Incorporating the regenerative evaporative cooler and the desiccant rotor, a prototype of the desiccant cooling system was built in the configuration shown in Fig. 2(a). As the sensible heat rotor, an appropriate commercial product was selected for the effectiveness of 80% at the process air flow rate of 20 CMM. The direct evaporative cooler at the supply air outlet was omitted in the prototype for simplicity. Since the process in the direct evaporative cooler is adiabatic, the omission of it does not influence the cooling performance. The exterior dimension of the completed prototype is 700(W) x 800(D) x 1,900 mm(H).

The prototype was tested at the ARI condition (indoor: 27oC, 50%RH, outdoor: 35oC, 40%RH) for performance evaluation. The regeneration air temperature was 59.5oC. The ventilation ratio was

0. 3, that is, the supply air comprises of 30% outdoor air and 70% recirculation air. The supply air flow rate was 14.6 CMM and the regeneration air flow rate was 14.0 CMM. The rotation period of the desiccant rotor was set at 450 s.

The psychrometric diagram of the desiccant cooling process is depicted in Fig. 7 from the

0.03

0.025

0.02

0.015

0.01

0.005

measured data of the temperature and the humidity at various points in the desiccant cooling system. The circled numbers in the figure imply the numbered locations in Fig. 2(a). For comparison, the expected at the design stage from the simulation is also shown in the figure. It is seen that the actual operation of the prototype follows closely the process as was designed.

The cooling capacity and COP are evaluated with following equations:

Qcool P5V pout (i5 i1)

where Qcool is the cooling capacity, Qreg the regeneration thermal energy input, Welec the auxiliary electric input, i the enthalpy, and Vpout is the supply air flow rate.

The cooling capacity was evaluated as 4.41 kW and COP as 0.762. It should be noted that this performance was obtained with the regeneration air temperature of 59.5oC.

The electric input was assessed mostly for the fans. The pressure drop in the process air side was 430 Pa and that in the regeneration air side was 390 Pa. Based on the measured values of the flow rate and the pressure drop, the fan efficiency is estimated around 35%, which is quite low for the fan in this range of flow rate. By improving the fan efficiency, it is quite clear that the system efficiency can be improved substantially. As an ultimate case, the COP based only on the thermal energy input is found as 0.867.

It should be also noted that the cooling performance in Table 1 was obtained with the ventilation ratio of 0.3. If the cooling of the ventilation air is accounted in the evaluation of the cooling performance, that is, if i2 is used instead of i1 in Eq. (1), the cooling capacity is evaluated as 5.8 kW and COP as 1.0.

3. Conclusion

In this study, a prototype of the desiccant cooling system incorporating a regenerative evaporative cooler was designed, fabricated and tested for the performance evaluation. To this purpose, two important components, i. e., the regenerative evaporative cooler and the desiccant rotor were developed and assembled into the system.

The regenerative evaporative cooler is to cool a stream of air using the evaporative cooling effect without an increase in the humidity ratio. It is comprised basically of a pair of dry and wet channels and the evaporation water is supplied only to the wet channel. By redirecting a portion of the air flown out of the dry channel into the wet channel, the air can be cooled down to a temperature lower than its inlet wet-bulb temperature at the outlet end of the dry channels. The regenerative evaporative cooler was built by compiling the multiple pairs of dry and wet channels. The two channels were separated by a thin flat plate and metal fins were inserted into both the channels to extend the contact surfaces improving the compactness of the cooler. A desiccant rotor was fabricated using the polymeric desiccant newly developed in Korea Institute of Science and Technology (KIST). To fabricate the desiccant rotor, firstly the polymeric desiccant was prepared by ion modification of the super absorbent polymer and laminated by coating the

desiccant on a 0.1 mm thick polyethylene sheet. Then the sheet was corrugated and rolled up into a rotor.

Incorporating the regenerative evaporative cooler and the desiccant rotor, a prototype of the desiccant cooling system was built. The exterior dimension of the completed prototype is 700(W) x 800(D) x 1,900 mm(H). The prototype was tested at the ARI condition (indoor: 27oC, 50%RH, outdoor: 35oC, 40%RH) for performance evaluation. With the regeneration air temperature of 59.5oC and the ventilation ratio of 0.3, the cooling capacity was measured as 4.41 kW and COP as 0.762.

References

[1] W. A. Belding and M. P. F. Delmas, Novel desiccant cooling system using indirect evaporative cooler, ASHRAE Transactions 103 (1997), 841-847.

[2] S. Jain, P. L. Dhar, and S. C. Kaushik, Evaluation of solid desiccant based evaporative cooling cycles for typical hot and humid climates, Int. J. Refrigeration 18 (1995), 287-296.

[3] A. A. Jalalzadeh-Azar, W. G. Steele, and B. K. Hodge, Performance characteristics of a commercially available gas-fired desiccant system, ASHRAE Transactions 106 (2000), 95-104.

[4] I. L. Maclaine-Cross and P. J. Banks, A general theory of wet surface heat exchangers and its application to regenerative evaporative cooler, J. Heat Transfer 103 (1983), 579-585.

[5] S. T. Hsu, Z. Lavan, and W. Worek, Optimization of wet-surface heat exchangers, Energy 14 (1989), 757-770.

[6] B. S. Choi, H. Hong, and D.-Y. Lee, Optimal configuration for a compact regenerative evaporative cooler,

3rd Asian Conference on Refrigeration and Air-Conditioning, Gyeongju, Korea (2006).

[7] G.-E. Song and D.-Y. Lee, Development of a compact regenerative evaporative cooler, 13th IHTC,

Sydney, Australia (2006).

[8] G.-E. Song, S.-M. Yoon, and D.-Y. Lee, An experiment on modular regenerative evaporative cooler for commercial use, Int. Congress of Refrigeration, Beijing, China (2007).

[9] D.-Y. Lee and M. S. Park, Solid desiccant and desiccant rotor, Korean Journal of Air-Conditioning and Refrigeration Engineering 34 (2005), 36-45.

In addition to the solar driven cooling systems described above, other passive cooling systems were also integrated to the building, including Outside Air Pre-cooling by means of a horizontal ground heat exchanger (e. g., earth tubes) directly connected to the Air Handling Units (AHUs).

For night cooling, natural ventilation works in combination with Radiative Cooling. It was implemented here in the form of a series of radiative panels placed on the roof and connected to radiant floors in all office zones which dissipate indoor heat gains at night.

2.2. Active Cooling Systems

Finally, the HVAC system is completed by a Conventional 100kW Air-to-water Heat pump to

ensure good thermal comfort inside the building even when unconventional systems are unavailable.

The variety of systems that has been integrated will allow researchers to study many different combinations of passive and active systems and look for the best strategies in order to achieve the targeted energy savings.

2. Control strategies

As mentioned previously, this paper will focus on the control strategies for cooling systems that has been implemented in the PSA building situated in Almeria. The difficulty lies in the optimal management of both conventional and unconventional cooling systems with the aim of minimizing the overall energy consumption while ensuring good summer thermal comfort. This is a quite difficult equation to solve and for this reason a whole research project will be dedicated to improving the control strategy initially designed for the building launch and testing phase. The control strategy explained here is therefore an initial, non-optimized one.

In a previous paper [4], the energy and exergy performance of a solar assisted standard DEC system were studied. In this work some improvements are made to the results of the previous paper:

• The parasitic electric consumption for the operation of fans and pumps are accounted for.

• A new definition for the exergy input to the systems is considered, which accounts for the exergy content of the primary sources, namely the fuel used to feed heaters and power plants for the production of electric energy.

As far as the first point is concerned, the pressure losses Apa occurring in each component of the air — handling unit were determined by means of data provided by the manufacturers, as reported in Table 2; an additional pressure loss of 150 Pa was adopted to account for the air distribution system, which may be considered the same for all the systems. The pressure losses Apw inside the pipes for the distribution of hot and cold water were also appropriately assessed by taking into account the volumetric water flow rate (Vw), the pipe diameter and its length. The parasitic electric consumption for fans and pumps can then be assessed, assuming qf = 0.7 and np = 0.6 as the efficiency of fans and pumps, respectively, and by means of the following formulas:

As regards the definition of the exergy input to the systems, in this paper the exergy of the primary sources is accounted for, namely the exergy of the fuel burned to feed the heat generator for the production of hot water and the power plants for the production of electric energy. According to this approach, the primary exergy associated with a certain amount of electric power Pel and thermal power Qhg may be respectively assessed as:

Here the ratio between the Higher Heating Value (HHV) of the fUel and its Lower Heating Value (LHV) is used because the exergy content of the fuel is related to its HHV, while the useful energy produced during the burning process is proportional to the LHV. In this analysis, natural gas was considered as the fuel used for the heat generator (HHV / LHV = 1.1), whereas oil was adopted for the power plants (HHV / LHV = 1.06). Furthermore, pel = 0.37 was adopted as the average efficiency for the production of the electric energy and its distribution to the final user, whereas ng = 0.90 was used as the efficiency of the heat generator. In Fig. 2 the comparison between conventional HVAC and standard DEC is reported; the comparison is based on three parameters, namely:

• the Specific Primary Energy Consumption (SPEC), defined as the ratio of the Primary Energy Consumption of the system to the overall thermal building load (QL + QS);

• the Specific Irreversibility Production (SPIR), defined as the ratio of the total Irreversibility Production of the system to the overall thermal building load (QL + QS);

• the exergy efficiency Z, defined as the ratio of the useful exergy output to the overall exergy input, accounted as primary exergy (see Eqn. 3).

V abs J

In Eqn. 3 we have considered that, when solar energy is used to assist the regeneration process, only a fraction (1-F) of the thermal load Qhc on the heating coil is covered by using fuel; the remaining fraction F is covered by solar energy, whose exergy content is considered proportional to the Carnot factor associated with the absorber plate temperature Tabs. The exergy flows and the irreversibility produced by each process are determined by means of the Gouy-Stodola equation, customized for the analysis of HVAC systems and humid air streams [5, 6]; the dead state corresponds to the outdoor conditions.

The standard DEC cycle has been studied for different regeneration temperatures. Thanks to the results shown in Fig. 2, it is possible to define the minimum solar fraction F needed to attain a second law efficiency of the DEC system better than that of a conventional HVAC system. This minimum value depends on the regeneration temperature required by the desiccant wheel; as an example, when working with a regeneration temperature as high as 90°C, at least F = 0.35 is required to get a higher exergy efficiency than the conventional HVAC, whereas F = 0.15 is sufficient if the regeneration temperature is as high as 70°C. When using high regeneration temperatures, a higher thermal power is required by the heating coil, but the dehumidification potential of the desiccant wheel also gets higher, thus allowing a reduction of the size of the pre­cooling coil (EB, see Fig. 1). For this reason, if a very high solar fraction is adopted — more or less higher than 80% — it seems to be more performing to work with higher regeneration temperatures. Further aspects will be addressed later in the paper.

When looking at the first law performance, the advantage of using solar assisted DEC system is more evident, and the energy break-even point is reached for a very low solar fraction. It has also to be underlined that the contribution of the parasitic consumption is not negligible. The exergy provided to feed fans and pumps ranges from 13% of the overall exergy input in a standard DEC system to 21% in a solar-assisted system with F = 1. In the conventional HVAC system this contribution reduces to the 5%, due to the low number of components inside the AHU.

For the identification of the safety level of a working fluid, the ASHRAE 34 safety classification that applies for refrigerants can be used. This classification is based on two key parameters: the toxicity and the flammability. Toxicity can be identified by some numbers such as TLV (Threshold Limit Value). Flammability is generally identified by the LFL (Lower flammability limit) and the HOC (Heat of Combustion). The ASHRAE standard 34 is made of two classes of toxicity (A: non-toxic B: toxic.) and three groups of flammability characteristics (1: no flame propagation, 2: low flammability limit and 3: high flammability limit). The matrix shown in Fig. 2 was adopted for an easy identification of the safety level of any substance. From this classification, the most desirable class for an ORC working fluid is

A1. In addition to the aforementioned desirable safety properties, the working fluid should be non-explosive and non-radio-active.

Fig. 2: ASHRAE 34 Refrigerant Safety Classification

Joao Farinha Mendes Jose Pedro Almeida 1, Antonio Rocha Silva 1
Manuel Collares Pereira 2, Pedro Adao 2
Miguel Morgado 3
Andrea Costa 4

1 DER/INETI — Edificio G, Estrada do Pago do Lumiar 1649-038 Lisboa Portugal,

2 AOSOL, SA — Lugar da Sesmaria Limpa, 2135-402 Samora Correia, Portugal
3 EUROSOLAR, Lda, R. Domingos Jose de Morais, 57 — 2°Dto, 2685-046 Sacavem, Portugal.
4 ACE, Pfalzerstr. 75, 83109 Grosskarolinenfeld, Germany
‘Corresponding Author, farinha. mendes@ineti. pt

Abstract

This paper describes the work developed so far by the Portuguese partners, involved in the POLYSMART Project [1]. The main goal of the aforementioned project is to support the development of the market for small and medium capacity tri-generation plants, installing twelve demonstration systems, which involve a wide variety of different solutions, using commercial cogeneration systems fed by renewable or non renewable primary sources combined with small thermally driven cooling machines in different stages of development and with different operation principles. The paper makes a review of the rationale for the tri­generation concept in the Portuguese context, describes the two demonstration systems preview for installation in Portugal, shows the configuration adopted for both systems, the monitoring and evaluation procedure already agreed among the partners.

1. Introduction

The cost efficiency of a cogeneration plant depends on the number of operating hours, which can be significantly improved by using also the waste heat for cooling purposes, through a thermally — driven cooling machine.

Considering the recent Portuguese legislation about micro-generation, this type of system has become very interesting for the residential and small office buildings in Portugal, not only with regard to the inherent energy savings but also from a pure economic point of view.

This is also the case in other European countries, where there is an important effort in research institutions and industry interest on development of small thermally-driven cooling machines, able to use waste heat or heat produced by a renewable source.

The POLYSMART Project [1] intends to combine those efforts in a European Integrated Project partly funded by the European Commission under FP6, with the main goal to support the development of the market for small and medium capacity tri-generation plants. Coordinated by FhG-ISE, this project involves several established companies with market products in the cogeneration field and thermally-driven cooling machines developers presenting different stages of development of their products. In all participating countries a balanced number of private or public research institutions is included, giving a total number of 34 partners, that transform each working meeting in a real poly-generation congress.

The number and variety of products available at the moment, led to the design of different and interesting combination solutions, connected to the different locations where the twelve demonstration systems are installed. Different energy source supply and different thermally-driven cooling technologies, in seven European countries, will be connected in a wide variety of applications. The possible combinations, usages and links between main components of the poly­generation small scale demonstration systems studied in the framework of POLYSMART Project are described in the block diagram shown in Fig.1.

This paper describes the work developed so far by the Portuguese partners, involved in this project: INETI is responsible for monitoring the two sub-projects carried out in Portugal; AOSOL, a company producing solar collectors of the CPC type, is also a developer of an air-cooled ammonia — water absorption chiller designed for 8 kW cooling power. Two prototypes of this chiller will be used in both sub-projects; EUROSOLAR, an energy consulting company interested in the study and installation of distributed sustainable energy systems.

The first demonstration plant will provide the air-conditioning (heating and cooling) for part of the AOSOL office building whereas the second demonstration plant will be installed by EUROSOLAR at INETI in the new office building, Solar XXI, of the Renewable Energy Department. In both cases the energy necessary to heat up the domestic hot water is planned to be supplied by the tri-generation plants, which include 5 kW electric power generators, using respectively LPG and bio-fuel as primary energy source.

Related with these aspects it is important to make a survey of potential applications matching the design size of these poly-generation systems, which allow using (almost all of them) the waste heat produced during the year.

The paper also describes the main characteristics of each plant, explains its operation modes and. the monitoring scheme implemented at both sub-projects will permit to investigate and assess not only the reliability but also the economic and energy performance of their operation.

Exergy analysis is either applied for the identification of system irreversibilities via the calculation of exergy losses and exergy destruction, or for the assessment of system performance by calculating the exergy efficiency. As the system under consideration here is characterized by cyclic operation (fig 1) two approaches to exergy analysis are imaginable. Firstly, each cycle stage could be subject to an exergy analysis which would require taking into account the exergy of the sorption material and the adsorbate.

with Ew=E3=E4=0 during the desorption stage and Ei=E2=0 during the pre-cooling stage due to zero mass flow rate. The overall exergy balance for the cycle can then be expressed by equation 7.

£(( + E3 + E. ) — + E4 ) = Ed [J] (equation 7)

The average exergy destruction rate of one heat exchanger can be obtained dividing by the cycle time. The exergy efficiency can be expressed as the relation of exergetic product to the exergetic input. Identifying the increase in exergy between fresh air inlet and supply air outlet during adsorption as the system exergetic product, the exergy efficiency is given by equation 8.

U. Jakob1* and S. Saulich1

1 SolarNext AG, Nordstrasse 10, 83253 Rimsting, Germany
* Corresponding Author, ali. iakob@solarenxt. de

Abstract

This paper presents the development and investigation of solar cooling systems based on small-scale sorption heat pumps and chillers, respectively. An ammonia/water absorption chiller with a cooling capacity of 12 kW, the chillii® PSC12, a 17.5 kW water/lithium bromide absorber, the chillii® WFC18 and two water/silica-gel adsorption chillers with cooling capacities of 7.5 and 15 kW, the chillii® STC8 and chillii® STC15, all single effect, are specified as core components of solar cooling systems. Up to now over twenty chillii® Cooling and Solar Cooling Systems respectively are in installed in Germany, Austria, Spain, Italy, Malta, Romania, Syria, Canada, China and Australia. Different kind of applications are realised like for residential buildings, retirement home, office buildings, bank, bakery, greenhouse and institutes. The first experiences and experimental results of the installed solar cooling systems showed that the chillers and the solar cooling system work very well. Keywords: Solar cooling, absorption, adsorption, heat pump, chiller

1. Introduction

Active air-conditioning of buildings is also necessary at European climate conditions, especially in Southern Europe. Therefore the energy consumption for cold and air-conditioning is rising rapidly. Usual electrically driven compressor chillers (split-units) have maximal energy consumptions in peak-load period during the summer. In the last few years even in Europe this regularly leads to overloaded electricity grids. The refrigerants that are currently used in the split-units do not have an ozone depletion potential (ODP) anymore, but they have a considerable global warming potential (GWP), because of leakages of the chiller in the area of 5 to 15 % per year. However, solar cooling systems provide a sustainable active air-conditioning possibility. The sorption heat pumps or chillers use environmentally friendly refrigerants and have only very low electricity demand. Therefore the operating costs of these chillers are very low and the CO2 balance compared to split-units is considerably better. The main advantage of solar cooling is the coincidence of solar irradiation and cooling demand. Particularly the sale figures of split-units with a cooling capacity range up to 5 kW are rising rapidly. In Europe the number of sold units has risen about 53% from

5.3 million in 2004 to predicted 8.1 million in 2007 [1]. The Japan Refrigeration and Air Conditioning Industry Association (JRAIA) has expected a worldwide sales of 74.4 million units in 2007. The market potential for solar cooling systems with small-scale capacity is very large, so that different companies are developing solar cooling systems/kits for the product business [2]. In case active cooling being necessary, the long running times of the chillers are the key for economic efficiency of solar cooling systems. For residential buildings in Central Europe only about 50 to 200 cooling hours occur, whereas in the southern Mediterranean area as well as for some industrial
and office buildings approximately 1,000 full load hours are necessary. An all-season use of renewable energy sources for hot water, space heating and solar cooling is here indispensable.

The project faces difficulties related to the filter supply. The university procurement is still looking to find a reliable and reasonable channel for importing the needed filters. Due to the continental climate, Yerevan is a rather dusty city: the summer very intense winds remove and bring the desiccated upper layer of the soil. While there is a huge increase in the construction rate in Armenia, the construction infrastructure yet to solve a number of problems, that includes also HVAC components supply chain.

Due to this problem the system has been stopped last autumn, to be restarted very soon.

4. Powering the DESODEC system by PV.

It has been decided to amend the DESODEC project solar installation by a 5 kW PV system. The goal of this project was to provide independent and clean electric power for DESODEC system operation.

The average electric consumption of the DESODEC system is equal to 5 kW, with maximum value reaching up to 10 kW. The PV system has an inverter of 10 kW to meet the maximal power consumption need. The system has the following components: PV field; charge controllers; grid switch; battery bank; inverter; support structure; monitoring equipment. The battery bank is a series connection of 8 units of 6 volt Rolls deep cycle led acid solar batteries. The total capacity is 1150AH at 20 amperes discharge current, and 850AH for 100 amperes discharge current. At 48 volts this constitutes about 50 kWh of power stored, with average consumption of the DESODEC system equal to 5 kW it provides about 10 hours of uninterrupted operation. When batteries are exhausted and there is no sun, the DESODEC system switches to the grid [5].

One of the interesting outcomes of this part of the project is related to the architectural solution for installing SWH and PV panels onto a complex rooftop of an existing university building, illustrated in the fig. 6.

The DESODEC system operating experience can be used to improve future setups. A number of other

projects are expected to perform as a continuation for DESODEC (see e. g. [6]).

References

[1] J. Farinha Mendes, A. Hambarian, H-M Henning, V. Afyan, A. Pinov — “Solar Driven Desiccant Cooling Demonstration System” — Int. Congress on “Business and Investment for Renewable Energy in Russia”, May 31-June 04, 1999, Moscow.

[2] J. Farinha Mendes, A. Hambarian, H-M Henning, Tim Selke, V. Afyan, A. Pinov, F. Luginsland — “Solar Driven Desiccant Cooling System for American University of Armenia” — Int. Workshop on “Results of Fundamental Research for Investment, May 28-30, 2001, St. Petersburg.

[3] J. Farinha Mendes, A. Hambarian, H-M Henning, Tim Selke, V. Afyan, A. Pinov, F. Luginsland — “Experience of International Cooperation on Development of Cooling Systems for Buildings Using Solar Energy” — International. Workshop on Renewable Energy Applications, June 5-8, 2001, Moscow.

[4] J. Farinha Mendes, A. Hambarian, H-M Henning, Tim Selke, V. Afyan, A. Pinov, F. Luginsland — “Sistema de Demonstragao com Energia Solar e Tecnologia DEC para Arrefecimento Ambiente Instalado na Universidade Americana da Armenia” — Accepted for oral presentation at the XI Iberian and VI IberoAmerican Solar Energy Congress to be held in Vilamoura (Algarve, Portugal), 29 Sept — 02 Oct 2002.

[5] Zhozef Panosyan, Artak Hambaryan, Kenell Touryan, Armen Tumanyan, Yeremia Yengibaryan, Mikayel Piradyan, Arsen Darbasyan, Wilhelm Akunyan. Design, “Construction and Monitoring of a Solar

Photovoltaic Station of AUA” — 21st European Photovoltaic Solar Energy Conference, 4-8 September 2006, Dresden, Germany.

[6] Artak Hambarian. “Renewable Energy Related Projects of the Engineering Research Center of the American University of Armenia. Invited conference paper”. ArmTech 2007 Congress, July 4-7, San Francisco, CA USA.

Regarding TRNSYS models, novel types were created for absorption chillers, using COP values from manufacturers’ data (not just COP max but COP(T)). The model is able to run for a whole year (365 days) according to control rules, self-deciding whether to operate in heating or cooling mode.

For building simulation, Type12c was used in the model. Type12c was used instead Type56 because it is less complex and the results have enough accuracy for the purpose of studying the system. The models also consider solar gains through the glazed area. Typelb allows the simulation of a flat-plate collector. In order to simplify the model, the same type was used for simulating the vacuum tube collector. For thermal storage, several stratified tanks with variable inlet and uniform heat losses were considered — Type4c. Several data files of absorption chillers were created according to Yazaki and Phonix chiller technical data, with Type107. For the electrical vapor compression chiller Type53 was used with a data file containing information of the

YorkLCHHM200 WL machine. Other types used were: Type109-TMY2, Type3b for simulation of pumps and cooling tower (less complex compared to Type51), Type91 and Type6.

For the hotel and office building located in Rome and Lisbon, cooling needs correspond to 65 up to 85% of the total thermal load. In Berlin, those buildings have more heating needs, although cooling needs to be considered because it represents 15 to 25% of the total thermal load.

In a single-family house, the cooling load is not so high because it doesn’t match so considerably with occupation time (except on weekends). In Rome and Lisbon it corresponds to values between 25-40%. For Berlin, it can be neglected (less than 5%).

4 Results

The objective of the ORASOL project is to propose both a fundamental reflection but also an applied study of solar cooling processes. Indeed, the first step of the project involves the development of new models for all the components of the systems, and also the simulation of the whole installation including the building. The second step will be the validation of the models and the simulations. This part relies mainly on the use of experimental facilities proposed by the various partners. The validation may also involve parametric sensitivity analysis procedures and inter software comparisons between the different partners.

The objectives are to work out various tools such as:

• Simulation tools for components, systems and installations.

• Sizing tools for new installations

• Control tools

• Optimization tools for components, systems and installations.