AOM & AOMR S eries selection
AOM SERIES
3000
I J
F G H
E
C D
2000
B
A
F G H
E
C D
AOM-45
B
A
F G
1000 800
AOM-35
C D E
AOM-40
B
A
F G H I
C D E
B
500 600 400
A
AOM-25
Fs
I
F G H
AOM-30
D E
B C
A
G
F
E
D
AOM-20
300
C
B
A
G H
F
E
D
AOM-15
200
C
B
A
AOM-10
B
A
F G H
C D E
100
1
2
9 3 4 5 6 7 8 10
20
30 40 50 60 80
100
200
GPM
SELECTION GUIDE The performance curves are based on 50 sus oil & 1000 Standard Feet Per Minute air velocity. If your air velocity is other than 1000 SFPM, please use the correction curve located on this page before choosing a model. SIZING To properly size a AOM air-cooled oil cooler for mobile equipment, first determine some basic parameters associated with your system. HEAT LOAD In many instances the heat load must be determined by using the following method. The total potential or horsepowermethod is themost commonmethod, and is thesimplest way todeterminebasicheat rejection requirements formobile hydraulic systems. The total potential is equal to the maximum operating flow and pressure that are generated by the system under full load. To determine the total potential (HP) use the following formula. HP = [ System Pressure (PSI) x System flow (GPM) ] / 1714 Example: HP = (3000 PSI x 40 GPM) / 1714 = 70 HP or the total input potential To determine the system heat load in BTU / HR use a percentage (v) of the system potential HP. The factor (v) can be calculated by adding up the actual inefficiencies of a system; however, for most applications a (v) value of 25% - 30% can be used. Example: 70 HP x .25 = 17.5 HP heat To convert the horsepower of heat into BTU/HR use the formula below: HP x 2542 = BTU/HR Example: 17.5 HP x 2545 = 44,538 BTU/HR Applying into a return line For most open loop systems with a vane or gear type fixed delivery pumps. To calculate the Fs value required when applying the air/oil cooler into a return line use the formula below.
Q x Cv ____________ Tc exit - t ambient APPLYING INTO A CASE DRAIN LINE In circumstances where the system is closed loop or when return line flow is not available, the case drain flow can be utilized to help cool the system. However, in many instances, the case drain flow alone will not be enough to reject all of the heat generated by the system. Case drain lines should not be treated as a normal return lines since the pressure drop allowable usually can vary from 2 - 10 PSI max. Check with your pump manufacturer for the appropriate pressure drop tolerance before applying any cooler. To size the system for case flow or case flow plus any additional fluching loops, please use the following method. Formula Tc exit = { T - [ Q / (case flow gpm x 210) ]} Example Tc exit = { 150 - [ 44,538 / (10 x 210) ]} = 128.8 Tc exit = The corrected temperature of the oil exiting the cooler. Fs = CORRECTING FOR ALTERNATE AIR VELOCITY If your air velocity is other than 1000SFPM, you must correct to achieve the proper capacity required. Formula : CFs = Fs / Cf Example 1 Example 2 Air velocity 500 SFPM 1800 SFPM CFs = 944 Fs / .68 Cf = 1,388 1,639 / 1.35 = 1,214 see chart 44,538 x 1.06 ___________ = 1,639 128.8-100
Air Flow Correction Chart
2
1 .8 .6 .4 .5
BTU/ HR x Cv _______________ T - t ambient
Fs =
T = Desired system oil temperature leaving the cooler °F t ambient = Ambient air temperature entering the cooler °F Cv = Correction factor for oil viscosity. Example: ISO32 oil @ 150°F = 1.06
.3
.2
100
200
300 400 600 800 1000
2000 3000
Air Flow SFPM
note: AIHTI reserves the right to make reasonable design changes without notice.
260
Copyright © 2019 - 2020 American Industrial Heat Transfer, Inc.
355 American Industrial Drive LaCrosse, VA 23950
tel: 434-757-1800
fax: 434-757-1810
email: sales@aihti.com
Made with FlippingBook - professional solution for displaying marketing and sales documents online