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2 There should be no discernible fluctuation in pump speed If an operator can hear or see HVAC variable-speed pumps change their speed, there are pump control problems The rate of response for the control system may be too slow 3 All equal-sized pumps should be operating within 15 rev/min of each other If not, there again are control problems 4 The controlling differential pressure transmitter should hold the differential pressure at this transmitter to within 1 2 to 1 ft of head Fluctuation of the pressure beyond 1 ft from the set point indicates insufficient control 293 Evaluation of Existing Procedures Once the system head curve or area is developed, a figure similar to Fig 291 can be developed for the system If the shaded area is appreciable, there exist possibilities for energy savings The engineers for system design and operation should then continue their evaluation of the water system to determine actual energy savings by several procedures; some systems may require several such procedures: 1 Eliminate some or all of the existing mechanical devices such as balancing or pressure-reducing valves 2 Trim existing pump impellers 3 Change to variable-speed pumps 4 Determine if the pump programming is correct Are the right number of pumps being operated at all system loads The amount of overpressure that is occurring at the minimum flow point will help determine what procedure should be used In Fig 291, this overpressure is 120 21, or 99 ft The existing balance or pressureregulating valves may have been used to control this overpressure Removing them may cause operating problems without correcting the pumps as well

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The first step that should be considered is to trim the pump impeller to provide the maximum flow and head of 800 gal /min at 85 ft of head The dotted curve in Fig 291 describes the resulting head-flow curve for the pump Care should be taken in trimming the pump impeller The affinity laws cannot be taken for granted in trimming this impeller, since the

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system contains 20 ft of constant head across its cooling coils and their control valves and associated piping Equation 101 should be used to compute the impeller diameter This is done by finding the equivalent operating point on the present pump curve Q22 H2

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(101)

maximum flow and head conditions of 800 gal/min and 85 ft unknown equivalent points on the pump head-flow curve

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By trial and error, values of H3 are inserted in the preceding equation until Q3 and H3 fall on the known pump head-flow curve for the 10-in-diameter impeller operating at 1770 rev/min The equivalent operating point, after several trials, is determined from the equation to be Q3 889 gal/min and H3 105 ft Since the diameter varies directly with the flow, the new diameter is 800 889 10, or 90 in If the affinity laws had been used directly without recognition of the system head curve, the impeller diameter would be 800 1000 10, or 80 in The impeller would therefore be undercut and would not have sustained the desired point of 800 gal/min at 85 ft of head Equation 101 should always be used for trimming impellers, not the ratio of flows in gallons per minute from the affinity laws themselves Also, it must be remembered that the trimmed impeller must be replaced if the original design condition of 1000 gal/min at 100 ft is ever reached by the system in the future Trimming the impeller reduces the pressure from 120 ft at shutoff to 98 ft At minimum flow of 100 gal/min, the head will be 98 ft and the overpressure 98 21, or 77 ft This may still be too much overpressure for the coil control valves The trimmed impeller has saved energy, but much is still to be saved by the use of a variable-speed pump All the shaded area below the dotted curve for the trimmed pump can be saved by changing the original 10-in-diameter impeller to variable speed

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