In recent years, most industry professionals have been leaving the decision of driver size selection to pump-selection software. There is nothing wrong with that choice, and many selection software programs do a great job.
This column will explore some of the specifications and decision-making processes that occur behind the scenes. I offer this information because I have witnessed several poor decisions in recent years with regards to driver selection and sizing.
It is a delicate balancing act fraught with compromises to properly size a motor as a pump driver. Too big and you waste money in the initial cost and over the life of the unit because it manifests as inefficiency. Too small and you will reduce the life of the motor. Overloaded motors will run hot and fail the insulation system. Just an 18 degree Fahrenheit increase in normal winding temperatures will reduce the insulation life by 50 percent.
In most cases the pump driver will be an alternating current (AC) electric induction motor or an internal combustion engine. When quality steam is available and the duty cycle is approaching 100 percent, turbines are an efficient driver choice, especially in the larger horsepower (HP) ranges above standard National Electrical Manufacturers Association (NEMA) frame sizes.
Making a Choice
Let’s start with a simple pump curve and select the correct driver based on the rated hydraulic conditions. Refer to the pump curve (Figure 1, page 23). The rated hydraulic conditions for the example pump are 270 gallons per minute (gpm) at 115 feet of total dynamic head (TDH) pumping clear water at an ambient temperature of 68 F with a specific gravity of 1.0 and viscosity of 1 centipoise.
Unless the curve states otherwise, most every pump performance curve is based on clean water at 60 or 68 F with a 1.0 specific gravity and a viscosity below 5 centipoise.
The example pump is an end suction American National Standards Institute (ANSI) pump of size 2 x 3 x 6 operating at 3,550 rpm with the impeller trimmed to 5.5 inches. I have simplified the curve as much as possible for this example (efficiency at the duty point is 77 percent). Note that the pump will require 10.2 brake horsepower (BHP) at the duty point also known as the rated point. I used the basic horsepower formula (see Equation 1) to arrive at that number, which corresponds with the selection software. The program selects a 20 HP motor for the condition because I have the software sizing criteria set to select a motor for the maximum power on the design curve (an industry best practice).
You can also conclude that exceeding 15 HP with this selected pump impeller (5.5 inches) and the given fluid properties is unlikely. In this particular case, discuss with the end user and jointly decide whether or not the 15 HP motor is sufficient. However, for future use the end user may require an increase in the flow rate or head. This increase will require a larger motor. Perhaps in the future the system will have a component added or simply corrode or foul, all of which will cause the system curve to change and potentially require a larger driver.
Sometimes, simply due to budget constraints, the compromising answer will be to select the smaller 15 HP motor, but to size the baseplate, switchgear, wire size and conduit for the larger future motor frame. This example doesn’t carry much weight when considering the difference between a 15 and 20 HP motor. But assume the discussion is about 15,000 HP and 20,000 HP motors, and you can quickly realize it is a discussion and decision process not to be taken lightly. Furthermore, if the decision is for 200 pumps instead of one, the size selection decision will make a marked difference in operating costs.
Remember that in the example, the fluid was clean water at 68 F and 270 GPM at 155 feet (TDH). Now suppose the fluid properties have changed to a higher specific gravity of 1.2. This realistic and simple increase will change the required HP from 10.2 to 12.22 for the same head and flow. For a runout condition (far right on the curve) on the same size impeller of 395 GPM at 82 feet the new required horsepower will exceed 15 HP. This, by convention, now dictates a 20 HP motor. The point of the example is to illustrate that changes in the specific gravity will change driver size for the pump. Make your decisions accordingly.
Another practical example would be a change in viscosity. The first example was based on water with the viscosity at 1 centipoise. It is very common to have fluids that have much higher viscosities. Also note that the viscosity will change directly with temperature. A simple viscosity increase from one to 50 centipoise will increase the required horsepower from 10.2 to 13, and the revised maximum for a runout condition will be almost 23 HP. Consequently, the required motor size is now 25 HP.
Most experienced pump people will, as an accepted best practice, size the motor driver to be non-overloading for the selected impeller diameter curve. Many industries and end users will specify that the motor be sized to be non-overloading for the maximum size impeller in that pump (6.0 inches in our example), and in many cases there will be a service factor that is added to that max impeller quantity or at least to the selected impeller requirement.