Copyright Executive Summary

Transcription

1 Energy Savings Using Airius Air Pear Destratification and Air Circulation Fans in an HVAC Environment in Temperate and Sub Tropical zones. HAP Software Analysis Engineered by Vahid Vakiloroaya A Copyright Executive Summary Thermal Equalisation and air circulation has been proven worldwide to be effective in saving energy in most types of conditioned buildings, primarily in the heating climate of the northern hemisphere. The application of destratification and air circulation as a simple, cost effective, energy saving solution for air conditioned buildings in the southern hemisphere where the climate is temperate or sub-tropical has not been considered or understood until the last couple of years. However, the recent use of thermal equalisation in conditioned buildings such as retail precincts, schools, manufacturing plants, cold stores, warehouses and offices using products such as the Airius Air Pear Thermal Equalizer fans in Sydney, Melbourne, Brisbane and Auckland has provided some significant energy saving outcomes during the very hot summer of Energy Savings and short Returns on Investment in cooling mode from the use of Airius Air Pear destratification fans can be extrapolated to all summer periods in a range of locations. This report has been commissioned by Airius Oceania P/L to help mechanical engineers and our customers understand the efficacy of thermal destratification and air circulation in conditioned spaces (in the temperate and sub-tropical climate) as an acceptable and proven simple technology to significantly reduce HVAC energy usage in the cooling months of summer, spring and autumn when required. In addition user comfort is significantly improved due to the gentle air movement from Airius Air Pear units across the skin creating evaporative cooling. Outcomes of the modelling in this report for a 2000 sq. metre 4 metre high retail space using a water cooled HVAC system indicate cooling energy savings of a minimum of 10.9% across the year, for a 2 Deg. C Delta T between floor and ceiling, up to 23% energy savings where the Delta T is 6 Deg. C. Research from BSRIA C in the UK indicates that One Deg. C temperature increase per metre in height is common inside buildings. In Australia temperature differences of 3 Deg. C every metre in height has been recorded in buildings that Air Pears have been installed into. It is important to note that different types of HVAC systems such as air cooled units may show even higher energy savings dependent on climatic location, internal floor to ceiling Delta T as well as the Delta T between dry and wet bulb ambient temperature. Increased Delta T for both internal and ambient external temperatures will result in higher energy savings using destratification. Further energy savings, above the predicted savings achieved in this software process, can be realised via the use of thermal destratification creating other energy saving opportunities but those are outside the scope of this report. These include; accelerated reuse of the chilled air captured by thermal buoyancy up under the ceiling post discharge, increase or decrease of thermal set points as a result of destratification and a range of other energy saving opportunities. It is important to note that in some cases energy savings of HVAC in summer can reach 35% but the overall yearly cooling only savings average has been considered in this report. Heating savings using destratification should be added to this percentage. Hourly Analysis Program v4.61 Page 1 of 43

2 The outcomes of this analysis are as follows:- City Energy Saving for 2C (%) Energy Saving for 4C (%) Energy Saving for 6C (%) Sydney Melbourne Brisbane Auckland Introduction The worldwide use of Airius Air Pear destratification fans has been proven to significantly reduce equipment energy consumption in heating environments where the hot air rises to the ceiling and causes the heating system to over deliver on a continual basis in winter. (Carbon Trust UK, BSRIA) Energy savings of 35% of the HVAC system energy have been regularly achieved in heating environments through the use of Airius Air Pear Thermal Equalizer air turbines. While this use of destratification is also applicable to southern hemisphere locales the impact and value of destratification on the HVAC energy use in warm to hot summer conditions has had minimal consideration or review to date. The intent of this report is to validate the premise that destratification will also significantly reduce cooling energy in HVAC systems using a fixed internal temperature set point of 23 Deg. C in summer and 20 Deg. C in winter via the use of the latest HVAC design and energy modelling software known as HAP (By Carrier). The outcomes of this report provide an average yearly energy saving prediction for cooling energy only. Further energy savings above those identified in this software analysis can be achieved by the inclusion of heating energy savings, adjustment of the set points to reflect improved cooling in summer due to increased air flow (Arens et al, 2010; Aynsley, 2009.) and other initiatives linked to the use of thermal destratification and air circulation. That work is outside the scope of this report. 3- Strategy In this study, transient simulations have been carried out using the Hourly Analysis Program (HAP) 2 Version 4.6, a powerful HVAC and energy analysis software programme designed by Carrier and used worldwide to undertake HVAC system design and related energy consumption analysis of the building and the HVAC system which is installed in that building. In this application it has been used to identify and verify the energy saving potential of the AIRIUS Air Pear Thermal Equalizer destratification and air circulation fans in a nominated building type. These simulations have been established for the following four southern hemisphere cities using specific dynamic climate data -Sydney, Melbourne, Brisbane and Auckland, New Zealand. 4- Methodology The use of software modelling has limitations and in this application it is utilised to mimic the impact of destratification and air circulation on the HVAC system in a medium sized (2000 sq. mts.) retail store. A range of assumptions are made around the store building fabric, internal loads etc. Please note that while changing the fabric loads etc. will improve the building s heating and cooling loads the impact of those types of changes on the value of destratification are minimal. The energy saving potential in this study has been considered as a function of cooling plant duty cycling. Building cooling loads as a result of increased or decreased insulation levels, glazing performance etc. is important only for sizing the cooling equipment capacity and has very limited impact on the value of destratification. A range of data around building fabric and internal heat loads were input into the model to provide the data used for analysis so as to assure the reader that the modelled building complies with the latest building code requirements around energy efficiency. Dynamic climate data utilised in the carrier HAP software provides the climatic information needed to provide modelling accuracy and relevance. The building is initially modelled using the nominated HVAC system (see below) then the software is rerun in the relevant climatic zone but with the destratification temperature differences reduced to zero. Hourly Analysis Program v4.61 Page 2 of 43

3 5- Airius Air Pear fans Airius Air Pears are an American designed and manufactured patented Thermal Equalizer air turbine fan that uses a unique rotor, stator and venturi throat design to propel large volumes of air gently in a non-turbulent manner over long distances. Their exclusive design allows them to propel the air in a narrow focused column, minimising air dispersion and turbulence. The narrow column air enables the units to effectively move air from floor to ceiling with minimal disturbance and maximum control over locations and efficacy of air flow. This is achieved with very low amounts of energy. The Airius Air Pear model 15 utilised in this study uses 15 watts of power at 240 volts. Working in concert together the units quickly destratify or circulate air in a space. 6- Case Study The case study is a commercial shopping space with a 4 metre high ceiling and a 2,000 square metre floor area. The number and size of Airius Air Pear units has been selected based upon calculations provided by Airius Oceania P/L. 15 off Model 15 Airius Air Pear units have been considered as the destratification source. Each unit consumes 15 watts of power at 50 HZ. The selected HVAC system for this building is a water-cooled chiller type which provides chilled water of 6 Deg. C for an air-handling (AHU) unit. The AHU fan is a Variable Air Volume (VAV) unit. An occupancy load of 200 people has been considered inside the building. (For more info please see the attached documents) All building fabric, lighting loads and HVAC systems for the different locations have been modeled under the 2013 NCC Section J energy efficiency protocols. Relevant and detailed climatic data for each location has been input into the facility and the examination is based on cooling periods only when cooling is required inside the building. 7- Temperature Differences Three temperature differences (floor to ceiling) of 2Deg. C, 4Deg. C and 6Deg. C have been considered for each city in the nominated space. 8- Occupation levels Occupation levels are considered as 200 persons in the space. One person per 10 sq. metres. 9- How Destratification Saves Energy in Warm Climates The energy saving potential using the destratification strategy is primarily due to the duty cycling of the cooling plant. By destratifying the space the return air temperature to the cooling system in summer is cooler and the preset internal temperatures are held constant for a longer period of time. This causes the chiller and compressors to shut down for a longer period during the occupied period of the day, start later and turn off earlier resulting in reduced energy savings. In a conditioned facility the higher the temperature difference between floor and ceiling the greater the energy savings using destratification. Different systems such as air cooled designs in different climates may result in larger energy savings. Additionally, the greater the difference between ambient dry and wet bulb temperatures results in larger energy savings. 10- Limitations The software doesn t examine other areas of energy savings or thermal comfort achieved with the use of Airius Air Pear fans such as:- Reduction and subsequent accelerated use of cold air captured at ceiling discharge level due to thermal buoyancy and heating of the chilled air. Air circulation using the Airius Air Pear fans optimises this energy discharge ensuring the chilled air is bought to the floor more quickly. This stops the over delivery of conditioned air. Removal of hot and cold spots in the space. Increased summer thermostat setting and decreased winter thermostat setting Reduced AHU and fan loads due to the air movement being provided by the Airius Air Pear units Reduced HVAC AHU energy and smaller duct design (less backpressure) if the Airius Air Pears are connected to the HVAC ducts and installed as a substitute powered ceiling register. Provision of air circulation creating comfort based evaporative cooling. Hourly Analysis Program v4.61 Page 3 of 43

4 11- Outcomes The energy saving potentials for these cities using this approach is as followings: City Energy Saving for 2C (%) Energy Saving for 4C (%) Energy Saving for 6C (%) Sydney Melbourne Brisbane Auckland Addendum No 1 Weather profiles for the aforementioned cities are as follows: Sydney Design Parameters: City Name... Sydney Location... Australia Latitude Deg. Longitude Deg. Elevation m Summer Design Dry-Bulb C Summer Coincident Wet-Bulb C Summer Daily Range K Winter Design Dry-Bulb C Winter Design Wet-Bulb C Atmospheric Clearness Number Average Ground Reflectance Soil Conductivity W/(m- K) Local Time Zone (GMT +/- N hours) hours Consider Daylight Savings Time... No Simulation Weather Data... Sydney (IWC) Current Data is Carrier Australia Design Cooling Months... October to March Design Day Maximum Solar Heat Gains Hourly Analysis Program v4.61 Page 4 of 43

5 (The MSHG values are expressed in W/m² ) Month N NNE NE ENE E ESE SE SSE S January February March April May June July August September October November December Month SSW SW WSW W WNW NW NNW HOR Mult January February March April May June July August September October November December Mult. = User-defined solar multiplier factor. Hourly Analysis Program v4.61 Page 5 of 43

6 Table 1. Descriptive Parameters: City... Sydney Location... Australia Type of Data... (IWC) Latitude Deg. Longitude Deg. Elevation m Local Time Zone (GMT +/- N hours) hours Average Ground Reflectance Table 2. Dry-Bulb Temperature Statistics ( C ): Month Absolute Average Average Average Absolute Maximum Maximum Minimum Minimum January February March April May June July August September October November December Hourly Analysis Program v4.61 Page 6 of 43

7 Table 3. Daily Solar Radiation Statistics: Daily Total Solar on Horizontal ( kj/m² ) Daily Clearness Number (dimensionless) Month Maximum Average Minimum Maximum Average Minimum January February March April May June July August September October November December Hourly Analysis Program v4.61 Page 7 of 43

8 Table 4. Time of Occurrence for Maximums and Minimums: Month Highest Dry-Bulb Lowest Dry-Bulb Maximum Total Minimum Total Temperature Temperature Solar Solar January Jan 12, 1200 Jan 18, 0900 Jan 2 Jan 16 February Feb 10, 1500 Feb 27, 0400 Feb 2 Feb 11 March Mar 28, 1400 Mar 9, 0600 Mar 3 Mar 31 April Apr 7, 1300 Apr 21, 0700 Apr 1 Apr 16 May May 6, 1500 May 18, 0600 May 4 May 30 June Jun 5, 1500 Jun 12, 0600 Jun 1 Jun 7 July Jul 23, 1500 Jul 27, 0700 Jul 30 Jul 2 August Aug 17, 1500 Aug 25, 0600 Aug 31 Aug 22 September Sep 30, 1200 Sep 11, 0600 Sep 28 Sep 9 October Oct 18, 1300 Oct 8, 0300 Oct 28 Oct 19 November Nov 3, 1500 Nov 18, 0600 Nov 17 Nov 1 December Dec 21, 1300 Dec 11, 0600 Dec 21 Dec 9 Table 5. Air System Data 1. General Details: Air System Name... HVAC System Equipment Type... Chilled Water AHU Air System Type... VAV Number of zones System Components: Ventilation Air Data: Airflow Control... Proportional Ventilation Sizing Method... Sum of Space OA Airflows Minimum Airflow... 0 % Unocc. Damper Position... Closed Damper Leak Rate... 0 % Outdoor Air CO2 Level ppm Central Cooling Data: Supply Air Temperature C Coil Bypass Factor Cooling Source... Chilled Water Schedule... JFM* * * * * * OND Capacity Control... Cycled or Staged Capacity - Fan On Supply Fan Data: Fan Type... Forward Curved Configuration... Draw-thru Fan Performance Pa Overall Efficiency % % Airflow Hourly Analysis Program v4.61 Page 8 of 43

9 % kw % Airflow % kw Duct System Data: Supply Duct Data: Duct Heat Gain... 2 % Duct Leakage... 2 % Return Duct or Plenum Data: Return Air Via... Ducted Return 3. Zone Components: Space Assignments: Zone 1: Zone 1 Space x1 Thermostats and Zone Data: Zone... All Cooling T-stat: Occ C Cooling T-stat: Unocc C Heating T-stat: Occ C Heating T-stat: Unocc C T-stat Throttling Range K Diversity Factor % Direct Exhaust Airflow L/s Direct Exhaust Fan kw kw Thermostat Schedule... Thermostat Unoccupied Cooling is... Not Available Supply Terminals Data: Zone... All Terminal Type... VAV box Minimum Airflow L/s Zone Heating Units: Zone... All Zone Heating Unit Type... None Zone Unit Heat Source... Hot Water Zone Heating Unit Schedule... JFMAMJJASOND 4. Sizing Data (Computer-Generated): System Sizing Data: Cooling Supply Temperature C Supply Fan Airflow L/s Ventilation Airflow L/s Hydronic Sizing Specifications: Chilled Water Delta-T K Hot Water Delta-T K Safety Factors: Cooling Sensible % Cooling Latent % Heating % Zone Sizing Data: Zone Airflow Sizing Method... Peak zone sensible load Space Airflow Sizing Method... Individual peak space loads Zone Supply Airflow Zone Htg Unit Reheat Coil - (L/s) (kw) (kw) (L/s) Equipment Data No Equipment Data required for this system. Hourly Analysis Program v4.61 Page 9 of 43

10 Table 6. Plant Information: Plant Name... Plant Plant Type... Chiller Plant Design Weather... Sydney, Australia 2. Cooling Plant Sizing Data: Maximum Plant Load kw Load occurs at... Jan 1800 m²/kw m²/kw Floor area served by plant m² 3. Coincident Air System Cooling Loads for Jan 1800 System Cooling Coil Load Air System Name Mult. ( kw ) HVAC System System loads are for coils whose cooling source is ' Chilled Water '. Hourly Analysis Program v4.61 Page 10 of 43

11 1. Plant Information: Plant Name... Plant Plant Type... Chiller Plant Design Weather... Sydney, Australia 2. Chiller Load Profiles from January to January : Hourly Analysis Program v4.61 Page 11 of 43

12 DESIGN MONTH: JANUARY OA TEMP TOTAL COOLING Hour ( C ) ( kw ) Total Ton-hrs Hourly Analysis Program v4.61 Page 12 of 43

13 Hourly Analysis Program v4.61 Page 13 of 43

14 Chiller Load (kw) Data for January Hour of Day Hourly Analysis Program v4.61 Page 14 of 43

15 Equipment Capacity Capacity Capacity Total Hours Capacity is Insufficient Insufficient Insufficient Total Hours with Sufficient by 0%-5% by 5%-10% by >10% with Unmet Equipment Month (hrs) (hrs) (hrs) (hrs) Loads Loads January February March April May June July August September October November December Total Table 7. (above) Plant Simulation Table 8. Space Input Data Space 1. General Details: Floor Area m² Avg. Ceiling Height m Building Weight kg/m² 1.1. OA Ventilation Requirements: Space Usage... User-Defined OA Requirement L/s/person OA Requirement L/s Space Usage Defaults... ASHRAE Std Internals: 2.1. Overhead Lighting: Fixture Type... Recessed (Unvented) Hourly Analysis Program v4.61 Page 15 of 43

16 Wattage W/m² Ballast Multiplier Schedule... Lighting Schedule 2.4. People: Occupancy People Activity Level... Medium Work Sensible W/person Latent W/person Schedule... People Schedule 2.2. Task Lighting: Wattage W/m² Schedule... None 2.5. Miscellaneous Loads: Sensible W Schedule... Airius Schedule Latent... 0 W Schedule... None Hourly Analysis Program v4.61 Page 16 of 43

17 2.3. Electrical Equipment: Wattage W/m² Schedule... Lighting Schedule 3. Walls, Windows, Doors: Exp. Wall Gross Area (m²) Window 1 Qty. Window 2 Qty. Door 1 Qty. S E Construction Types for Exposure S Wall Type... Wall Assembly 1st Window Type... Window Construction Types for Exposure E Wall Type... Wall Assembly 1st Window Type... Window 2 4. Roofs, Skylights: (No Roof or Skylight data). 5. Infiltration: Design Cooling ACH Design Heating ACH Energy Analysis ACH Infiltration occurs at all hours. 6. Floors: Type... Floor Above Conditioned Space (No additional input required for this floor type). 7. Partitions: (No partition data). Hourly Analysis Program v4.61 Page 17 of 43

18 Table 9. System Design Report Air System Information Air System Name... HVAC System Equipment Class... CW AHU Air System Type... VAV Number of zones... 1 Floor Area m² Location... Sydney, Australia Sizing Calculation Information Zone and Space Sizing Method: Zone L/s... Peak zone sensible load Space L/s... Individual peak space loads Calculation Months... Oct to Mar Sizing Data... Calculated Central Cooling Coil Sizing Data Total coil load kw Sensible coil load kw Coil L/s at Jan L/s Max block L/s at Jan L/s Sum of peak zone L/s L/s Sensible heat ratio m²/kw W/m² Water 5.6 K rise L/s Load occurs at... Jan 1800 OA DB / WB / 22.6 C Entering DB / WB / 19.0 C Leaving DB / WB / 15.1 C Coil ADP C Bypass Factor Resulting RH % Design supply temp C Zone T-stat Check... 1 of 1 OK Max zone temperature deviation K Supply Fan Sizing Data Actual max L/s at Jan L/s Standard L/s L/s Actual max L/(s-m²) L/(s-m²) Fan motor BHP BHP Fan motor kw kw Fan static Pa Hourly Analysis Program v4.61 Page 18 of 43

19 Outdoor Ventilation Air Data Design airflow L/s L/s L/s/person L/s/person L/(s-m²) L/(s-m²) Hourly Analysis Program v4.61 Page 19 of 43

20 Table 10. System Design Report 2 DESIGN MONTH: JANUARY CENTRAL CENTRAL CENTRAL ZONE OA SUPPLY COOLING COOLING HEATING PRECOOL PREHEAT TERMINAL TERMINAL HEATING TEMP AIRFLOW SENSIBLE TOTAL COIL COIL COIL COOLING HEATING UNIT Hour ( C) (L/s) (kw) (kw) (kw) (kw) (kw) (kw) (kw) (kw) Hourly Analysis Program v4.61 Page 20 of 43

21 Load ( kw ) Data for January Total Cooling Total Heating Hour of Day Hourly Analysis Program v4.61 Page 21 of 43

22 Table 11. System Design Report 3 ZONE: Zone 1 DESIGN MONTH: JANUARY ZONE TERMINAL TERMINAL ZONE OA ZONE ZONE SENSIBLE ZONE COOLING HEATING HEATING TEMP TEMP RH AIRFLOW LOAD COND COIL COIL UNIT Hour ( C) ( C) (%) (L/s) (W) (W) (W) (W) (W) Hourly Analysis Program v4.61 Page 22 of 43

23 W Zone: Zone 1 Data for January 140K Zone Sensible Zone Conditioning 120K 100K 80K 60K 40K 20K Hour of Day Hourly Analysis Program v4.61 Page 23 of 43

24 Addendum No 2. Melbourne Design Parameters: City Name... Melbourne Location... Australia Latitude Deg. Longitude Deg. Elevation m Summer Design Dry-Bulb C Summer Coincident Wet-Bulb C Summer Daily Range K Winter Design Dry-Bulb C Winter Design Wet-Bulb C Atmospheric Clearness Number Average Ground Reflectance Soil Conductivity W/(m- K) Local Time Zone (GMT +/- N hours) hours Consider Daylight Savings Time... No Simulation Weather Data... Melbourne (IWC) Current Data is Carrier Australia Design Cooling Months... October to March Hourly Analysis Program v4.61 Page 24 of 43

25 Design Day Maximum Solar Heat Gains (The MSHG values are expressed in W/m² ) Hourly Analysis Program v4.61 Page 25 of 43

26 Month N NNE NE ENE E ESE SE SSE S January February March April May June July August September October November December Month SSW SW WSW W WNW NW NNW HOR Mult January February March April May June July August September October November December Mult. = User-defined solar multiplier factor. Hourly Analysis Program v4.61 Page 26 of 43

27 Table 1. Descriptive Parameters: City... Melbourne Location... Australia Type of Data... (IWC) Latitude Deg. Longitude Deg. Elevation m Local Time Zone (GMT +/- N hours) hours Average Ground Reflectance Table 2. Dry-Bulb Temperature Statistics ( C ): Month Absolute Average Average Average Absolute Maximum Maximum Minimum Minimum January February March April May June July August September October November December Hourly Analysis Program v4.61 Page 27 of 43

28 Table 3. Daily Solar Radiation Statistics: Daily Total Solar on Horizontal ( kj/m² ) Daily Clearness Number (dimensionless) Month Maximum Average Minimum Maximum Average Minimum January February March April May June July August September October November December Hourly Analysis Program v4.61 Page 28 of 43

29 Table 4. Time of Occurrence for Maximums and Minimums: Month Highest Dry-Bulb Lowest Dry-Bulb Maximum Total Minimum Total Temperature Temperature Solar Solar January Jan 14, 1600 Jan 23, 0500 Jan 14 Jan 1 February Feb 3, 1600 Feb 21, 0500 Feb 2 Feb 8 March Mar 24, 1400 Mar 13, 0300 Mar 13 Mar 18 April Apr 10, 1500 Apr 23, 0600 Apr 9 Apr 24 May May 19, 1500 May 22, 0700 May 2 May 31 June Jun 1, 1600 Jun 21, 0900 Jun 29 Jun 26 July Jul 28, 1500 Jul 13, 0600 Jul 25 Jul 4 August Aug 26, 1400 Aug 18, 0600 Aug 31 Aug 6 September Sep 20, 1600 Sep 8, 0500 Sep 30 Sep 12 October Oct 26, 1800 Oct 18, 0600 Oct 24 Oct 27 November Nov 25, 1500 Nov 11, 0200 Nov 27 Nov 6 December Dec 9, 1300 Dec 2, 0500 Dec 8 Dec 16 Hourly Analysis Program v4.61 Page 29 of 43

30 4.3 Brisbane Design Parameters: City Name... Brisbane Location... Australia Latitude Deg. Longitude Deg. Elevation m Summer Design Dry-Bulb C Summer Coincident Wet-Bulb C Summer Daily Range K Winter Design Dry-Bulb C Winter Design Wet-Bulb C Atmospheric Clearness Number Average Ground Reflectance Soil Conductivity W/(m- K) Local Time Zone (GMT +/- N hours) hours Consider Daylight Savings Time... No Simulation Weather Data... Brisbane (IWC) Current Data is Carrier Australia Design Cooling Months... October to March Hourly Analysis Program v4.61 Page 30 of 43

31 Design Day Maximum Solar Heat Gains (The MSHG values are expressed in W/m² ) Hourly Analysis Program v4.61 Page 31 of 43

32 Month N NNE NE ENE E ESE SE SSE S January February March April May June July August September October November December Month SSW SW WSW W WNW NW NNW HOR Mult January February March April May June July August September October November December Mult. = User-defined solar multiplier factor. Hourly Analysis Program v4.61 Page 32 of 43

33 Table 1. Descriptive Parameters: City... Brisbane Location... Australia Type of Data... (IWC) Latitude Deg. Longitude Deg. Elevation m Local Time Zone (GMT +/- N hours) hours Average Ground Reflectance Table 2. Dry-Bulb Temperature Statistics ( C ): Month Absolute Average Average Average Absolute Maximum Maximum Minimum Minimum January February March April May June July August September October November December Hourly Analysis Program v4.61 Page 33 of 43

34 Table 3. Daily Solar Radiation Statistics: Daily Total Solar on Horizontal ( kj/m² ) Daily Clearness Number (dimensionless) Month Maximum Average Minimum Maximum Average Minimum January February March April May June July August September October November December Hourly Analysis Program v4.61 Page 34 of 43

35 Table 4. Time of Occurrence for Maximums and Minimums: Month Highest Dry-Bulb Lowest Dry-Bulb Maximum Total Minimum Total Temperature Temperature Solar Solar January Jan 30, 1300 Jan 3, 0300 Jan 11 Jan 2 February Feb 18, 1200 Feb 3, 0400 Feb 1 Feb 25 March Mar 21, 1300 Mar 19, 0500 Mar 5 Mar 16 April Apr 1, 1300 Apr 13, 0600 Apr 1 Apr 23 May May 3, 1100 May 28, 0700 May 2 May 15 June Jun 18, 1400 Jun 21, 0700 Jun 8 Jun 2 July Jul 31, 1400 Jul 13, 0100 Jul 31 Jul 18 August Aug 22, 1100 Aug 8, 0100 Aug 31 Aug 6 September Sep 17, 1300 Sep 19, 0600 Sep 25 Sep 11 October Oct 27, 1500 Oct 6, 0300 Oct 27 Oct 14 November Nov 13, 1300 Nov 24, 0500 Nov 24 Nov 30 December Dec 6, 1300 Dec 1, 0500 Dec 1 Dec 13 Hourly Analysis Program v4.61 Page 35 of 43

36 4.4 Auckland Design Parameters: City Name... Auckland Location... New Zealand Latitude Deg. Longitude Deg. Elevation m Summer Design Dry-Bulb C Summer Coincident Wet-Bulb C Summer Daily Range K Winter Design Dry-Bulb C Winter Design Wet-Bulb C Atmospheric Clearness Number Average Ground Reflectance Soil Conductivity W/(m- K) Local Time Zone (GMT +/- N hours) hours Consider Daylight Savings Time... No Simulation Weather Data... Auckland (TMY) Current Data is NIWAR Design Cooling Months... October to March Hourly Analysis Program v4.61 Page 36 of 43

37 Design Day Maximum Solar Heat Gains (The MSHG values are expressed in W/m² ) Hourly Analysis Program v4.61 Page 37 of 43

38 Month N NNE NE ENE E ESE SE SSE S January February March April May June July August September October November December Month SSW SW WSW W WNW NW NNW HOR Mult January February March April May June July August September October November December Mult. = User-defined solar multiplier factor. Hourly Analysis Program v4.61 Page 38 of 43

39 Table 1. Descriptive Parameters: City... Auckland Location... New Zealand Type of Data... (TMY) Latitude Deg. Longitude Deg. Elevation m Local Time Zone (GMT +/- N hours) hours Average Ground Reflectance Table 2. Dry-Bulb Temperature Statistics ( C ): Month Absolute Average Average Average Absolute Maximum Maximum Minimum Minimum January February March April May June July August September October November December Hourly Analysis Program v4.61 Page 39 of 43

40 Table 3. Daily Solar Radiation Statistics: Daily Total Solar on Horizontal ( kj/m² ) Daily Clearness Number (dimensionless) Month Maximum Average Minimum Maximum Average Minimum January February March April May June July August September October November December Hourly Analysis Program v4.61 Page 40 of 43

41 Table 4. Time of Occurrence for Maximums and Minimums: Month Highest Dry-Bulb Lowest Dry-Bulb Maximum Total Minimum Total Temperature Temperature Solar Solar January Jan 11, 1400 Jan 3, 0400 Jan 5 Jan 17 February Feb 16, 1500 Feb 28, 1900 Feb 8 Feb 17 March Mar 3, 1300 Mar 21, 0500 Mar 3 Mar 7 April Apr 2, 1300 Apr 30, 2300 Apr 2 Apr 3 May May 3, 1300 May 30, 0600 May 2 May 26 June Jun 2, 1200 Jun 8, 0500 Jun 16 Jun 19 July Jul 22, 1200 Jul 20, 0300 Jul 31 Jul 28 August Aug 23, 1400 Aug 31, 0500 Aug 31 Aug 16 September Sep 2, 1300 Sep 5, 0500 Sep 23 Sep 18 October Oct 30, 1500 Oct 22, 0400 Oct 27 Oct 18 November Nov 6, 1300 Nov 4, 0500 Nov 29 Nov 14 December Dec 20, 1300 Dec 3, 0300 Dec 3 Dec Conclusions The outcomes from this report which utilised the latest software (which was conducted by an experienced and well recognized mechanical engineer and PHD student in HVAC design and operation) indicate significant savings can be achieved through the use of thermal destratification and air circulation using Airius Air Pear air turbines in temperate and sub tropical climates. With savings of a minimum of 10.6%- 14% in these climates thermal equalisation can significantly reduce energy use and improve thermal comfort. The low energy consumption of Airius Air Pear fans and their specific design ensures the units achieve destratification quickly and cost effectively, resulting in optimised HVAC outcomes and energy savings. In addition even greater savings can be recognised by the addition of a range of energy savings outcomes achieved by the use of destratification that are not included in this modelling exercise. Hourly Analysis Program v4.61 Page 41 of 43

42 1.The Author Vahid Vakiloroaya Vahid has modeled for energy savings and air conditioning design over 150 buildings across Australia using this HAP software. He is an experienced mechanical engineer designing a range of air conditioning systems. EDUCATION 2010/Present; PhD School of Electrical, Mechanical and Mechatronic Systems, University of Technology, Sydney, Australia Bachelor of Science in Mechanical Engineering Hons (1st Class), Iran EMPLOYMENT 2013 /Present Chief Executive Officer -Green HVAC Solution Sydney, Australia HVAC Designer (Part Time) A1Best Air Conditioning Services Pty Ltd Sydney, Australia Managing Director ASA; Tehran, Iran HVAC Design Manager Sabalan; Tehran, Iran HVAC Design Engineer HITACHI; Tehran, Iran Awards of NASSCOM Australia Innovation Student Awards 2013, Innovative Hybrid Design of an Energy Efficient Solar Assisted Air Conditioner Using Supervisory Programmable Logic Controller. Winner of UTS Annual Green Hero Award 2013 Winner of UTS Research Showcase Innovation Award 2013 Highly Commended Consensus Innovation Awards 2013, Ultra Cooler. Engineer Australia Excellence Awards, 2013 Finalist, IEAust, Development of a New Eco Friendly and Energy Efficient Solar Powered Single Effect Hot Water Absorption Air Conditioning System. TRAILBLAZER 2012 Finalist, UTS, Uniquest, Davies Collision Cave, Fisher Adams Kelly. Winner of the Australian Postgraduate Award (APA) by the Department of Innovation, Industry Science and Research in conjunction with Australian Universities, Best Practical HVAC Engineer Award 2005, Hitachi Co. Hourly Analysis Program v4.61 Page 42 of 43

43 Book Chapters V. Vakiloroaya, J. Madadnia, Cooling Coil Design Improvement for HVAC Energy Savings and Comfort Enhancement, Sustainability in Energy and Buildings, Springer Berlin Heidelberg, Chapter 85, , Journal Publications Author of 8 highly ranked international journal papers (See the attached materials) Conference Publications Author of 16 international conference papers Book Publications Author of 10 books in field of HVAC& (See the attached materials) Patents Name of Invention: Solar Coolant System with the use of Adsorption Process, Invention Registry book No.: 31370, Declaration Registry book No.: , Date of Registration: April 05, Name of Invention: Intelligent Deodorize with the Use of Forward Filtration, Invention Registry book No.: 35848, Declaration Registry book No.: , Date of Registration: February 22, Vahid Vakiloroaya, A Novel Cost Effective Chilled Water Direct Evaporative Cooling System, Number: DISC UTS , Institution: University of Technology, Sydney. Vahid Vakiloroaya, Energy Efficient Solar Assisted Air Conditioner Using New Discharge By Pass Line, Number: DISC UTS , Institution: University of Technology, Sydney. 2. Carrier HAP Software Carrier's Hourly Analysis Program is two powerful tools in one package. HAP provides versatile features for designing HVAC systems for commercial buildings. It also offers powerful energy analysis capabilities for comparing energy consumption and operating costs of design alternatives. By combining both tools in one package significant time savings are achieved. Input data and results from system design calculations can be used directly in energy studies. Carrier web site, Accessed References A. Arens et al. 2009: Moving Air for Comfort ASHRAE, B. Aynsley, R; 2007: How Air Movement Saves Energy in Indoor Environments ; Ecolibrium, 2007; AIRAH. C. BSRIA; Hourly Analysis Program v4.61 Page 43 of 43