Sacramento

Seattle

Climate Zone

Los Angeles

	Nominal Tons								Annual Savings
	5	10	20	35	75	125	175	210
Atlanta	$242	$465	$884	$1,562	$3,281	$5,218	$7,214	$8,612	19%
Chicago	$228	$431	$801	$1,422	$2,964	$4,678	$6,429	$7,655	19%
Houston	$278	$544	$1,058	$1,861	$3,946	$6,442	$8,958	$10,719	17%
Los Angeles	$46	$91	$177	$311	$662	$1,088	$1,516	$1,816	5%
Miami	$394	$769	$1,493	$2,628	$5,569	$9,089	$12,635	$15,117	21%
Minneapolis	$244	$461	$856	$1,518	$3,162	$4,980	$6,840	$8,142	18%
New York	$212	$401	$748	$1,326	$2,769	$4,383	$6,030	$7,182	19%
Sacramento	$163	$306	$562	$999	$2,073	$3,242	$4,439	$5,278	12%
Seattle	$160	$300	$548	$975	$2,020	$3,146	$4,303	$5,113	20%
Tulsa	$271	$520	$981	$1,735	$3,640	$5,818	$8,032	$9,582	16%
Estimated Savings From AAON Rigid Polyurethane Foam Cabinet

Tulsa

Houston

Minneapolis

Chicago

Miami

Atlanta

New York

Executive Summary

Lost energy is lost money. As utility costs increase, poor insulation and poor air seals will result in more wasted heating and cooling dollars. Architects, engineers, and owners know that utilizing quality materials and construction techniques will minimize losses in the building. For instance, the ASHRAE standard 90.1-2007 requires all above deck insulation in climate zones 2 through 8 to have a minimum thermal insulating value of R-20 and climate zone 1 to have a minimum R-13. Likewise, ASHRAE 90.1-2007 requires sealing, caulking, gasketing, or weather-stripping of various areas of the building envelope. Like the building, the Heating Ventilating and Air Conditioning (HVAC) cabinet can lose energy through poor insulation and poor air seals. Like the building, the HVAC cabinet should have requirements for minimum insulation and air seals. An HVAC cabinet can become a pathway for heating and cooling energy to enter or escape from a building.

Conventional HVAC cabinets incorporate narrow one-half to one inch fiberglass insulation attached to a single wall of galvanized sheet metal. Thermal resistance values for fiberglass panels are typically less than R-2. The R value of a fiberglass panel is reduced even more without a thermal break between the HVAC tunnel air temperature and the outside ambient air temperature. Due to the lack of published standards on the HVAC cabinet air leakage, air infiltration percentages are not available. Although air infiltration rates may vary between manufacturers, 4% of total air flow at 1 inch of internal negative static water pressure can be used as a representative leakage rate.

AAON uses a different approach. AAON manufactures a double wall Rigid Polyurethane Foam panel with thermal breaks for the HVAC cabinet’s air tunnel. By implementing a composite structure, the foam and sheet metal are combined into a cabinet with improved insulation and air seals. The AAON two inch wall panel has a thermal resistance of R-13. This is equivalent to using panels with thermal breaks and four inch thick, 0.5 pound per square foot fiberglass. This would commonly be found on more costly custom equipment. All AAON panels incorporate thermal breaks to separate the HVAC tunnel air temperature with the outside ambient air temperature. Cabinet testing has shown the air infiltration rate is below 1.5% of total air flow at 1 inch of internal negative static water pressure.

The increased insulation of an AAON cabinet will reduce the undesired heating and cooling of the cabinet airstream due to the outside ambient temperature. By improving air tightness, the AAON cabinet reduces any load created from the outside air. One benefit of an AAON cabinet is a reduction in owner’s operating cost up to 21% each year.

The utilization of the AAON foam panel design has improved:

• Operating Costs
• Thermal Resistance and Breaks
• Air Seals
• Rigidity
• Impact Resistance
• Maintainability
• Indoor Air Quality
• Equipment Lifetime

The conventional fiberglass insulated cabinet creates a thermal bridge for heating and cooling energy between a building’s interior and the outside environment. The AAON Rigid Polyurethane Foam cabinet saves cooling and heating energy through improved insulation and air seals. This reduces the energy lost to the environment and reduces the building owner’s operating cost. Saved energy is saved money.

Rigid Polyurethane Foam Panel Design

The manufacture of AAON Rigid Polyurethane Foam implements cutting edge technology. Low viscosity polyurethane liquid is injected into a galvanized steel casing with integrated thermal breaks. As the liquid foam fills the casing, trapped air escapes through designed openings. After the casing is evacuated of all air, the polyurethane liquid is cured through a pressurized baking process. The resulting closed cell foam core has a density of two pounds per cubic foot. This composite design results in improved operating costs, thermal resistance and breaks, air seals, rigidity, impact resistance, maintainability, indoor air quality, and equipment lifetime.

Thermal Resistance

The one-half to one inch thick fiberglass panels used in conventional HVAC cabinets will have a thermal resistance of R-0.5 to
R-3.5. AAON Rigid Foam Panels utilize two inch thick walls and a two and one half inch thick roof. The foam panels have a thermal resistance of R-13 and R-16 respectively. This is equivalent to four inches of fiberglass commonly found in more costly custom HVAC cabinets.

Thermal Break

Conventional fiberglass cabinets have sheet metal panels that have no thermal break, creating a direct pathway from the cabinet’s interior to the atmosphere. The published
R-value of fiberglass insulated cabinets is much less because of this thermal bridge.

Sheet Metal Thermal Bridge Fiberglass Insulation Conductive Pathway Only External Wall

Conventional Fiberglass Panels

AAON incorporates a thermal break in all its foam panels. This break disconnects the conductive path between the cabinet interior and the atmosphere, meaning R-13 is the actual thermal resistance of the two inch panels.

Thermal Break Polyurethane Injected Foam Insulating Gasket Galvanized Steel Internal and External Walls

AAON Rigid Polyurethane Foam Panels

Air Seals

Fiberglass cabinets have no seal, or the seal is cut in the corners. Without a seal, the tolerance difference between the opening and the door will lead to increased infiltration. Likewise, seals joined at the corners allow ambient air into the airstream through this gap. One reason for the low infiltration rate in the AAON cabinet is the continuous door sealing. On doorways and openings into the air stream, AAON uses a continuous seal to prevent leakage at corner joints. The continuous seals reduce the infiltration rate on AAON cabinets.

Continuous Bulb-Seal Door Jamb Thermal Break

AAON Rigid Polyurethane Foam Panels

Rigidity

The laminate construction of the polyurethane foam and galvanized steel increases the panel rigidity. This construction yields a light weight panel, while still providing an exceptional L/240 deflection ratio at eight inches of static pressure. For example, a panel five feet long subjected to eight inches of static pressure would have a maximum deflection of one-quarter of an inch. AAON standard design exceeds custom HVAC cabinets that have panels designed to L/200 deflection. The increased rigidity is another reason for the low infiltration rate on AAON cabinets.

Other HVAC cabinets may claim heavier gauge sheet metal makes a panel rigid. This statement is misleading; the rigidity of an object is not just based on material thickness. Rigidity is also affected by the geometry of the panel and the method of cabinet assembly.

Impact Resistance

An AAON Rigid Polyurethane Foam cabinet is remarkably impact resistant. The addition of the foam increases the impact resistance of the panels. In a recent product test, the AAON cabinet was able to withstand two direct hits from an 8 foot long 2” x 4” traveling at over 35 miles per hour. Picture 1 shows no reduction of cabinet integrity after two strikes in the same place.

Maintainability

One other advantage to the AAON Rigid Polyurethane Foam panel is the internal protective barrier. The conventional fiberglass panel is exposed to condensation and particulates in the air stream. By using a galvanized internal barrier with a thermal break, the AAON panel is washable and resists moisture formation. In climates where air streams may contain salt, the ability to clean the salty condensate will prevent corrosive damage.

Indoor Air Quality

Two components in the Rigid Polyurethane Foam panel inhibit microbial growth. The thermal break in the panel will inhibit moisture formation on the internal barrier surface, while the closed cell foam will resist moisture absorption and microbial growth. Compared to conventional fiberglass cabinets, the AAON cabinet promotes a higher indoor air quality.

Equipment Lifetime

Another important factor in the HVAC cabinet design is the heating and cooling savings over the entire equipment lifetime. As a fiberglass cabinet ages, the fiberglass insulation peels away and sags off of the sheet metal structure. This will decrease the fiberglass cabinet thermal resistance. The AAON HVAC cabinet is designed to maintain a consistent thermal resistance. Over the equipment lifetime, the AAON cabinet would increase its savings compared to the fiberglass cabinet.

Operating Cost

The following examples quantify the savings a building owner can experience with an AAON Rigid Polyurethane Foam cabinet. A simplified 1 foot cube will be used to compare the additional cooling load between a fiberglass insulation design and an AAON design. After the simplified cube is explained, the same calculations are performed on typical HVAC cabinet sizes. Then additional cooling infiltration loads between the fiberglass insulated cabinet and the AAON cabinet will be compared. Similarly, the additional heating load through insulation and infiltration will be compared. At the end, various cities with different climates will be presented with the cooling, heating, and total savings.

Calculation Considerations

In a laboratory setting, a test was performed comparing a double wall, 1 inch thick fiberglass cabinet to a Rigid Polyurethane Foam AAON cabinet. When internal negative static pressure was equal to 1 inch water gauge, the fiberglass design allowed 4% ambient air flow to enter the cabinet. The fiberglass unit incorporated seals for all access panels, grommets for copper tubing (i.e. condenser coil or compressor compartment interface with air tunnel), and gaskets in the electrical access points. If a cabinet did not incorporate these design features, the expected infiltration percentage could easily be 6% or more. The AAON Rigid Polyurethane Foam cabinet allowed only 1.5% air flow to enter the cabinet at the same 1 inch internal negative static water pressure.

Testing of the two designs indicates the percentage infiltration between the designs increases disproportionately as internal static pressure increases. Figure 1 shows a 63% difference between the fiberglass design and the AAON design at 1 inch internal static pressure, while the difference at 3 inch internal static is 70%. This study shows that heating and cooling load calculations should use infiltration rates of 4% or more for the fiberglass design and 1.5% for the AAON Rigid Polyurethane Foam design.

Increased Cooling Load (Insulation)

If the outside ambient is warmer than the HVAC tunnel air stream, conductive heat transfer will occur through the HVAC cabinet and increase the cooling load. The conductive energy entering the HVAC cabinet is proportional to the thermal resistance of the panels.

In this example, the R value for a one-half to one inch thick, 0.5 pound per square foot fiberglass cabinet is 2. For the initial calculations, a one foot cube will have a 55ºF supply air and an 80ºF return air equally distributed in the air tunnel. The supply side roof and return side roof surface areas’ are each 0.5 ft2.

The initial outside ambient temperatures will be for Atlanta, Georgia and will come from the ASHRAE “Bin and Degree Hour Weather Data for Simplified Energy Calculations.” Table 1 shows the dry bulb temperatures from 67ºF to 97ºF. These temperatures and the hours at each condition will be used to total the year’s increased cooling load.

Solar radiation can also increase the surface temperature of the HVAC cabinet. The solar radiation calculations have been excluded from these conductive heat transfer calculations since daylight, solar altitude, cloud index, shading, etc. require detailed site information for proper modeling.

By inputting the supply side temperature difference, roof surface area, and roof R-value into the conductive heat transfer equation, the increased cooling load imposed through the supply side roof is found.

Similarly, the extra cooling load through the return side roof is found by changing the air stream temperature.

The fiberglass panels will allow heating of the air stream 10.50 Btu/hr through the supply roof and 4.25 Btu/hr through the return roof. By repeating the process for the entire cube, 73.75 Btu/hr of increased cooling is required when the outside dry bulb temperature is 97ºF. Similarly, the process can be repeated for a cube using AAON Rigid Polyurethane Foam design of R-13 walls and R-16 roofs. The entire AAON cube would only require 10.92 Btu/hr of additional cooling. Table 2 gives the detailed values for the entire cube. By multiplying the whole cube’s conductive heat transfer by 9 hours, the year’s increased cooling load at the 97ºF condition is 664 Btu’s for the fiberglass insulated cube. The AAON cube only requires an additional 98 Btu’s. The AAON design has decreased the extra cooling load by 85%.

Considering all cooling conditions between 67ºF and 97ºF, the increased cooling load required for the fiberglass and the AAON design is shown in Table 3. At 67ºF the additional cooling required from the heat transfer into the supply section is less than the heat transfer out of the return section to the outside ambient. At this condition, the net thermal transfer is negative.

As Table 3 shows, the difference between the fiberglass design and the AAON Rigid Polyurethane Foam design is 59,021 Btu’s at 100% occupancy and 29,511 Btu’s at 50% occupancy. Compared to the fiberglass insulation design, the AAON Rigid Polyurethane Foam design decreases superfluous cooling loads by 85%.

Figure 2 reinforces the results from Table 3. The increased cooling load through the fiberglass insulation design is considerably higher than the AAON Rigid Polyurethane Foam design.

Now that the calculations with a model cube are complete, the same calculations are performed with the approximate HVAC cabinet sizes and tons as indicated in Table 4.

Figure 3 gives a good indication of the increased cooling load based on the various cabinet sizes. At every cabinet size, the AAON design saves cooling energy.

Increased Cooling Load (Infiltration)

At 1 inch negative internal static water pressure, 4% infiltration enters the premier fiberglass cabinets. This means that 4% of the air flow can enter the HVAC cabinet and create an additional load. The additional 4% air flow is significant because of the sensible and latent load added to the system. For instance, a 10 ton unit with an estimated 4,000 cubic feet per minute (cfm) would have 160 cfm of infiltration. Using Atlanta, Georgia bin data, 97ºF (Dry Bulb) and 75.67ºF (Wet Bulb), the air density is 0.0696 lb/ft3 with an enthalpy of 39.77 Btu/lb. The supply air enthalpy will be 23.22 Btu/lb at 55ºF.

As the calculation shows, the additional cooling required due to infiltration is 11,058 Btu/hr. At the 97ºF conditions, the 10 ton unit can have an additional 0.92 tons of cooling required due to infiltration. The Atlanta bin data shows 9 hours of this condition each year. During these 9 hours, the infiltration causes 8.3 ton-hr of lost energy. These 9 hours would require an additional 99,522 Btu’s of cooling. Table 5 shows the losses for dry bulb temperatures 67 ºF and higher.

Each year 24,315,367 Btu’s of additional cooling is required because of the fiberglass cabinet’s infiltration rate. The fiberglass cabinet requires an additional 2,026 ton-hr of cooling each year. By conservatively estimating that the building is only occupied for 50% of those temperatures gives an additional cooling requirement of 12,157,683 Btu’s, or 1,013 ton•hr, each year.

Now, consider the additional cooling required when a cabinet only has 1.5% of air flow infiltrating. At 50% occupancy, the AAON cabinet would only require an additional 4,559,131 Btu’s, or 380 ton-hr, each year. The low infiltration rate from an AAON Rigid Polyurethane Foam cabinet reduces this superfluous cooling load by 63%.

Total Increased Cooling Load

The insulation losses and infiltration losses for temperatures at or above 67ºF can be summed to yield each year’s increased cooling load. To compare the increased cooling loads for each cabinet size, see Figure 4.

The lower resistance insulation combined with the high infiltration rate can dramatically increase the cooling load on an HVAC unit. For instance, operating a10 ton fiberglass HVAC cabinet at 50% occupancy could require an additional 13,072,275 Btu’s of cooling each year in Atlanta, Georgia. Table 6 provides a sample calculation for yearly increased cooling load of a building with twenty 10 ton units.

A twenty unit office building using 10 ton fiberglass cabinets could have 261,445,500 Btu’s of increased cooling due to the fiberglass insulated cabinet’s lower resistance insulation and higher infiltration rate. At $0.08 a kWh, a building owner with these fiberglass HVAC cabinets is wasting about $6,128 each year. An equal size AAON cabinet would require about $2,200 each year for increased cooling loads. If utility costs are $0.12 a kWh, the fiberglass cabinet uses an additional $9,192 for cooling, while the AAON cabinet only uses an additional $3,300. A building owner with the AAON designed HVAC cabinet could be saving $5,892 each year in cooling costs.

Increased Heating Load (Insulation)

If the outside ambient is cooler than the HVAC tunnel air stream, conductive heat transfer will occur through the HVAC cabinet and increase the heating load. The conductive energy leaving the HVAC cabinet is proportional to the thermal resistance of the panels.

With one-half to one inch thick, 0.5 pound per square foot insulation, the fiberglass cube’s roof has an R value of 2. The one foot cube will have 85ºF supply air and 75ºF return air equally distributed in the air tunnel. The supply side roof and return side roof surface areas’ are 0.5 ft2.

The outside ambient temperatures for Atlanta, Georgia will be taken from the ASHRAE ‘Bin and Degree Hour Weather Data for Simplified Energy Calculations’. Table 7 shows the dry bulb temperatures from 62ºF to 12ºF. The temperature and hours at each condition will be used to determine additional heating loads for the year.

Similarly, the additional heating load through the return side roof is found by changing the air stream temperature.

The fiberglass panels will allow 5.75 Btu/hr of heat through the supply side roof to the outside ambient. It also allows 3.25 Btu/hr of heat through the return side roof. The entire fiberglass cube would allow 45.00 Btu/hr of heat to transfer out of the cube. With the AAON Rigid Polyurethane Foam design, the entire cube would only allow 6.67 Btu/hr of heat transfer to the ambient air.

Table 8 has detailed values for the fiberglass and AAON cube. For the 1,027 hours, the fiberglass cube is at 62ºF and requires an extra 46,215 Btu’s of heating. The AAON design only requires an additional 6,850 Btu’s. The AAON design has decreased the superfluous heating load by 85%.

For all heating conditions between 62ºF and 12ºF, the increased heating load for both designs are shown in Table 9.

The AAON Rigid Polyurethane Foam design would save 323,607 Btu’s at 100% occupancy and 161,804 Btu’s at 50% occupancy. Compared to the fiberglass insulation design, the AAON Rigid Polyurethane Foam design decreases additional heating loads by 85%. Figure 5 gives a visual representation of the results found in Table 9. The increased heating load through the fiberglass insulation design is considerably higher than the AAON Rigid Polyurethane Foam design.

Increased Heating Load (Infiltration)

During heating conditions, the infiltration losses occur when cold air enters the HVAC cabinet and absorbs heat from the system. The bin data for Atlanta will be used to find the sensible heat required due to infiltration. A 10 ton fiberglass cabinet, with 4,000 cubic feet per minute air flow, has 4% (160 cfm) of 62ºF outside ambient air infiltrating the cabinet.

As the calculation shows, infiltrating cold air would require the HVAC system to heat at an additional 3,969 Btu/hr to maintain the 85ºF supply air. The bin data shows that Atlanta will experience 1,027 hours at 62ºF, for at total of 4,076,267 Btu’s of additional heating. Table 10 shows the losses for dry bulb temperatures 62ºF and below.

If all heating losses at or below 62ºF are summed, the result is 31,604,358 Btu’s. Estimating a building occupancy of 50% would result in 15,802,179 Btu’s of extra heating required because of the fiberglass cabinet’s 4% infiltration rate.

By comparison, an AAON cabinet with 1.5% infiltration would only require 5,925,817 Btu’s for a building occupied 50% of the heating year. An AAON Rigid Polyurethane Foam cabinet has reduced the additional infiltration heating load by 63%.

Total Heating Losses

Insulation and infiltration losses for temperatures at or below 62ºF can be summed for the total yearly increased heating load. Figure 6 indicates the lower resistance value and higher infiltration rates can dramatically increase the heating load on an HVAC system.

For instance, at 50% occupancy, a fiberglass 10 ton unit would require an additional 20,816,793 Btu’s each year. Table 11 provides an example of yearly increased heating cost for a building with twenty 10 ton units.

A twenty unit office building using 10 ton fiberglass cabinets could have 416,335,860 Btu’s of heat wasted through the cabinet structure each year. At $0.80 a therm, the fiberglass cabinet uses an additional $3,330 in heating costs each year. The same building, with the AAON Rigid Polyurethane Foam cabinets, would only require an additional 133,155,780 Btu’s, or $1,066. If utility costs were $1.20 a therm, the fiberglass cabinet uses an additional $4,996 of additional heating, while the AAON cabinet only uses an additional $1,598. A building owner with the AAON designed HVAC cabinet could save $3,398 each year in heating costs.

Reduced Operating Cost

Now that insulation and infiltration losses for both cooling and heating have been calculated,
Figure 7 shows how the AAON Rigid Polyurethane Foam design can save an Atlanta, Georgia building owner between $242 and $8,612 per unit each year with $0.12/kWh and $1.20/therm utility rates.

Savings are calculated for cities in various ASHRAE climate zones shown in Figure 8. When calculating the savings, each city’s bin data is based on the ASHRAE “Bin and Degree Hour Weather Data for Simplified Energy Calculations.” The utility rates used for each city is $0.12/kWh and $1.20/therm. The cooling and heating savings for Atlanta, Chicago, Houston, Los Angeles, Miami, Minneapolis, New York, Sacramento, Seattle, and Tulsa are shown in Table 12 and 13.

Conclusion

As utility prices increase, heating and cooling energy lost through poor insulation and poor air seals will result in significant monetary losses to building owners. The purchase of an AAON Rigid Polyurethane Foam cabinet will reduce these monetary losses through improved thermal resistance, thermal breaks, and quality air seals. The AAON cabinet will reduce the cost of cooling and heating operations.

Using the AAON Energy and Economic Analysis Program, the estimated total heating and cooling costs for the representative cities are calculated. Then, using the results in Table 12 and 13, the yearly savings for the example office building with twenty 10 ton units are shown in Table 14.

Polyurethane Foam Core Panel with Thermal Break

Two inch, double wall, rigid polyurethane foam insulation compared to one inch of fiberglass batt

Picture 1: AAON Rigid Polyurethane Foam Panels

Figure 1: Cabinet Infiltration Testing - Fiberglass Cabinet Versus
AAON Rigid Polyurethane Foam Cabinet

Dry Bulb Temperature (°F)	Time At Condition (hours)
97	9
92	32
87	220
82	758
77	768
72	1,037
67	1,162
Table 1: Atlanta Cooling Bin Data

	Fiberglass		AAON
	R Value	Additional Cooling Load (Btu’s/hr)	R Value	Additional Cooling Load (Btu’s/hr)
Supply Roof	2	10.50	16	1.31
Supply Walls	2	42.00	13	6.46
Return Roof	2	4.25	16	0.53
Return Walls	2	17.00	13	2.62
1 ft Cube Insulation Increased Cooling (Btu’s/hr)	73.75		10.92		AAON Savings
9 Hours at 97°F (Atlanta Bin Data)	664		98		85%
Table 2: Atlanta 1 Foot Cube 97°F Condition Increased Cooling Load

Dry Bulb Temperature	Time At Condition	Fiberglass Increased Cooling		AAON Increased Cooling
°F	hrs	Btu’s/hr	Btu’s	Btu’s/hr	Btu’s
97	9	73.75	664	10.92	98
92	32	61.25	1,960	9.07	290
87	220	48.75	10,725	7.22	1,588
82	758	36.25	27,478	5.37	4,069
77	768	23.75	18,240	3.52	2,701
72	1,037	11.25	11,666	1.67	1,728
67	1,162	-1.25	-1,453	-0.19	-215
100% Occupied Increased Cooling Load (Btu’s)			69,280		10,259
50% Occupied Increased Cooling Load (Btu’s)			34,640		5,129
Table 3: Atlanta 1 Foot Cube Total Yearly Increased Cooling Load

		Approximate Tons
		5	10	20	35	75	125	175	210
Cabinet Dimensions	Approximate Flowrate (ft3/min)	2,000	4,000	8,000	14,000	30,000	50,000	70,000	84,000
	Length (in)	78	88	110	153	241	287	287	329
	Width (in)	42	59	64	100	100	100	142	142
	Height (in)	35	47	57	70	102	102	102	102
	Approximate Surface Area (ft2)	81	132	187	437	650	748	891	992
Table 4: Approximate HVAC Cabinet Dimensions

	Fiberglass		AAON
	R Value	Additional Heating Load (Btu’s/hr)	R Value	Additional Heating Load (Btu’s/hr)
Supply Roof	2	5.75	16	0.72
Supply Walls	2	23.00	13	3.54
Return Roof	2	3.25	16	0.41
Return Walls	2	13.00	13	2.00
1 ft Cube Insulation Increased Heating (Btu’s/hr)	45.00		6.67		AAON Savings
1,027 Hours at 62ºF (Atlanta Bin Data)	46,215		6,850		85%
Table 8: Atlanta 1 Foot Cube 62ºF Condition Increased Heating Load

Heating infiltration Model

Sacramento

Marine (C)

Seattle

Los Angeles

All of Alaska in Zone 7

except for the following

Boroughs in Zone 8:

Bethel	Northwest Artic
Dellingham	Southeast Fairbanks
Fairbanks N. Star	Wade Hampton
Nome	Yukon-Koyukuk
North Slope

Figure 8: ASHRAE Climate Zones

Dry (B)

Tulsa

Houston

Zone 1 includes

Hawaii, Guam,

Puerto Rico,

and the Virgin Islands

Moist (A)

Minneapolis

Chicago

Miami

Atlanta

New York

	Twenty 10 Ton AAON Cabinets Savings	Estimated Yearly Cooling and Heating Costs	Estimated Percentage Savings
Atlanta	$9,300	$50,250	19%
Chicago	$8,620	$46,500	19%
Houston	$10,880	$63,750	17%
Los Angeles	$1,820	$38,850	5%
Miami	$15,380	$72,150	21%
Minneapolis	$9,220	$50,550	18%
New York	$8,020	$42,000	19%
Sacramento	$6,120	$49,050	12%
Seattle	$6,000	$30,750	20%
Tulsa	$10,400	$64,950	16%
Table 14: Percentage Savings Of An Example Office Building With Twenty 10 Ton Units

The AAON Rigid Polyurethane Foam Cabinet provides an improvement in operating cost, thermal resistance, air seals, rigidity, impact resistance, maintainability, indoor air quality, and equipment lifetime.

Turn the page for total yearly savings of 10 cities in six representative ASHRAE climate zones.

Yearly Savings from AAON Rigid Polyurethane Foam Cabinets

Yearly Savings from AAON Rigid Polyurethane Foam Cabinets

For more information, contact your local AAON sales representative.

It is the intent of AAON to provide accurate and current product information. However, in the interest of product improvement, AAON reserves the right to change pricing, specifications, and/or design of its product without notice, obligation or liability. Copyright © AAON, all rights reserved throughout the world. AAON® and AAONAIRE® are registered trademarks of AAON, Inc., Tulsa, OK.

2425 S. Yukon Ave. • Tulsa, OK 74107 • (918) 583-2266

FoamPanel • R83680 • 100301