Bell & Gossett Part Load Efficiency Value Part 4: End-of-Curve Selections

RL Deppmann
July 18, 2016
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When looking at Bell and Gossett pump selections, we often find higher part load efficiency (PLEV) pump choices are to the right of the BEP, or best efficiency point. How close to end-of-curve should a prudent engineer choose?

Part load efficiency value pump selection tableThe following shows a Bell and Gossett selection table sorted on PLEV, or part load efficiency value. The most efficient part load selection is the e-1510-3AD with a PLEV of 81.79. This selection is 3500 RPM and not the traditional 1750 normally scheduled. That 3AD selection also shows it is 90% of end-of-curve (EOC). How important is EOC?


Is It Safe to Select Pumps to the Right of BEP?

ASHRAE suggests pumps be selected between 66% and 115% of BEP. In this example, the ASHRAE satisfactory range is between 473 GPM and 824 GPM. This selection meets that criteria.

diagram showing satisfactory range on either side of BEP

ASHRAE’s selection criteria is concerned with the operating efficiency of the pump selection. Of course, efficiency is important, but concerns about running off the end of the curve are even more important.

This example has an EOC point of 891 GPM at the design speed of 3550 RPM and a 6.625” impeller. Since the pump is selected at 800 RPM which is 90% of end of curve, could it be a problem? The answer, like so many others when we get close to the edge, is: it depends!

Issues Surrounding the EOC Point

When ASHRAE suggests a maximum of 115% of BEP, there’s the assumption that you selected the head of the pump exactly with no guesses, rounding up, or “rules of thumb.” There’s also an assumption that there is no safety factor. What effect might these things have on a pump too close to EOC (92.5% in this example)?

Here’s the same curve showing a control curve of 30% of design head and variable speed.

control curve of 30% of design head and variable speed

Where would the operating point be if 15% were added for a safety factor and 20% overestimate of pump head?

Think that’s ridiculous? How many of us use 4.0 feet per hundred as a default in pipe friction when the B&G system syzer® would show 2.7? How many of us automatically use 6” pipe when the system syzer suggests 5”? How many of us use 25% or 50% for fittings as an estimate? How many times did we round up an equipment pressure drop and then add safety to it? We play it safe in pump head selections and, in general, we’re all guilty…including me!

actual head example

This selection is off the curve at design flow rate!

Another issue is the balance of the system. Engineers often specify 10% balance tolerance, so many of the balancing procedures start with the pump at 110% of design flow, and the discharge triple duty valve or speed is raised to maintain that point during balance. It’s not unusual when the balance is complete that the speed is never adjusted or the impeller trimmed as ASHRAE suggests in the 90.1 standards. This makes the selection go even farther to the right.

Diversity is the expectation that all control valves on terminal units will not be open at the same time. When using diversity in the design, the pump GPM is lower than the total of the terminal units. What happens when there’s a system startup or night/weekend setback and there’s a call for the system to change room temperatures all at once? Diversity disappears as all the valves go open at once. Again, a chance to move farther to the right of design.

Finally, there’s the assumption that the controlled system curve remains stable during operation. Many articles have shown control curve shifts under various combinations of 2-way operation. Some of those shifts cause the control curve to drop and operate with more flow and less head than design. Again, this moves the operation to the right on the pump curve.

control area map with system head curves

Best Practice for Selections

All of these possible outcomes should be weighed when deciding whether to move to the right of BEP with your selections.

When tempering pump part load efficiency with the possible unintended operation points, we suggest standardizing on selections at 85% of EOC or less, unless more analysis of a possible system curve drift is reviewed. This seems to be a comfortable compromise between the old sage statement of “always select far left of BEP” and the newer cry of “efficiency trumps all.”

Next week we’ll conclude this series on Bell and Gossett PLEV with a few comments about part load and part flow.

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