In the February 2010 issue of Pumps & Systems, I discussed my Suction Specific Speed (S) Calculator and its ability to predict the stable range of flow for a particular centrifugal pump. In November 2011, I wrote a follow-up that addressed the S value of wastewater pumps. Recently, I have seen some engineering specifications that limit S to a maximum of 11,000 for any wastewater pump. I disagree with this across-the-board limit for several reasons that I will address in this column.
Suction Specific Speed
In case you did not read my previous columns, I will start with a brief overview of suction specific speed. In the early 1960s, many pump users began to encourage their manufacturers to provide pump designs that reduced the required net positive suction head (NPSHr).
The NPSHr at the best efficiency point (BEP) flow is a function of the impeller design, and a major design characteristic is the ratio of the impeller eye diameter to its overall diameter. As this ratio increases, the entrance velocity decreases, and NPSHr is reduced. These large-eye impellers allowed pumps to operate satisfactorily in applications with low NPSH available (NPSHa).
There was, however, a down side. The peripheral velocity of the large eye also increased, and at some capacity, flow into the entrance was distorted because of the high peripheral speed.
This caused some of the flow to reverse direction and begin recirculation at the entrance of the eye (suction recirculation). This recirculation can result in intense vortices that cause cavitation and pressure pulsations.
The flow at which suction recirculation begins depends on the impeller design, but as the eye-diameter ratio increases, so does the recirculation point as a percent of BEP flow. The calculation for suction specific speed was developed to help predict the point at which suction recirculation could begin. As the value of S increases, the flow at which recirculation can begin moves closer to BEP flow. Guidelines were established that suggested that S values should not exceed a range of 8,500 to 9,500 for pumps that could potentially operate at flows that were significantly below BEP flow. Lower flows could be caused by dynamic changes in system conditions or by a throttle valve at the discharge.
Suction specific speed is calculated using Equation 1.
S = N √Q / NPSHr0.75 [Equation 1]
S is directly proportional to the pump speed in rpm (N) and the square root of pump flow in gallons per minute (Q). It is inversely proportional to NPSHr to the three quarter power. Therefore, S will increase with an increase in speed and/or flow. It will also increase with a decrease in NPSHr.
Let’s take a look at a couple examples. The two pumps described below have a 6-inch suction and are designed for a BEP rate flow of 1,500 gallons per minute at a total dynamic head of 60 feet:
NPSHr is very similar for both, but Pump A operates at 1,750 rpm, while Pump B operates at 1,150 rpm. Both have a specific speed (Ns) of around 2,200. Pump A has a relatively high eye-diameter ratio (0.54) which accounts for its low NPSHr. Pump B has a lower eye-diameter ratio (0.38), but because it operates at a lower speed, its NPSHr is also low. The calculations for S are 13,044 for Pump A and 9,363 for Pump B. Based on the engineering specification I mentioned earlier, (S max = 11,000) Pump A would not be an acceptable option.