t [T_0H(i+1)], when the heating (or air conditioning) installation is working. Note the difference in notation. The air temperature without heating is called T_0 whereas the air temperature with heating is called T_0H. A complete diagram of software operation is shown in figure H.2 7 Figure H.1 – Operating software diagram 8 2.9. AFTER RUNNING THE PROGRAM The simulation of 'Walls' gives as result the need of energy of the building for air conditioning and heating during one year. The values of variables are given per ∆t (= 360 seconds). Since ∆t is a very small interval of time, the use of the function 'hour_1' is recommended in order to get the values of variables in different formats (hourly, daily or monthly). Function hour_1 The function 'hour_1' must be run after the simulation of 'Walls' is completed. It will take the values of most important variables in 'Walls' and will return the same variables for longer intervals of time. It can return the highest value, the lowest, the median or the addition of all values of the interval. There is three possible intervals: one hour, one day and one month. simulation_Walls The result of all the variables of the simulation are saved in file the 'simulation_Walls.mat'. This file can be loaded and used for subsequently calculations. In the present study, the variables saved in 'simulation_Walls' are the base for sizing the different solar installations, as explained in following chapters. 9 3. PHOTOVOLTAIC INSTALLATION Function PowerPhoto In this function are calculated the main parameters of the photovoltaic installation. The main variables – consumed energy, produced energy and auxiliary energy – are characterized of the subscript 'panel'. Before run it, it is needed to load the file 'simulation_Walls'. The function 'PowerPhoto' can be run independently of 'PowerCollector6' and 'adsorption6' (see chapters 4 and 5 of this section). 3.1. SET THE PARAMETERS In this section are chosen the number and surface of photovoltaic panels as well as the orientation and the tilt of them. The software will returns later the rate of energy covered with this installation. The voltage of the batteries is needed to calculate the storage capacity in a posterior step. 3.2. RADIATION ON THE SURFACE OF THE PANEL This equation calculates the irradiance (W/m2 ) and the energy (J) on one panel. The equation is the same as the function 'radiation1'. 3.3. ENERGY FROM ONE PANEL Calculation of energy generated for one panel is made according to explained in reference [10]. The used nomenclature is also the same and is explained in the software. First of all, the characteristic parameters of the chosen panel are set. It is possible with them to calculate the form factor FF of the panel, which can be considered as the relation between the highest theoretical and the really produced energy by the panel. Then, the variation in open circuit voltage Vel,OC due to external air temperature is calculated. For the other hand, it is also calculated the variation in short circuit current ISC due to the variation in solar irradiance. With these parameters is possible to calculate the power produced by one panel, E_Ppanel as shown in the software. 3.4. CONSUMED AND PRODUCED ENERGY An specific heat pump must be chosen for this application according to the values of Q_dot_H, calculated in function 'Walls'. The heat pump is characterized of the maximal power for heating (or air conditioning) that it is able to produce, and the COP (coefficient of performance). These values are given by the manufacturer. It is supposed that the spin of the heat pump can be regulated in order to produce always the required energy until this maximal value. If required energy is higher, the heat pump will operate at its highest power. In this situation, the electrical consumption of the heat pump will be the required power for heating (or air conditioning) divided by the COP. Pheatpump=Eheating COP (W) and Eheatpump =Pheatpump ⋅t (J) On the other hand, it is needed to know the value of the electrical consumption of appliances, Eappliances . This value is given in chapter 3 of this project. The addition of heat pump and appliances consumption is the theoretical consumption of the building, called ET,photo : 10 ET,photo = Eheatpump + Eappliances (J) The energy consumption of appliances is only daily knew. Therefore is this value interpolate to get the consumption per ∆t. The produced energy from one panel was below calculated. We must multiply this value by the number of panels to get the total production. The produced energy is affected of the efficiency of the installation ( photo ), which is calculated in the software . The energy demanded by the building will be Ephoto=ET , photo photo where, according the nomenclature used in the software, will be E_photo=E_T_photo/eta_photo The auxiliary energy is in this section also calculated, like the difference between the consumed and the produced energy. Eaux , photo=Ephoto−EP , panel (J) The values of produced, consumed and auxiliary energy are also calculated hourly, daily and monthly by following the same structure as in function 'hour_1'. 3.5. SOLAR FRACTION. The parameter solar fraction, F_panel, shows the relation as a percentage between the produced and the consumed energy for one day, one month and the complete year. There is one variant of this parameter called F_panel_real. This one takes into account that the storage capacity of the batteries is limited and in some periods in summer a part of the energy can not be stored and is therefore wasted. 3.6. BATTERIES These equations are an extract from [10] and show the method to calculated the storage capacity of the batteries. These method is used in the calculation of installations isolated from the electric grid in which the batteries installation must provide all the energy needed by the building in cloudy days. The parameter N_d 'number of days' set the number of autonomy days of the installation without solar irradiance. The installation of this project is connected to the grid. Therefore, the accumulated energy will be calculated as the highest difference between the produced and the consumed energy in one day (normally in summer), represented with the variable 'capacity'. 11 4. HOT SANITARY WATER INSTALLATION Function PowerCollector6 In this function are calculated the main parameters of the hot sanitary water installation of the case 1 in this Thesis. The main variables – consumed energy, produced energy and auxiliary energy – are characterized of the subscript 'collector'. Before run it, it is needed to load the file 'simulation_Walls'. The function 'PowerCollector6' can be run independently of 'PowerPhoto' and 'adsorption6' (see chapter 5 of this handbook). 4.1. SET THE PARAMETERS In this section are chosen the number (N_collector) and surface (A_collector) of thermal collectors as well as the orientation (theta_collector) and the tilt (delta_collector) of them. The software will returns later the rate of covered energy with this installation. The software is planned according an schema in which the thermal collectors are connected in parallel. It is needed to see chapter 5 if N_collector > 1 and the collectors must be connected in series. rho_water and cp_water are the density and the specific heat of the heat transfer fluid respectively. The value of flow through the collectors, m_kg_h, is recommended by the manufacturer. But it can be changed if necessary. It is also needed to set the accumulator volume. In section 4.2.5. of the Thesis are given the relations for a good choice of accumulator volume. 4.2. DESIGN CONDITIONS This section sets the hot sanitary water flow needed to satisfy the requirements. This value is converted into energy by making an energy balance between the water inside the the accumulator at the design temperature, and the water coming from public net. The values of cold water temperature in the public net are given in the bibliography. 4.3. RADIATION ON THE SURFACE OF THE COLLECTOR This equation calculates the irradiance (W/m2 ) and the energy (J) over one collector. The equation is the same as function 'radiation1'. 4.4. PRODUCED ENERGY One specific thermal collector must be chosen to know the characteristic parameters given by the manufacturer: eta_0, a1 and a2. It is supposed that the input temperature in the collector, Tin, will be 30 ºC as median value. This supposition is acceptable in absence of a model of the accumulator and by accepting that the system will be provided of an automatic control system. The efficiency in heat transfer is set as 0.8. And it is also supposed that the highest power of auxiliary heater placed inside the accumulator, P_heater_HSW, will be 700 W, as recommended in [10]. The instantaneous energy produced by a thermal collector is given by three equations (they correspond with equations (4.15), (4.16) and (4.17) from the Thesis). All the parameters of these equations are defined in chapter 4.2.3. of the Thesis. 12 collector=0−a1 ⋅Tm ,collector−Tamb Gcollector −a2 ⋅Tm, collector−Tamb2 Gcollector (4.15) Tm ,collector=Tout ,collectorTin , collector 2 (4.16) ˙ mw ⋅cp, w ⋅Tout−Tin=collector ⋅Gcollector⋅Ncollector⋅Acollector (4.17) The three equations are solved simultaneously for Tout resulting in a second degree polynomial with the form A.Tout^2 + B.Tout + C = 0 The coefficients A, B and C are calculated in the function PowerCollector6.m There is two solutions for Tout. The only one valid is given like Tout ,collector=−B−  B2−4⋅A⋅C 2⋅A It is important to note that the coefficients A, B and C are different each instant of time. Once knew the output temperature, we can calculate the produced energy in the collector with equation 4.17 and the energy stored in the accumulator. The difference between the needed energy, Q_HSW, and the stored energy, Q_acc, gives the value of the required auxiliary energy, E_aux_HSW. This value can be positive, if there is a lack of energy; or negative. That means that the energy will be stored in the accumulator. Finally, the thermal collector efficiency is calculated. The calculation of these parameters is made for each ∆t. After are they calculated hourly, daily and monthly. The stored energy in one day, according to the characteristics of the accumulator, is supposed to be consumed at the end of that day. Because of that it can't be used the next day. 4.5. SOLAR FRACTION As made in section 3.5 of this handbook, the parameter solar fraction, F_HSW, for the hot sanitary water installation, shows the relation as a percentage between the produced and the consumed energy for one day, one month and the complete year. 13 5. ADORPTION MACHINE INSTALLATION Function adsorption6 Fundamentals of an adsorption machine are not implemented in this function. However, the adsorption machine works by means of a hot water flow supply. Therefore, here is only described the performance of an installation producing Hot Water (and Hot Sanitary Water, as well), similar as explained in chapter 4. This function is called 'adsorption6' in order to make a difference with function 'PowerCollector6', but the contents of them are very similar. In this function are calculated the main parameters of the installation described in case 2 of the Thesis. The main variables – consumed energy, produced energy and auxiliary energy – are here characterized of the subscript 'ads'. Before run it, it is needed to load the file 'simulation_Walls'. This function can be run independently of 'PowerCollector6' and 'PowerPhoto'. 5.1. SET THE PARAMETERS This section is the same as the chapter 4.1 with only one difference: The function 'PowerCollector6' is planned for thermal collectors connected in parallel. In case 2, the collectors are going to be connected in series of two, in order to obtain a higher temperature. Therefore there is the variable N_serie, which set the number of collectors connected in series. 5.2. DESIGN CONDITIONS This section sets values of energy needed to obtain the hot water flow satisfying the requirements for heating (Q_heating ), air conditioning (Q_cooling) and Hot Sanitary Water (Q_HSW). The energy for appliances is also considered in order to calculate the global efficiency of the installation. Like in chapter 4.2, the values of cold water temperature are given in the bibliography. 5.3. RADIATION ON THE SURFACE OF THE COLLECTOR This equation calculates the irradiance (W/m2 ) and the energy (J) over one collector. The equation is the same as function 'radiation1'. 5.4. PRODUCED ENERGY One specific thermal collector must be chosen to know the characteristic parameters given by the manufacturer: eta_0, a1 and a2. It is supposed that the input temperature in the first collector collector of the serie, Tin1, will be 20 ºC as median value. This supposition is acceptable in absence of a model of the accumulator and by accepting that the system will be provided of an automatic control system. The efficiency in heat transfer is set as 0.8. And it is also supposed that the highest power of auxiliary heater placed inside the accumulator, P_heater_ads, will be 8000 W. As explained in chapter 4.4 of this handbook, the instantaneous energy produced by a thermal collector is given by three equations (they correspond with equations (4.15), (4.16) and (4.17) from the Thesis). All the parameters of these equations are defined in chapter 4.2.3. of the Thesis. 14 There is a difference in relation with the calculation of a single Hot Sanitary Water installation (chapter 4.4 of this handbook), since two collectors are going to be placed in series. In this case, the output temperature of the first one, Tout1, will be the input temperature of the second one, Tin2. From here on, the calculation of the parameters is the same as explained in chapter 4.4. of this handbook. Note the subscripts 1 and 2, making the difference between the first collector of the series and the second one. Finally is made the calculation of the available cooling power from the adsorption machine. This one is affected of the external air temperature. The power supply for air conditioning decreases if the external temperature increases; and the power supply increase until 11 kW (highest power for cooling, according the manufacturer). The variations follow the equation of a straight line as shown in the simulation. This equation has been deduced from the graphics provided by the manufacturer, and shown in chapter 5.4.2 of the Thesis. The calculation of these parameters is made for each ∆t. After that are they calculated hourly, daily and monthly. The stored energy in one day, according to the characteristics of the accumulator, is supposed to be consumed at the end of that day. Because of that it can't be used the next day. 5.5. SOLAR FRACTION As made in sections 3.5 and 4.5 of this handbook, the parameter solar fraction, F_ads, for the installation described in case 2, shows the relation as a percentage between the produced and the consumed energy for one day, one month and the complete year. This comparative is made for thermal energy only, F_Q_ads, and including also the energy for electrical appliances which must be taken from the electric grid, F_E_ads. 15