December 21, 2010

My New Year’s Pumping Resolutions

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This year my New Year’s Resolutions are going to be a little different. Instead of making resolutions for myself I would like to make resolutions for all of my readers. These resolutions are appropriate for design engineers as well as owners and operators of pumped systems. Using this approach I don’t have to break any of my own resolutions, and if you wish to break them, then you shouldn’t feel any guilt either. But I promise these are for the good of your plant designs.

So here goes, my resolutions for YOU, and the pumps in YOUR plant.
  1. “I resolve to get a copy of the manufacturer’s supplied pump curve for each centrifugal pump in my plant.”
    • By having the pump curve, you will be able to determine if the pump is operating properly. The manufacturer’s supplied pump curve is the most important document needed for pump system maintenance, without it you are flying blind.
  2. “I resolve to install pressure gages on the pump suction and pump discharge for each pump in my plant.”
    • Having accurate pressure gages on the pump suction and discharge allows you to easily determine the differential pressure across each pump. When used in conjunction with the pump curve (acquired by resolution 1) you can determine the flow rate through the pump.
  3. “I resolve to develop a means of determine the flow rate through a pump.”
    • This one is very flexible, it can either be an installed meter (only if you have the cash), a clamp on Doppler meter, or determine the power supplied to the motor. Using the flow rate, the pump curve (resolution 1) and the differential pressure values (resolution 2) you’ll be able to determine if the pump is operating on the pump curve. This is very helpful in troubleshooting the operation of any centrifugal pump.
  4. “I resolve to determine where each pump is operating in relation to the pumps Best Efficiency Point.”
    • If the pumps operational flow rate is between 80% to 120% of the pumps BEP listed on the manufacturer’s pump curve (resolution 1) then that pump should have a long and prosperous life.
  5. “I resolve to investigate all pump mechanical seal or bearing failures this year.”
    • If the pump is not operating between 80% to 120% around the BEP (resolution 4) the cause of the failure is most likely due to shaft deflection cause by continually running the pump outside the pumps sweet spot.
  6. “I resolve to look into performing a pumped system assessment per the ASME EA-2 Energy Assessment for Pumping Systems.”
    • The standard can be purchased from the American Society of Mechanical Engineers Website www.asme.org, or the Hydraulic Institute Website www.pumps.org.
If you follow all these resolution then your pumped systems (or your customer’s pumped systems) will be running efficiently. You’ll have reduced your operating costs, reduced your maintenance costs, or reduced your capitol cost, all while increasing your plants reliability and profitability. Now wouldn’t you feel better if you were able to keep these resolutions rather than sweating off a couple of pounds at the gym?

That’s my list, but I’d like to hear your professional New Year’s Resolution Lists. Maybe I forgot something on my list? On the other hand, maybe you have other goals for 2011? Leave me a comment or better yet, send me an email, as I have resolved this year to once again answer all questions or comments.

In addition if you would like to be a guest blogger let me know, always interested in finding out what others are thinking about.

December 8, 2010

Valve World Expo, Dusseldorf Germany

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I just got back from the 2010 Valve World Conference and Exhibition in Dusseldorf Germany. It was a long trip through 10 time zones. Engineered Software had a booth at the exhibition and I had the privilege of giving two presentations at the conference. The conference was three days in length and then it was back on the plane for a long ride home. The conference was well attended despite the snow storm and record cold for all three days of the conference.

My wife and I really enjoyed the city wide Christmas celebration with hundreds of street vendors selling German food, gifts, candy, and mulled wine. The first evening we arrived we were outside in the snow, on a crisp and clear night enjoying a hot cup of mulled wine with 400 others. After two cups we made it back to the room and fell fast asleep without any problems with jet lag.

After setting up the booth on Monday and a good night’s rest we were ready to go. The show traffic was great and we met some of our existing customers along with meeting many new engineers involved with the design and operation of piping systems from around the world.

One of my discussions with a visitor was particularly noteworthy. On the second day of the conference, an entourage of four came to the booth, a man in his late 50’s lead the group followed by three younger men in their 20’s (Photo 1). The older gentleman only spoke Russian and German and one of the younger men translated. We introduced ourselves through the younger translator and found out the older man was Professor Gancho Dimitrov from the University of Architecture, Civil Engineering and Geodesy in Sofia Bulgaria. Since I had taught two Engineered Software classes at the Worley Parsons office in Sofia two year, earlier we had something in common and the conversation progressed.

This is me talking to Professor Gancho Dimitrov (far right)
and his students at the Valve World Exhibition. Special thanks
to our translator, the young gentleman between us two old guys.

Professor Dimitrov had many years of operational experience and had written multiple text books on water and waste water treatment. He then asked if I could set up a simple system using the software with multiple pumps. I created a system using metric units (I am "MSU" engineer, Metric as a Second Unit). He wanted a system with three pumps installed and with a total system flow rate of 600 m3/hr. I then selected a pump to pass 200 m3/hr with the total head needed to pass the system flow rate of 900 m3/hr. When I placed the three pumps in the system, the calculated total flow rate was 600 m3/hr, with each pump passing 200 m3/hr. He then wanted me to turn off one of the pumps and calculate the flow through the system with two pumps running.

I knew what he was up to; he wanted to check to see that the flow rate through the two pumps operating in parallel was something less than 400 m3/hr. A typical rookie mistake is in thinking that running two pumps in parallel will translate into two-thirds the flow rate of three pumps in parallel. That subject is covered in detail in our Piping System Fundamentals class. As soon as he saw the answer on the PIPE-FLO screen he immediately started drawing a multiple pump curves on a system curve and talking to his student doing the translation. See figure 1.

Figure 1.


This is the system Professor Dimitrov’s sketched showing how multiple pumps in a system should operate when the resistance is a mixture of both static head and dynamic head caused by pipeline head loss. Notice that with the mixed system when only one pump is running the pump passes 320 m3/hr, two pumps running passes 500 m3/hr, and when all three pumps are running, passes 600 m3/hr.

I knew I needed to look into the system to find out the reason for this unlikely event. It turns out that the system that I designed in PIPE-FLO was dominated by static head, with very little dynamic head loss due to pipe friction (Remember metric units are my second units). The result was a very flat system resistance curve, almost horizontal. While he was still drawing his system curve (Figure 1), I started drawing my system curve (Figure 2) showing how multiple pump curves intersected a resistance curve dominated by static head. As you can see from the system curve, each of the three pumps under this unusual situation produces 200 m3/hr each regardless of the number of pumps running.

Figure 2.
 
This is the system that I had created in PIPE-FLO to show how the system operated. I had not realized that the system that I create was a system dominated with static head. Notice how the flow rate through each pump is 200 m3/hr.

As soon as each of us had our turn explaining our systems with the unfortunate student translator, we both agreed that the PIPE-FLO program produced accurate results for this highly unusual system example.

You could say that a system resistance curve was considered a universal language used to describe the operation of operating piping systems. I had a great time talking to Professor Dimitrov and promised to visit the next time I’m in Sofia Bulgaria.

If you have an opportunity to visit a trade fair in Europe, I would suggest you go, even if you have to work it around a vacation. Valve World was rather small only 20,000 attendees, but was for a very specifically targeted audience. We will also be exhibiting at another international trade show, ACHEMA 2012, running from June 18th – 22nd. The 2009 show drew over 179,000 attendees, and had over 23,000 exhibitors! Like I said the Germans really know how to have a trade fair.

Now it’s time to hear from you. What trade shows do you plan on visiting and why? What value do you find in attending trade shows? What predictions do you have for the 2011 trade show season?

Please feel free to share your experiences, or opinions on this blog entry or any other subject that is of interest. Leave a comment below or email me. I can be reached at blogger@eng-software.com.