|
Typical Design |
85 Ambient | |||||||||||||||||
| Tonnage | # of Units | Compressor 1 | Compressor 2 | Condenser Fan | Supply Fan | Unit FLA | AirBoss FLA | Unit Total Amps | kW | kw/hr | ||||||||
| 25 | 4 | 18.60 | 18.60 | 5.00 | 6.30 | 48.50 | N/A | 194.00 | 89.24 | 16.36 | ||||||||
| 20 | 6 | 20.00 | 13.20 | 5.00 | 4.93 | 43.13 | N/A | 258.78 | 119.04 | 21.82 | ||||||||
| Total | 220 | 10 | 452.78 | 208.28 | 38.18 | |||||||||||||
Table 7. Conventional system energy usage.
|
AirBoss Design |
85 Ambient | |||||||||||
| Tonnage | # of Units | Compressor 1 | Compressor 2 | Condenser Fan | Supply Fan | Unit FLA | AirBoss FLA | Unit Total Amps | kW | kw/hr | ||
| 25 | 5 | 18.60 | 18.60 | 5.00 | 6.89 | 49.09 | 6.65 | 245.45 | 112.91 | 20.70 | ||
| 20 | 3 | 20.00 | 13.20 | 5.00 | 3.10 | 41.30 | 3.99 | 123.90 | 56.99 | 10.45 | ||
| Total | 185.0 | 8 | 10.64 | 369.35 | 169.90 | 36.04 | ||||||
Table 8. Conventional system energy usage.
Another simulation was run for a 115 ton part load day and the energy saving was calculated to be 5% less for the AirBoss system. Please refer to the AirBoss presentation for the results and energy analysis for this simulation.
Heating Analysis
For high-ceiling open interior facilities, the roof surface is the largest source of heat loss. The amount of heat loss is calculated using Equation 2.
qr=U×A×∆tr
where,
qr = Heat loss through the roof (Btu/hr)
U = Average heat transfer coefficient for the roof (Btu/hr·ft2·°F)
A = Roof area (ft2)
∆tr= Difference of the indoor roof temperature and outdoor temperature (°F)
Based on the equation, the heat loss through the roof can be reduced by decreasing the indoor temperature. Using AirBoss, this can be accomplished by destratification. A conventional system allows heat from the space to rise and increases the indoor temperature at the roof. To determine the indoor temperature at the roof for both systems, simulations with Solidworks® 2016 were performed. The space setpoint was set at 75° with the design parameters in Table 9.
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