Three years operation experience of a ground source heat pump system in Northern Greece
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Three-years operation experience of a ground sourceheat pump system in Northern GreeceA.Michopoulos,D.Bozis,P.Kikidis,K.Papakostas,N.A.Kyriakis*Process Equipment Design Laboratory,Department of Mechanical Engineering,Aristotle University of Thessaloniki,P.O.Box487,54124Thessaloniki,GreeceReceived16May2006;received in revised form1August2006;accepted4August2006AbstractThe paper presents the basic parameters and the energyflows of a ground source heat pump system(GSHP)used for air conditioning the New City Hall of Pylaia(Thessaloniki area—Northern Greece).The building is a typical public one,with an air-conditioned area of1350m2.The ground source heat pump installation is the largest in Greece,and its operation is monitored with the aid of a DAQ system.The energyflows presented in the paper are based on DAQ recordings of thefirst3years of system’s operation.It is proved that the energy demand of the system is significantly lower,compared to that of conventional heating and cooling systems.The seasonal COP of the system has not yet been stabilized, gradually increasing,as it is expected due to the operation of the ground heat exchanger.#2006Elsevier B.V.All rights reserved.Keywords:Ground source heat pump system(GSHP);Energy demand;Heating loads;Cooling loads1.IntroductionHeat pumps are characterized by the strong dependency of their coefficient of performance(COP)on primary circuit temperature.Consequently,‘‘pumping’’heat from a very low (e.g.around freezing or below)temperature heat reservoir or rejecting heat to a high temperature(408C or higher)heat reservoir make the system inefficient in terms of primary energy(electricity)demand.This characteristic implies that the ambient air,depending on climate conditions,may not be the best choice for primary circuit heat reservoir.The use of surface or underground water reservoirs orflows in water-to-air or water-to-water systems overcomes this disadvantage,but again such reservoirs orflows are not widely available.Due to the heat capacity of soil,ambient air temperature variations are directly reflected only on the surface soil temperature,their effect being reduced at deeper layers.As a consequence,soil temperature is stabilized at the yearly average air temperature after the depth of about10m[1].A ground heat exchanger can therefore be formulated,supplying the primary circuit of the heat pump with afluid of a more or less constant temperature.A number of ground heat exchanger concepts(vertical, horizontal,of in series or in parallel connection,etc.)have been developed,featuring different degrees offluid temperature stability[2–4].In this work,a vertical ground heat exchanger of parallel connection coupled to a heat pump system for air conditioning a public building in northern Greece is presented with energy data regarding its operation over3years.2.Description of the building and installationThe ground source heat pump system is installed at the New City Hall of Pylaia,a suburban of Thessaloniki,in Northern Greece.The building was designed in1995and the construction works were completed in2002.It is located at a distance of8km from Thessaloniki centre,in an area with basic climate parameters as listed in Table1.These parameters, combined with the shape and orientation of the building,may impose simultaneous heating and cooling of different thermal zones,especially during intermediate seasons(autumn and spring).The building houses the Administration Services of the Pylaia Municipality,and it consists of two underground and/locate/enbuildEnergy and Buildings39(2007)328–334*Corresponding author.Tel.:+302310996083;fax:+302310996087.E-mail address:nkyr@auth.gr(N.A.Kyriakis).0378-7788/$–see front matter#2006Elsevier B.V.All rights reserved.doi:10.1016/j.enbuild.2006.08.002three over groundfloors.The main functions of the building (offices,meeting rooms,a200people auditorium and corridors) are located at the three over groundfloors,covering a total air-conditioned area of1350m2.Auxiliaries(store rooms,record rooms,utilities and car parking)cover a ventilated area of 1070m2and they are located at the two underground levels.On average,the building is in operation250days per year,from 08:00until18:00.During the design phase,the total heating load of the building was calculated at150kW,with60%of it being ventilation losses.The total cooling load was calculated at 270kW,appearing at the time slot15:00–17:00in July.The observed significant difference between heating and cooling loads is mainly due to the high solar loads,and it is typical for office buildings in Greece,even in the northern part of the country.The offices and the corridors are air-conditioned with two pipe fan-coil units.In terms of their connection to the hot or chilled water loops,the fan-coils were organized in four groups, based on the operation and the thermal characteristics of the room they serve.As a result,four fan-coil loops were formed, serving building areas with similar thermal behavior and operation profile.These loops were connected respectively to four water-to-water heat pump systems and they are capable of totally independent operation,meaning that,depending on the requirements of the zones they serve,some of them may provide heating while the others may provide cooling.Three Central Air Handling Units(AHUs)with water coils provide make up air to the building.The water coil of each AHU is connected to a group of heat pumps.The water coils of the AHUs and the fan-coils were selected for water inlet temperatures of40and98C,heating and cooling,respectively.A total of seven heat pump groups were installed,four serving the fan-coils and three the AHUs.The cooling capacity of each heat pump group is20–60kW,depending on the group. Each group consists of one to two in parallel-connected heat pumps,operating under common control.Twenty-one vertical boreholes(3Â7on a4.5Â4.5grid)up to a depth of80m consist the ground heat exchanger.Each borehole features a4in.diameter,with a single U-shape PE-HD tube—o.d.40mm.The primary circuitfluid is de-ionized water without any anti-freezing agent.In order to promote the thermal conductivity between the U-tubes and the surrounding soil,but also for their protection,a1:19betonite/cement mixture was used.As a backup of the ground heat exchanger,a120kW oil-fired conventional boiler and a cooling tower were installed.An overview of the system is shown in Fig.1.A central BMS is also foreseen,to fully control the operation of all the devices and networks of the system and also to provide system monitoring.This BMS has not yet been installed; presently control being provided either locally,with small autonomous units,or manually.An external data logging system is also installed,simply for monitoring the behavior of the whole installation.3.The data logging systemAim of the system is to provide an external overview of the operation of the installation,therefore only a limited number of data are recorded,as it follows:Ground heat exchanger inlet and outlet temperatures,using film-type4wire Pt-100temperature sensors.Ambient air temperature,using a3-wire Pt-100temperature sensor,located outside,at the NW side of the building, relatively protected from direct sunshine.Campbell Scientific,type CR-10data logger.One set of data,consisting of the three temperatures and the date and time of the day,is stored every10min.The central pump delivery is not recorded since,at least for the time being,its operation is of the on–off type,and repeated measurements in different days and hours(using the ultrasonic Panametrics PT878flow meter)revealed that it remains constant at48m3/h.Fig.2shows a typical winter day(heating period)recording. During the night the heat pump system is out of operation,and the water temperatures recorded correspond to the room temperature where the sensors are located.The system is turned-on at07:00and the water of the primary circuit starts to circulate.Temperatures gradually decrease to the operation level imposed by the ground heat exchanger,but the temperature gain can be clearly seen.Due to the increasing ambient temperature and solar gains,the thermal load of the building,is reduced at around noon,and,as result,water temperatures gradually increase.The heat pumps stop at14:30 and thefluid temperatures start rising,until,after about4h, they reach the equilibrium point(room temperature).Fig.3shows a typical recording of a summer day(cooling period).The inlet and outlet temperatures have mutually changed relative positions,meaning that the water is now cooled in the heat exchanger,and their level is significantly higher than that during heating.The start and end point of heat pump operation are again clearly visible(07:00and13:00, respectively).It can be also seen that the central circulation pump is always on.4.Operation resultsThirty-six months of operation monitoring have already been accumulated(January2003–December2005)and someA.Michopoulos et al./Energy and Buildings39(2007)328–334329 Table1Basic climate parameters of building’s areaLatitude/longitude408360/228590Heating period November–MarchHeating design conditions(99.6%)À58CMean daily temperature in January 6.18CHeating degree days(base188C)1800KdaysCooling period Mid of May–SeptemberCooling design conditions(0.4%DB/MCWB)34.0DB/21.0WBMean daily temperature in July268CUndisturbed ground temperature188C330A.Michopoulos et al./Energy and Buildings39(2007)328–334Fig.1.System overview.Fig.2.Typical recording of the ground heat exchanger operation for heating(28-02-2003).significant conclusions regarding the operation and economy of the system can be drawn.The energy exchanged between water and soil in the 10min interval between two successive entries of the data logging system can be calculated as Q ¼˙mc ð#out À#in Þ1060½kWh (1)where ˙m is the main pump water delivery [kg/s];c the specific heat capacity of water [kJ/(kg K)];#out the water temperature atthe ground heat exchanger outlet [8C];#in is the water tem-perature at the ground heat exchanger inlet [8C].The ‘‘instantaneous’’(10min interval)heat supplied to the building and the electricity consumption of the heat pump system can be calculated from Eq.(1),using the COP value given by the device manufacturer for the average between inlet and outlet water temperature.Based on Eq.(1),the heat exchanged between water and soil as well as the heat supplied to the building will be positive or negative.Conventionally,the heat supplied to the building (heating period)is taken positive.A.Michopoulos et al./Energy and Buildings 39(2007)328–334331Fig.4.Monthly distribution of heat exchange in the ground heat exchanger and operating hours for the period 01-2003to12-2005.Fig.3.Typical recording of the ground heat exchanger operation for cooling (16-07-2003).Obviously,the electricity consumption of the heat pump system is always positive,regardless of the operation mode.Fig.4shows the monthly values of the heat exchange between water and soil over the period monitored.It is observed that during the first year (January–December 2003)the system was in operation 24h/day,for heating or cooling.During the remaining period (January 2004–December 2005)the system was shut down during the intermediate seasons (April,May and October),since the ambient temperature during these months was in the range 15–188C,around the change over temperatures of the buildings zones,therefore there was no need for either heating or cooling.Fig.4shows also that the hours of operation per month for some months during the first year were up to 70%higher of the respective months of the next year,the respective loads being increased by as much as 97.5%.This can be attributed to the more extreme ambient conditions of 2003,as it is verified in Fig.5,where the average month temperature is plotted.Additionally,it has to be attributed also to the manual operation of the system and the lack of experience of the operator.This is verified by the monthly loads of the building shown in paring for example the data for Feb 2003and 2004,it is clear that despite the fact that the average ambient temperature is roughly the same,around 5.28C,the heating load in 2003A.Michopoulos et al./Energy and Buildings 39(2007)328–334332Fig.5.Monthly thermal load of the building and monthly average ambient temperature for the period 01-2003to12-2005.Fig.6.Seasonal COP of water-to-water heat pumps.was17.37MWh,while in2004only9.53MWh,meaning that in2003the rooms were heated far beyond the required temperature.Another important conclusion regarding the system operation is revealed in Fig.6.As it can be seen,there is an increasing trend of the seasonal COP for heating,from4.4to5.2and a much less enhanced decreasing trend of the seasonal COP for cooling,from 4.5to4.4.This is due to the cyclic(heating–cooling)operation of the system over the year,which imposes higher ground temperature at the beginning of the respective period.This ground temperature increase has a stronger influence on the heating mode rather than on the cooling one,because of the average temperature level.It is expected that the system will reach an equilibrium condition after a limited number of periods, with the corresponding seasonal COP stabilized.In order to form an energy comparison basis of the system, the electricity required around the year for heating and cooling the building with a more conventional air-to-water(AW)heat pump system was calculated,using the COP corresponding to the ambient air temperature of each10min interval.The heat pump of the system is assumed to produce hot or chilled water, which is then delivered to the existing fan-coils.Additionally, the energy requirements of a completely conventional system were calculated.This system is assumed to consist of an oil boiler with an efficiency of88%for heating and air-to-air split air conditioners(AA)for cooling.For the comparisons,an overall efficiency of33%is assumed for electricity production from fossil fuels.Only the thermal and cooling loads were considered in this comparison,i.e.the energy requirements for (a)water circulators,(b)de-icing of the AW heat pumps,(c) fan-coil blowers were neglected.The results of this comparison per month are shown in Fig.7.The equivalent total thermal energy per operation period for each system is listed in Table2. It is clear that the most energy demanding system for heating is the conventional boiler,followed by the AW,requiring respectively up to120%and50%more thermal energy than the GSHP(see Fig.7)or97%and45%period average(see Table2).For cooling,the worst system is the AA,followed by the AW,requiring respectively up to90%and50%more energy (see Fig.7)or55%and28%period average(see Table2).5.ConclusionsThe ground source heat pump system of the New City Hall of Pylaia-Thessaloniki(total enclosed area of1350m2), consisted of7groups of water-to-water heat pump,21 boreholes with80m depth and fan-coil units has accumulated 3years of trouble free operation in heating and cooling mode.The basic operation characteristics are constantly monitored over this period and the results show that the ground heat exchangerfield approaches equilibrium in terms of start and end period temperatures,this also reflected on the seasonal COP.The primary energy required by the system for heating is estimated to be lower by45%and97%(period average)as compared to that of air-to-water heat pump based and conventional oil boiler respectively.In cooling mode the relevant differences are estimated at28%and55%for air-to-water and air-to-air heat pump based systems.Thesefigures prove that inA.Michopoulos et al./Energy and Buildings39(2007)328–334333Fig.7.Energy demand comparisons of alternative systems. Table2GSHP thermal energy demand and the equivalent for the alternative systems perperiod and mode of operationPeriod Heating[GWh th]Cooling[GWh th]GSHP AW Boiler GSHP AW AA1st21.525.835.680.6103.5125.42nd16.722.731.539.346.157.63rd17.525.434.431.937.446.5both modes,heating and cooling,the GSHP system is significantly less demanding in terms of primary energy. 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