The 2017 SAWD Jubilee which was held in Myrtle Beach June 10th – 12th always draws many pump professionals and their families. This year’s theme was “A County Fair with Ocean Air.” In keeping with the theme, National Pump gave away red bandanas with the company logo for those who stopped by our booth. On display were National Pump’s selection of submersible and booster pumps. The Jubilee Show is always a good time to meet up with new and existing customers to discuss their pump needs, learn about new products and attend some technical seminars.
Pictured below is National Pump Territory Sales Manager Joel Rackley and National Pump Georgia Branch Manager Mark Boutwell with show attendees.
When selecting a pump, it is extremely important to ensure that the net positive suction head available (NPSHA) is greater than the net positive suction head required (NPSHR) of the pump to prevent cavitation.
NPSHA is the amount of absolute suction head available in feet of liquid at the first stage impeller datum minus the absolute vapor pressure of the liquid.
NPSHA = h,atm + h,s – h,vp = ft of liquid
h,atm = atmospheric pressure head = ft
h,s = total suction head = h,gs + h,vs + z,s = ft
h,gs = suction gauge head = ft
h,vs = suction velocity head = ft
z,s = elevation from the gauge centerline to first stage impeller datum* = ft
(*The “J” dimension shown in the National Pump Company Engineering Catalog for bowl assembly dimensions shows the location of the first stage impeller datum)
h,vp = liquid vapor pressure
NPSHR is a minimum NPSH given by the pump manufacture for the pump to achieve the specified performance. This value may be equal to the NPSH3 of the pump or many contain a margin above the NPSH3 of the pump depending on the manufacture.
NPSH3 is the net positive suction head required resulting in a 3% loss of total head at the first stage impeller due to cavitation (Figure 1). This is the NPSH value determined during testing. National Pump Company publishes a NPSH3 curve, which is labeled as NPSHr in PumpFLO.
If a pump is design with an insufficient margin between the NPSH3 of the pump and the NPSHA, cavitation will occur. Cavitation is due to the pressure within pump dropping below the vapor pressure of the liquid which results in the liquid becoming a vapor. This vapor reduces the area where the liquid can flow causing the loss in performance. As the vapor travels though the pump, the pressure increases causing the vapor bubbles to collapse returning to a liquid. This collapse results in noise, vibration and material loss reducing the pump life.
The Hydraulic Institute has a guideline for NPSH margin, ANSI/HI 9.6.1. This guideline discusses a number of items which influence the needed margin along with recommended margins. The recommended margin is based on either the:
While the recommendations vary based on application, size, materials and operating region, a 3.3-foot (1.0-meter) margin or 1.1 ratio, whichever is greater, is typically acceptable (Figure 1).
Figure 1 – Curve Showing Head Performance and NPSH3 at a Specified NPSHA
Ensuring an adequate NPSH Margin between the NPSH3 of the pump and the NPSHA will ensure the pump performances properly.
Figure 2 – CFD Analysis Showing Pressure Gradient Thru the Impeller (left) and Cavitation Bubble Sheet (right)
Director of Engineering
National Pump Company – Glendale, Arizona
National Pump Company is proud to announce our ISO 9001 standard certification renewal from ISO 9001:2008 to the new ISO 9001:2015 standard.
As part of a continued focus to improve its quality management system in efforts to exceed customer expectations, National Pump Company is proud to announce that it obtained the ISO 9001:2015 certification. This certification transitioned NPC from the previous ISO 9001:2008 quality system standard to the new globally recognized quality system that all ISO 9001 certified companies will be required to comply with by September 2018.
ISO 9001 is the international standard for quality management systems that is recognized and respected in more than 170 countries with over one million companies certified. This standard is based on a number of quality management principles including; a strong customer focus, the motivation and engagement of top management, the process approach, and continual improvement. Using ISO 9001 helps ensure that customers consistently get quality products and services, which in turn brings many shared business benefits.
By achieving this level of certification, National Pump Company continues to demonstrate our ability and desire to effectively and efficiently provide a quality management system while continuously improving products and services to valued customers.
Martin S. Anthony
Director of Quality and Continual Improvement
National Pump Company – Glendale, Arizona
Vertical turbine pump (VTP) and driver alignment is critical for extending the serviceable life of the driver, pump bearings and mechanical seal assembly while also providing vibration free service of your installation. As VTPs utilize multiple components which may make proper field alignment more complicated, it is important to apply the skill, time and patience necessary to make the minor adjustments needed to insure proper alignment. This article will focus on the shaft alignment of the driver, discharge head, shaft coupling and mechanical seal housing for pumps (and pump cans) that are to be installed and leveled according to manufacturer’s recommendations.
As with any pump installation, end users should pay close attention to the pump application and where the pump is operating on the performance curve. A properly sized pump can provide years of trouble-free service and increase the mean time between failures caused by wear and induced vibration issues. The pump manufacturer will typically specify the preferred and allowable operating ranges on their performance curve as well as minimum continuous stable flows.
The pump driver may consist of an electric motor, vertical gear, or steam turbine that incorporates a vertical solid shaft design mounted on the pump’s discharge head. The vertical solid shaft driver must be supplied with special shaft and base flange tolerances. API 610 11th Edition specifies the tolerances in Figure 1. The maximum shaft runout and shaft to driver face perpendicularity of 0.001 total indicated runout (TIR) are most important. The 0.005 TIR maximum axial float may be achieved in most cases, but some extra high thrust designs may require greater axial float.
The pump discharge head should be welded according to specification requirements. If it is constructed of carbon steel, a post weld heat treatment (PWHT) process is recommended after fabrication and prior to machining to prevent warping after the final machining process. Users should give special consideration to the driver to discharge head female/male register fit, typically referred to as the National Electrical Manufacturers Association (NEMA) driver “AK” dimension.
The discharge head should be designed to allow the driver to freely move in any horizontal direction, at least 0.020 inch/inch (in/in) TIR relative to the vertical axial centerline of the discharge head. Instead of tapped holes, the discharge head should incorporate through bolting for mounting the driver. This design element will facilitate additional horizontal movement necessary to achieve proper alignment. Alignment positioning screws are required for any driver which exceeds 500 pounds per API 610 11th Edition, section 184.108.40.206.2. When alignment-positioning screws are incorporated into the discharge head design, the register fit between the discharge head and the driver must have open clearances. A register with greater clearance is helpful because it allows the driver to be roughly positioned. Alignment- positioning screws for drivers under 500 pounds are also recommended to facilitate alignment.
The driver should not be aligned using shims, especially if the pumps are to be used with electric motors that have variable frequency drive systems (VFDs) because this setup will change the resonant frequency of the driver/discharge head structure.
A rigid flanged spacer coupling must be supplied with special tolerances. API 610 11th Edition specifies these tolerances in section 220.127.116.11 which requires the coupling faces to be perpendicular to the axis within 0.0001 in/in of face diameter or 0.0005 in/in TIR total, whichever is greater.
The fabricated discharge head should be relieved of stress once welding is complete and prior to machining. During the machining process, stresses induced by welding can result in runout. The runout issues can affect the perpendicularity of the motor mounting flange and/or the concentricity to the seal chamber bore.
The seal chamber must be supplied with a registered fit. This registered fit must be concentric to the shaft and have a 0.005 in/in TIR per API 610 11th Edition section 6.8.4. The seal chamber face should have a runout or 0.0005 in/in of seal chamber bore TIR per API 610 11th edition section 6.8.5.
The pump and driver should be coupled, and runout should be inspected. The shaft runout must be within the maximum allowed by the seal manufacturer for that particular mechanical seal. This value is typically 0.001 to 0.002 in TIR. Users should also check the seal register and face runout. Documentation of the inspection should include the pump and driver serial number along with measurements. The AFS coupling should be tagged for use on the specific pump and match marked. These steps will ensure proper assembly orientation.
Cleaning all surfaces before attempting to align the pump and driver is vital. If alignment was not performed at the factory, the keys of the AFS couplings may need to be deburred and the flange faces may need to be cleaned to remove any protective coating.
A dial indicator connected from the driver shaft should be used to obtain a TIR within 0.005 in/in at seal chamber register. The driver to pump coupling should then be installed to verify the shaft TIR does not exceed the limits recommended by the seal manufacturer. If the shaft runout cannot be achieved, a slight adjustment to the driver may be required. The pump/driver coupling may also need adjustment. Rotating one half of the coupling may reduce perpendicularity tolerance stack-up, which can cause problems. If the coupling must be installed in a particular way, it should be match marked. Once the shaft runout has been verified, the seal chamber register should be rechecked to confirm it is still acceptable and the seal chamber face runout must also be checked. Once the alignment is verified, the mechanical seal can be installed.
If the runout tolerances cannot be achieved, end users can consider the following troubleshooting checks. The easiest process to check first is the pump to driver coupling. Each coupling part can be checked both individually and as an assembled unit. If this process identifies a runout issue, the coupling can be reworked or replaced.
In many cases, the seal housing can be removed without removing the motor. Once the seal housing is removed, the runout can be inspected and verified. If the seal housing has an excessive runout, this component should be reworked or replaced. If the runout issue is not found in the seal housing, check the runout between the driver shaft and the seal housing bore on the discharge head. If excessive runout exists at this check, the discharge head is the source of the issue.
Checking the shaft runout of the pump driver can be achieved without removing it. If everything to this point has been found to be satisfactory, the driver will need to be removed and the shaft to the driver face checked for perpendicularity. Pumps that do not have alignment-positioning screws will also need to have the register concentricity inspected with relation to the shaft. If these items have been checked and found acceptable, the issue is with the pump – either the discharge head or the pump shaft.
Figure 1. The drawing shows the critical dimensions. Ensuring the proper seal alignment between the pump and driver is the best safeguard for prolonging seal life and maximizing the mean time between repairs.
Many Farmers and Pump Dealers only consider the initial purchase cost of the pump and motor as their TOTAL COST OF OWNERSHIP, without considering ALL of the key factors which include:
It is surprising to most users that the cost of operating a pump over its service life far exceeds the initial purchase cost. Factors include:
When comparing the operating costs at 2 different installations (as illustrated on page 2), the energy savings alone paid for the entire initial cost of the most efficient pump and motor in less than a few years! Projected savings over 20 years of ownership is projected to be enormous!
When purchasing a new pump, the following should be considered:
BE SMART, BUY QUALITY and SAVE!
For a complementary performance test and ‘wire to water’ efficiency analysis, please contact your local National Pump location.