A VAV system operates as shown in Fig. 3-23. The solid lines show the full-load
design condition of 100 tons with a room SHF of 0.75. At the estimated minimum load of 15 tons with SHF of 0.9, the air-flow rate is decreased to 20 percent of the design value and all outdoor air is shut off. Estimate the supply air temperature and apparatus dew point of the cooling coil for minimum load, assuming that state 3 does not change.
The solution is carried out using Chart 1a, as shown in Fig. 3-23. Because the outdoor air is off during the minimum-load condition, the space condition and coil process lines will coincide as shown by line 3–2′–d. This line is constructed by using the protractor of Chart 1a with a SHF of 0.9. The apparatus dew point is seen to be 55 F, as compared with 50 F for the design condition. The air-flow rate for the design condition is given by
\dot{m}_{2} = \dot{q} (i_{3} – i_{2})
\dot{m}_{2} = \frac{100(12,000)}{29.4 – 23.2} = 193,550 lbma/hr
or
\dot{Q}_{2} = \dot{m}_{2} v_{2}/60 = 193,550(13.25)/60 = 42,700 cfm
Then the minimum volume flow rate is
\dot{Q}_{m} = 0.2(42,700) = 8500 cfm
and the minimum mass flow rate may be estimated by assuming a value for v_{2^{′}} :
\dot{m}_{m} = 8500(60) /13.28 = 38,400 lbma/hr
State point 2′ may then be determined by computing i_{2^{′}} :
i_{2^{′}} = i_{3} – \frac{\dot{q}_{m}}{\dot{m}_{m}} = 29.4 – 15(12,000)/38,400 = 24.7 Btu/lbma
Then, from Chart 1a, the air condition leaving the coil is 60.5 F db and 57.5 F wb. Calculation of the coil water temperature is beyond the scope of this analysis; however, the mean water temperature would be increased by about 7 degrees from the design to the minimum load condition due to decreased flow rate. The use of outdoor air during part load is discussed below.