Introduction to FAN SELECTION
FAN LAWS
In a
NOTE: A 25% increase in rpm results in a 95% increase in horsepower. Considering this, initial fan selections should be sized with motor horsepowers greater than necessary if any increase in fan rpm is likely in the future.
cfmNew | = |
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| x | cfmOld | This equation relates horsepower to rpm. The change in |
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| horsepower can be determined when the rpm is increased by | ||||||||||||
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PsNew | = | rpmNew | 2 |
| PsOld | 25%. This is shown below: |
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| Bhp | New | = (1.25)3 | x Bhp | Old | = 1.95 x | Bhp | Old | ||||||||
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BhpNew | = | rpmNew |
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rpmOld |
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Adjusting Fan Performance
There is a direct relationship between cfm and rpm within a system. Doubling the fan rpm will
Sample: The example at the right shows a fan curve at 700 rpm which had an operating point of 1000 cfm at 0.25 in. Ps. What rpm is required to move 2000 cfm through the same system?
Solution: Within a system, cfm is directly related to rpm.
Therefore, the new rpm (rpm2) can be determined from the | |||||||||
following equation: | ( | cfm2 | ) |
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rpm2 = | rpm1 | x |
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cfm1 |
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| 2000 cfm |
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| 1400 rpm | ||
= | 700 rpm | x | ( 1000 cfm ) | = | |||||
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Referring to figure at right, this results in sliding up the system resistance curve from 700 rpm to 1400 rpm. Notice that as we doubled our airflow from 1000 cfm to 2000 cfm, the Ps went up from 0.25 in. to 1.0 in. It must be kept in mind that we are not changing the system, only increasing fan speed. Therefore, we must remain on the system resistance curve. Within a system, Ps varies as the square of cfm. Since cfm and rpm are directly proportional, an equation relating Ps and rpm can be derived as follows:
Ps2 | = | Ps1 | x | ( | rpm2 | )² | ||
rpm1 | ||||||||
For our example, |
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Ps2 | = | 0.25 in. | x | 1400 rpm | ||||
700 rpm |
This verifies the operating point on the 1400 rpm curve (2000 cfm at 1.0 in. Ps). With this example, it should be clear how cfm, rpm and Ps tie together in a
system. | Varying Operating Points | |
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Example
Solution
| Sound Levels | Refer to the Suggested Limits for Room Loudness chart to |
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| In many cases, the sound generated by a fan must be | determine the acceptable sone range for the application. |
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| As a general guideline, choose a fan that has a sone value |
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| considered. For the fan industry, a common unit for |
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| within the range specified. |
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| expressing sound pressure level is the sone. In practical |
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| terms, the loudness of one sone is equivalent to the sound | Note: Rooms with a hard construction (concrete block, |
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| of a quiet refrigerator heard from five feet away in an | tile floors, etc.) reflect sound. For these rooms, select |
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| acoustically average room. | fans on the lower end of the range. Rooms with soft |
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| construction or those with carpeting and drapes, etc., |
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| Sones are a linear measurement of sound pressure levels. | absorb sound. For these rooms, fans near the higher end |
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| For example, a sound level of 10 sones is twice as loud as | of the range may be selected. |
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| 5 sones. |
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| For example, an exhaust fan for an |
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| Suggested Limits for Room Loudness |
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| office in the “Suggested Limits for Room |
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| Sones | DBA |
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| Loudness” chart below says that offices |
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| Private homes (rural and suburban) |
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| Conference rooms |
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| Hotel rooms, libraries, movie theatres, executive offices |
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| Schools and classrooms, hospital wards, and operating rooms |
| 0” Ps only the |
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| Courtrooms, museums, apartments, private homes (urban) |
| less than 12. Therefore, the |
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| Restaurants, lobbies, general open offices, banks |
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| best selection for this application. |
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| Corridors and halls, cocktail lounges, washrooms and toilets |
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| Hotel kitchens and laundries, supermarkets |
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| Light machinery, assembly lines |
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| Machine shops |
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| Heavy machinery |
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| From AMCA Publication 302 (Application of Sone Ratings for Non Ducted Air Moving Devices with |
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| F A N F U N D A M E N T A L S | 133 | |
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