Fluid Power Journal Tech Directory 2010 by Innovative Designs & Publishing, Inc.

Airline Lubrication Pros and Cons I Know, It hertz The Perfect Hydraulic Fluid

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contents Tech Directory 2010

•

Volume 17

•

Issue 9

Features

8 10 12 14 20

The Perfect Hydraulic Fluid By Brendan Casey

To Lube or Not to Lube?

By Richard F. Bullers, Senior Applications Engineer, SMC Corporation of America

2010 Minnesota Fluid Power Skills Competition

Tech Directory Listing

Submitted by Jeannine Uehling, Minnesota Fluid Power Skills Competition Director, IFPS Chapter 5

By Dan Helgerson, CFPAI, CFPAJPPCC, CFPMT, CFPCC, CFPS Cascade Steel Rolling Mills, Inc.

departments

Tech Directory Matrix

I know, it hertz

4 5 6 30 31 32 33 34 35 36 40

Notable Words IFPS Time Capsule Figure It Out Web Marketplace Industry News People In The News Air Teaser Product Review Association News Calendar of Events Classifieds

Official Publication of The International Fluid Power Society

electrohydraulics

www.atos.com

Vane pumps

Piston pumps

Hydraulic cylinders

Solenoid valves

Modular valves

Special valves

Servoproportionals

Digital proportionals

Cartridge valves

Digital electronics

Axes controllers

Servoactuators

on line

Home page This is Atos Profile Technology Components News Catalog on-line Digital news Applications Blocks Power units Training Links Contact us

new handbook electrohydraulics A 28-pages technical handbook, english 15 x 21 cm, code TH10, has been conceived to provide engineers & students with a comprehensive survey of up-to-date electrohydraulics. It contains information, sections, data, diagrams, application schemes of main electrohydraulic components with enphasys on new digital proportionals. On request it will be posted free of charge.

digital electrohydraulic controls Atos offer today a complete line of digital electrohydraulic proportionals plus new related digital drivers and new digital axis motion controllers. Digital electronics add valuable plus: • better performances: hysteresys, response time, linearity • software setting of hydraulic parameters: scale, bias, ramps, non-linearities… by your PC, using Atos user-friendly software E-SW-PS • diagnostics and computer assisted maintenance • optional alternated P/Q control for valves and pumps Servoproportionals, direct or 2-stage ISO valves, pressure controls, digital cartridges, digital variable pumps, digital servoactuators, digital axis controllers. Also in rugged or ex-proof esecutions. Extensive technical tables are available on Atos Catalog on-line, together with a lot of variants for any application: look at www.atos.com

Atos electrohydraulics info@atosusa.com

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NotableWords

Celebrating

years

50 years? 50 years! Whoa – what lasts 50 years anymore? Certainly not things that remain static and don’t change with the times. I think that is one of the most remarkable things about the International Fluid Power Society – CHANGE. Its principles and mission are the bedrock that doesn’t change, but its offering to both industry and individuals does. When the Fluid Power Society was first established 50 years ago, it dealt with the technologies and parameters of that time. Today, the numbers of yesteryear as represented by flows, pressures, speeds, control, etc. would be considered “middle of the road vs. state of the art” as needed in modern machine design and performance. The IFPS of today is current with the new frontiers. Our certification programs regularly go through updates to stay at the leading edge. CHANGE! A good thing. You’ll notice the wide range and growing number of certifications the IFPS offers. This growth and adaption to the needs of the industries has been the accomplishment of a large group of dedicated professionals who keep the process moving. These are the ties that bind the whole work together and further strengthen the bedrock that forms our Society base. And you know what? Those tests are defensible. They truly exhibit the strengths and capabilities of the individuals who pass the written and job performance tests. I love to say, “They prove you can not only talk the talk but you can walk the talk!” As the Society carries on, we continually look to the future (for example, Mechatronics!) with the new combination of many disciplines of the past. Our committees right now are putting together a certification program for this developing job classification. A Boy Scout merit badge! I am on this committee and am so excited about presenting our industries’ opportunities

Publisher Innovative Designs & Publishing, Inc. 3245 Freemansburg Avenue, Palmer, PA 18045-7118 Tel: 800-730-5904 or 610-923-0380 Fax: 610-923-0390 | Email: AskUs@ifps.org www.FluidPowerJournal.com Associate Publisher Marc Mitchell Art Director Quynh Vo Editor Kristine Coblitz VP Operations Lisa Prass Account Executive Bob McKinney Accounting Donna Bachman, Debbie Clune OPERATIONS ASSISTANT Tammy DeLong Circulation Manager Andrea Karges

International Fluid Power Society 1930 East Marlton Pike, Suite A-2, Cherry Hill, NJ 08003-2141 Tel: 856-489-8983 Fax: 856-424-9248 | Email: AskUs@ifps.org www.ifps.org

2010 Board of Directors President & Chairperson Rickey L. Rodeffer, CFPS, CFPMIH, CFPMT, CFPAI The Boeing Company Immediate Past President Robert Yund, CFPAI, CFPIHT, CFPS, CFPCC | Hennepin Technical College First Vice President Jon Jensen, CFPAI, CFPPS, CFPECS | SMC Corporation of America Vice President Education James F. Simpson, CFPS, CFPMM, CFPAI Nusim Assoc Fluid Power Consultant Treasurer Patrick J. Maluso, CFPMHM, CFPS, CFPAI | Western Hydrostatics, Inc. Vice President Membership & Chapter Support Leo C. Henry, Jr., CFPMHM, CFPCC, CFPAI | Altec Industries, Inc. Vice President Certification Wayne C. Farley, CFPMMH, CFPAI | American Electric Power Vice President Marketing and Public Relations Mark Perry, CFPHS | Fitzsimmons Hydraulics

Directors-at-Large

George Bufink, CFPAI, CFPMMH | American Electric Power Dennis Crouch, CFPCC, CFPHS, CFPIHT, CFPAI General Motors (retired) Mike Anderson, CFPS | Motion Industries Tom Blansett, CFPS | Eaton Corporation Justin Sergeant, CFPS | Open Loop Energy, Inc. Bismarck (Bill) Castaneda, CFPHS | Automation Tech, Inc. Jeremiah Johnson, CFPHS | Caterpillar, Inc. Doug Daniels, CFPHS, CFPAI | Mohawk College Jean Knowles, CFPS, CFPE | Spencer Fluid Power, Inc. Marti Wendel, CFPS, CFPE | The Paquin Company, Inc. L. David Ruffus, CFPAI, CFPMHM, CFPMHT | Georgia Power Company Richard Bullers, CFPPS | SMC Corporation of America

Honorary Directors

to a younger generation through this project. As you can see, the IFPS isn’t your same old Society. CHANGE! A good thing. People (volunteer people) come and go from the Board and its committees on a planned (for the most part) and regular basis. This helps the Society to move along the trail to the future in a systematic but exciting way. CHANGE! A good thing. Come join us! Get involved. You’ll be amazed at your own growth and CHANGE! I guarantee you’ll learn something new, and that’s what it’s all about. Here’s to another 50 years – IFPS!

Robert Firth John Groot, CFPPS Raymond Hanley, CFPE/AI-Emeritus Robert Sheaf, CFPAI, CFPE, CFPMM, CFPMT, CFPMIT, CFPMMH, CFPMIH, CFPECS

IFPS Staff

Donna Pollander, Executive Director Sue Tesauro, Certification Manager Adele Kayser, Communications Manager Sue Dyson, Membership Coordinator Connie Graham, Certification Coordinator Diane McMahon, Certification Coordinator Beth Borodziuk, Administrative Assistant Nick Pollander, Certification Assistant Diane McMahon, Bookkeeper

Salute! Fluid Power Journal (ISSN# 1073-7898) is the official publication of the International Fluid

By Mark Perry, CFPHS, Fitzsimmons Hydraulics, IFPS Director at Large and Chair of Marketing and Public Relations Committee

Power Society published bi-monthly with four supplemental issues, including a Systems Integrator Directory, Off Highway Suppliers Directory, Tech Directory, and Manufacturers Directory, by Innovative Designs & Publishing, Inc., 3245 Freemansburg Avenue, Palmer, PA 18045-7118. All Rights Reserved. Reproduction in whole or in part of any material in this publication is acceptable with credit. Publishers assume no liability for any information published. We reserve the right to accept or reject all advertising material and will not guarantee the return or safety of unsolicited art, photographs or manuscripts.

4 | Tech Directory 2010

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C elebrating 50Years

The International Fluid Power Society

IFPS Time Capsule

In 2010, the International Fluid Power Society (IFPS) will celebrate its 50th anniversary as the organization for fluid power and motion control professionals worldwide. In this column, which will run in every issue through 2010, we’ll take a look back at some of the most significant achievements and milestones in the Society’s history. Please participate in this column by submitting your own memories and photos to Kristine Coblitz at kcoblitz@fluidpowerjournal.com or Donna Pollander at dpollander@ifps.org.

1990-91: The Certified Fluid Power Engineer

hroughout the Society’s history, many individuals have worked tirelessly to make the organization the success it is today. One of its biggest accomplishments, the Certification Program, would not have been established without the assistance of the following individuals: • The early FPS/ICET Committee that developed the program for certification as Engineering Technician with a fluid power specialty consisted of Don Wiberg as chairman, Harry Ripple, Bruce Walker, and John P. Wilson. • The committee that wrote the early Fluid Power Specialist examination was chaired by Norman Dearth and included Gary Alzuhn, William Aminger, Hartley (Ben) Banton, Jack Johnson, Richard Minch, John Ortiz, Fred Ranney, Bob Renner, Allen Tucker, and Don Wiberg. • The Fluid Power Certification Policy Board was chaired by Don Wiberg and included Ed Briggs, Norman Dearth, Leon Gregoire, Robert Hanpeter, and Ned Stull. • The Fluid Power Technican Examination Committee was chaired by Norman Dearth and included Harold Albertson, Gary Alzuhn, Greg Crowley, John Ortiz, Don Wiberg, and William Zahn. • The Exploratory Committee activities relative to an Engineer Examination Committee resulted in two meetings: The first meeting was chaired by Robert Janeczko, and the second meeting was chaired by Robert Hanpeter.

Historical information for this column was obtained from Fluid Power – The Hidden Giant, John J. Pippenger, P.E. (Oklahoma: Amalgam Publishing Co., 1992).

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“From the beginnings of fluid power with Blaise Pascal in the 1600’s and the appearance of the first hydraulic press by Joseph Bramah in the late 1700’s; from the beginnings of pneumatic applications by Hero of Alexandria in 10 A.D. to the myriad of applications in our modernday world, the growth of fluid power has been phenomenal. Like all technology, the rate of day-to-day growth increases exponentially as time passes. There is no physical part of our everyday lives that is not touched (with great power and precision) by the fluid power industry. From hydraulic jacks to hydraulic machines that can “gently” stretch an aluminum sheet into the form of the common soda can, from a tire pump to the 400,000-rpm pneumatic dental drill, fluid power is all around us. Those who design, build, and repair in the fluid power industry must be on a path of constant learning to discover why fluid power works and what can be done with it in order to keep industry moving. Keep an open mind as you consider new possibilities for fluid power applications and make sure that you properly design new applications to complete their function in a safe manner. Remember the words of a very important person in the history of fluid power, Sir William George Armstrong: “It is our province, as engineers to make the forces of matter obedient to the will of man; those who use the means we supply must be responsible for their legitimate application.” – Robert Yund, AI, AJPP, AJPPCC, S, IHT, C&C, 2009 IFPS President

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Tech Directory 2010 | 5

FigureItOut igureItOut!

Robert J. Sheaf, Jr. | CFPAI, CFPAJPPCC, CFPAJPP, CFPE, CFPMIH, CFPMIP, CFPMMH, CFPMM, CFPMT, CFPS, CFPCC | CFC-Solar, Inc., www.cfc-solar.com, rjsheaf@cfc-solar.com

New Problem:

Sluggish Polishing Machine for a Casket Manufacturer A casket manufacturer has a machine that polishes the stainless steel exterior on finished caskets to a fine “brushed” look for one design that’s very popular. The polishing head is powered by a “servo valve” hydraulic system that allows them not only to vary the speed of the turning brushes but also maintain the force exerted on the brushes. The servo valve electronic controls incorporated a feedback signal from the hydraulic motor to assure a constant RPM speed for the brushes regardless of the pressure applied. This process has been in place for 10 to 15 years, and other than obvious maintenance fixes, it worked well. The workers did a good job of maintaining the ISO cleanliness code and temperature of the hydraulic oil. Oil samples always came back reflecting the good maintenance practices they had in place. However, a problem developed where the maximum brush RPM’s could not be reached and maintained, even though the circuit for advancing and applying pressure worked just fine. (See the accompanying circuit.) The coils of the servo valve were wired in parallel, and when the resistance of each was measured, they both appeared to be fine. The workers checked the signal coming out of the amplifier card controlling the servo valve, and it also seemed fine. They then replaced the servo valve with a new one after checking the continuity of the cable going to the valve. The system would work fine part of the time but not consistently. Any idea what could be wrong?

Answers and comments may be submitted to Robert Sheaf at rjsheaf@cfc-solar.com. Brush Force Brush RPM

Previous Problem:

Stainless Plate Mill Straightener System (from the September/October 2010 issue) A stainless steel rolling mill upgraded their “Plate Straightener” machine. The old hydraulic system was 40 to 50 years old with old manual valves and was overdue for an upgrade. The original circuit consisted of three sets of top rolls with a cylinder pressing down on each end. There were also three sets of fixed rolls on the bottom. Each cylinder had a pilot to open (10,000-psi rated) check valve on each port with an Enerpac relief in the cap end set for 9,000 psi. Each Set @ 9000 PSI cylinder was controlled with a manual three-position shear-type, four-way, rotary directional valve with all ports blocked in the center position. The operator would adjust the position of each roll by individually advancing one cylinder at a time watching its digital type A B position readout. Once it was positioned, he would leave the shear-type directional T P valve in the blocked center position. He would do this to all six cylinders. As the thick sheet of stainless would enter the rolls, they would be pinched or squeezed, causing the plates to straightSet @ en. If for some reason the plate would not 2000 PSI submit to the squeeze, something had M to give. The force pushing up on the rolls would reach 9,000 psi, and the cylinders would start to retract, allowing the warped plate to pass through. The system worked well before the upTypical roll cylinder circuit grade was installed. 2 required per roll The upgrade replaced the manual shear-type directional valves with solenoidoperated, three-position directional valves mounted on a manifold. The new directional valves were the sliding spool type with float centers. All of the old plumbing and hoses were replaced with new stainless tubing and hoses. The installation really looked nice and professional. (See attached circuit for a typical cylinder circuit.) After the system was started and debugged, the workers ran a warped plate through the machine and found it would not straighten the plate. The plate would just pass under the cylinders, pushing them up and not causing any force to straighten the plates. They felt that surely it was just air in the cylinders and all they had to do was bleed off all the trapped air. However, bleeding the air did not help the problem. During the troubleshooting process, they found all the PO check valves were leaking, so they ordered rebuild kits. After verifying the rebuilt checks would hold pressure, they re-installed the PO checks, bled all the air out, and still had the same problem of the cylinder backing off.

Solution:

1500 PSI

1650 PSI Water Supply

6 | Tech Directory 2010

The new design using the “float” center sliding spool valve should have worked fine. Pilot to open checks should have the directional valve ports open to tank to prevent any residual pressure or pressure build-up from leaking spool valves that might hold the checks open. I had designed the circuit for the upgrade and was sure it would work. I was talking to the operator asking if he had any other observations or problems, and he commented that the cylinders stroked faster when he would fully retract and extend them. It dawned on me that these large cylinders were cavitating on their extending stroke, and this void would allow the cylinders to retract. We installed flow controls on the rod side and adjusted them just enough to keep the cylinders from running away from the pump flow. The old plumbing probably had orifices or restrictions in the piping and was not noticed during their removal. www.ifps.org | www.fluidpowerjournal.com

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Tech Directory 2010 | 7

The

Perfect By Brendan Casey

Hydraulic Fluid

W About the Author

Brendan Casey has more than 20 years experience in the maintenance, repair, and overhaul of mobile and industrial hydraulic equipment. For more information on reducing the operating cost and increasing the uptime of your hydraulic equipment, visit

www.HydraulicSupermarket.com

8 | Tech Directory 2010

hen I present hydraulic maintenance training, a concept that I always enjoy explaining to my students is what I call the perfect hydraulic fluid. And it’s very simple. The perfect hydraulic fluid would have a viscosity index (the change in a fluid’s viscosity relative to temperature) represented by a horizontal line intercepting the Y axis at 25 centistokes (Fig. 1). Of course, no such fluid exists, and I don’t expect that such a fluid will be developed in my lifetime. But if such a fluid were developed, its creator would have the key to a gold mine. Fluid viscosity is one of the factors that determine whether full-film lubrication is achieved and maintained. If load and surface speed remain constant but elevated operating temperature causes viscosity to fall below that required to maintain the hydrodynamic film, boundary lubrication occurs with the possibility of friction and adhesive wear. Fig. 2 shows how this can manifest itself in an axial piston pump. The gold-colored varnish deposits are evidence that this hydraulic system has been operating over temperature. Due to low fluid viscosity, the lubricating film between piston and bore has been lost. The resulting friction has super-heated the piston, causing it to expand in its bore to the point of interference. Once this happens, the tensile force pulls the slipper(s) from the piston(s), resulting in catastrophic failure. Table 1 lists typical optimum and permissible viscosity values for an axial piston pump. Note the optimum viscosity range is 16 to 36 centistokes. This is the viscosity range where the system will operate most efficiently— highest ratio of output power to input power. Stated differently, this is the viscosity range where fluid friction, mechanical friction, and volumetric losses are optimal for system performance. But this only tells us half the story. There’s critical information missing. We need to know what operating temperature equates to each of these viscosity numbers. To establish this, we need to consider the weight of the fluid in the system and its viscosity index, represented by its gradient on a temperature/viscosity diagram. The flatter the line, the wider the allowable operating temperature range for both optimum and permissible viscosity. Here’s where the perfect hydraulic fluid comes in. If you could use a fluid that “flat-lined” on a temperature/viscosity diagram at 25 centistokes (Fig. 1), a significant variable is removed and problems aris-

ing from insufficient fluid viscosity are instantly solved. And that would be worth paying good money for. Alas, such a “magic pill” solution is not available to us right now, so we can’t control the rate of change of viscosity with temperature—or not to the ideal degree, at Figure 1: least. But we can control operating temperature. So here’s another ideal: the climate controlled hydraulic system. Most us would have driven or rode in an automobile fitted with climate control. You dial in say, 75°F (24°C), and regardless of whether it’s snowing outside or hot enough to fry an egg, the climate control heats or cools the auto’s interior to maintain the selected temperature. What if your hydraulic equipment had a similar system? You tell a computer the weight and viscosity index of the fluid you’re using and then select the Figure 1:

Viscosity cSt 25 25

Viscosity cSt Viscosity cSt

Temperature °C Temperature °C Temperature °C

Fig. 1: Temperature/viscosity diagram of the perfect hydraulic fluid Figure 2: Figure 2:

Fig. 2: Catastrophic failure caused by low fluid viscosity

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viscosity you want the system to run at…perhaps 25 centistokes. Then regardless of whether its summer or winter and the amount of heat load (internal leakage, etc.) on the system, the “climate control” heats or cools the oil as necessary to maintain optimum viscosity. The best part? It’s possible just not very practical. So with the perfect hydraulic fluid not available and the climate-controlled hydraulic system not feasible in most applications, human intervention is required. Someone has to do some legwork. Some of the variables that must be considered include • starting viscosity at minimum ambient temperature • maximum expected operating temperature, which is influenced by system efficiency, installed cooling capacity, and maximum ambient temperature • permissible and optimum viscosity values for individual components in the system Once all these variables have been taken into account and a fluid with a suitable weight and viscosity index has been selected, an additional column of information can be added to Table 1, so that it looks like that shown in Table 2. Having defined the operating parameters shown in Table 2 for a specific piece of hydraulic equipment, damage caused by low or high fluid viscosity can be prevented by installing fluid temperature alarms and/or shutdowns. In the absence of the perfect hydraulic fluid and short of installing climate control on all hydraulic equipment, this is the only way to ensure failures similar to that shown in Figure 2 don’t happen. For more information about hydraulic failures and how to prevent them, visit www.PreventingHydraulicFailures.com

Table 1: Typical Viscosity Values for Axial Design Piston Pump Viscosity Value

cSt

Minimum Permissible

Minimum Optimum

Optimum Bearing Life

Maximum Optimum

Maximum Permissible

1,000

Table 2: Viscosity with Corresponding Temperature Values Viscosity Value

cSt

Temperature (VG68 with VI ~ 95)

Minimum Permissible

95ºC

Minimum Optimum

78ºC

Optimum Bearing Life

65ºC

Maximum Optimum

55ºC

Maximum Permissible

1,000

2ºC

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Tech Directory 2010 | 9

Lube

or Not

toLube

By Richard F. Bullers, Senior Applications Engineer SMC Corporation of America, rbullers@smcusa.com

he question of whether or not to supply airline lubrication often comes up during the installation of pneumatic components, in the design of new machinery, or when rebuilding or retrofitting existing equipment. Understanding the pros and cons of using airborne lubrication can save you time, money, and trouble. To get started, first check the component’s lubrication requirement by reading the manufacturer’s product precautions. Neglecting this simple step may void the product warranty, so doing this easy homework up front pays off. When lubrication is required, the desired effect is to provide just enough airborne oil to create a thin film of lubricant between the mating surfaces of moving parts to extend the life of the pneumatic component. Careful attention must be given to specifying, installing, and correctly adjusting lubrication equipment and using the correct lubricant to accomplish this task successfully. Again the manufacturer’s product literature will likely be the best source of information to correctly match the product’s capabilities to the application requirements. We must also be aware that some applications have environmental extremes that require special attention to component lubrication. In high-heat environments, machinery subjected to being washed down for cleaning, or

where chemical contamination may occur, the lubricant may be compromised or rinsed away and need to be replaced on a regular basis to extend the life of a pneumatic component, primarily linear actuators. In these situations, the life of the pneumatic component may be extended for a period of time by providing airborne lubrication, and there is a reasonable argument for supplying it. By the same token, it is important to note these underlying factors actually exist and that oil is not being used simply because “that’s the way we’ve always done it.” So now that you have read the manufacturer’s product precautions and checked for conditions that might require lubrication, what if nothing indicates that lubrication should be used? Should you install a lubricator anyway, perhaps just to “play it safe”? Consider the consequences first. For example, standard lubricators are adjusted with a general procedure based on counting the number of drops per minute though a sight dome and correcting with a needle valve typically as the machine is running. How many drops per minute is often a matter of guesstimate rather then careful experimentation based on peak air flow demand, distance the lubrication has to travel, and nature of the equipment’s lubrication requirements. Given this, excessive lubrication is often applied. This lubricant ends up underneath machinery and in the surrounding air. In extreme cases of over-lubrication, oil mist may be visible as a haze throughout the surrounding environment. If the lubricator is over-adjusted to correct the issue, machine damage from lack of lubrication may occur, and often overlubrication is tolerated for this reason. Oil in the environment should be considered the same as an uncontrolled hazardous substance. It constitutes increased risk of fire, health-related issues such as respiratory illness, and falling incidents. If lubricators are being correctly applied and excess oil is not apparent in the atmosphere, there is always the microscopic oil you cannot see still floating around in the air. When the incorrect oil is used or if someone does not fill the lubricators on a timely basis, equipment damage is often the result. Hopefully the machine being down won’t be at the worst possible moment. In the meantime you are still paying for purchasing lubrication equipment, lubricant, oil dry for spills, and the fellow with the best intentions who made an honest mistake. When lubrication is applied where application concerns do not require it and lubricators are incorrectly adjusted, the results can be costly as summarized Table 1. If your evaluation process has included a review of the manufacturer’s recommendations and no environmental conditions exist that may wash away or degrade lubrication over time, then what other options are available?

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10 | Tech Directory 2010

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Fortunately, there is a straightforward answer to this question. The majority of contemporary pneumatic components does not require additional lubrication and have the added benefit of using less energy than their predecessors. Today’s pneumatic linear actuators now incorporate specialty piston seals that cup and store long lasting types of grease that remain for tens of millions of cycles. Gone, for the most part, are the simple o-ring piston seals of yesteryear that needed a continual oil supply to keep from rolling or extruding out of position. Actuator rod bearing materials exude lubricity while rod seals evenly spread, yet retain, a maximum amount of grease. Directional control valve design has evolved to extend the life of the component to tens of millions of cycles or more with clean dry air, while at the same time reducing energy consumption to fractions of a Watt. When designing new equipment, the choice is clear that “non-lube” components are of considerable advantage, but what if your existing machinery is already using lubricators? What if you want to address the environmental, health, and cost issues that now come to mind, but do not have unlimited resource to retrofit every machine? Immediate action to help clear the air can be taken by using a device known as an exhaust cleaner. This type of product can collect the exhaust air from single or multiple directional control valves and reclassify air by removing the bulk of oil mist at microscopic levels. Exhaust cleaners serve a useful purpose in applications where lubrication cannot be avoided and as an intermediate step in weaning your operation off the harmful and costly effects of unnecessary lubrication. The answer to the question of “To lube or not to lube?” starts with reviewing current conditions and practices and changing how you think about how and why you specify lubrication. In your efforts to change the game by making your environment healthier and less costly to maintain, you can pass along the benefits of eliminating unnecessary lubrication by making informed decisions in your machine design and maintenance practices.

Compressed Air System Considerations

Lubricated Non-Lube

Labor expense of repeated filling of oil reservoirs

YES

Expense of purchasing and stocking oil.

YES

Additional expense of specifying, purchasing, stocking, installing, and, maintaining, lubrication equipment

YES

Purchase of oil dry for spills

YES

Improper adjustment of lubrication equipment possible

YES

Excessive oil use resulting in waste

YES

Accelerated component wear and if oil supply is inadequate, not replenished, or discontinued

YES

Oil pooling under valve exhausts when used in excess

YES

Oil spillage

YES

Risk of the incorrect oil being used resulting in damage and/or down time

YES

Lubricating oil health and fire considerations

YES

Oil mist in the atmosphere presenting a health hazard

YES

Damage to pneumatic instrumentation equipment sensitive to oil contamination

YES

Longer cylinder life then non-lube type

YES*

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*The increase in life may be 10% or higher depending upon the grease used actuator type, and operating conditions. In extreme conditions lubrication may be the best alternative and worth the additional risks and expenses. In the majority of industrial pneumatic environments and applications, the risks and expenses outweigh the benefit. Request more information at www.fluidpowerjournal.com

www.ifps.org | www.fluidpowerjournal.com

Tech Directory 2010 | 11

Submitted by Jeannine Uehling, Minnesota Fluid Power Skills Competition Director, IFPS Chapter 5

As diverse as the applications for fluid power, so too were the contestants of the 2010 Minnesota Fluid Power Skills Competition. This competition has a long history of bringing together the top six students from the four technical colleges in Minnesota who provide exemplary fluid power programs. Ernie Parker and Bob Yund from Hennepin Technical College-Eden Prairie campus hosted this year’s competition. The competition was nearly four hours long with the Chapter 5 Education Meeting and Awards Dinner following. The competition consists of four very distinct skill sets: • In the Troubleshooting test section, contestants must be able to think on their feet under pressure while troubleshooting the schematic provided along with the customer’s description of the characteristic problems being experienced. • In the Fitting Identification test section, patterned after the International Fluid Power Society’s (IFPS) Job Performance Test, contestants are provided a Parker Thread Identification Kit and must identify a selection of fittings commonly found in industry. • In the Special Project test section, contestants are provided with a written description of a pneumatic system. They must select the correct pneumatic components, assemble them, draw the schematic, and demonstrate their system operation. • In the Written Test section, the contestant receives a written test presented in the same format as the IFPS certification tests.

12 | Tech Directory 2010

2b 3a

Fig. 1: Competition judge Scott Aldridge

with contestant Joshua Gramentz in the face-to-face troubleshooting test section where Aldridge is the customer with a hydraulic system failure.

Fig. 2: (a) Ben Lapatka reviews the section

instructions of the Fitting Identification Test section prior to the start of the exam, (b) Benjamin Flygare utilizes tools available to correctly identify the fittings donated to the Skills Competition by Doug Olson from Parker Hannifin Corp.

Fig. 3:

(a) Randy Meyer from John Henry Foster observes the contestants for the Special Project test section: front right is Jacob Dauer and (moving clockwise) Wade Wilke, Justin Skwira, Nick Schroeder, Ross Peterson, and Jeff Arbogast; (b) Joshua Goertz during the Special Project test section.

Fig. 4: Jeff Arbogast shown with Ross Peterson, Joshua Gramentz, and Jacob Dauer in the next row.

www.ifps.org | www.fluidpowerjournal.com

Fig. 5: Harley Bergeren awards the Past Presidents Scholarship to Cory Besel from Hennepin Technical College-Brooklyn Park. Fig. 6: The students competing in the 2010 Minnesota Skills Competition

(left to right): Front Row: Anthony Hallberg, Ben Lapatka, Wade Wilke, Jacob Dauer, Justin Kolander, Murdock McNickle, Josh Boltz, Jeff Gullick, Joshua Gramentz; Back Row: Dan Sarsland, Andrew Long, Joshua Goertz, Justin Skwira, Nathaniel Larson, Ethan Henneman, Joe Herder, Cory Besel, Nick Schroeder, Jeff Arbogast, Ross Peterson, John Siegle, Benjamin Flygare, Kyle Bahl. (Not shown: Mark Frankena)

Fig. 7: Top Five Awards (left to right): First Place: Anthony Hallberg, Hennepin Technical College-Eden Prairie. Fifth Place: Josh Boltz, Hennepin Technical CollegeBrooklyn Park. Fourth Place: Ross Peterson, Hennepin Technical College-Eden Prairie. Third Place: Murdock McNickle, Minnesota West Technical College-Granite Falls. Second Place: Jeff Arbogast, Hennepin Technical College-Brooklyn Park

Fig. 8:

Jeff Theisen, Chapter 5 president, with first place competition winner Anthony Hallberg

At the competition dinner, the instructors announced the names of the outstanding students who demonstrate not only academic excellence but also consistently go above and beyond what is expected of them, are always there for special projects, and are sought out by fellow students to help when needed. The outstanding students were • Wade Wilke from Alexandria Technical College • Liza Esterly from Hennepin Technical College-Eden Prairie • Joshua Gramentz from Minnesota West Community and Technical College • Josh Boltz from Hennepin Technical College-Brooklyn Park Harley Bergeren awarded the IFPS Chapter 5 Past Presidents Scholarship to Cory Besel from Hennepin Technical College-Brooklyn Park. Besel plans to use the scholarship toward completing his four-year degree. It is thanks to the dedicated volunteer efforts of the judges and the companies they work for, who provide them with the time to participate, that this competition has been so successful. Thanks to Randy Meyer from John Henry Foster, Scott Aldridge from Power Systems, Bryan Anderson from Oildyne Parker Hannifin, Wayne Walker from Sun Source, Heidi Kloskin from Hose and Conveyors Inc., and Tom Nelson from Catco. Scott Aldridge, applications engineer with Power Systems and graduate of Hennepin Technical College-Eden Prairie, provided words of wisdom to the students through his presentation, touching on the importance of their professionalism, continuing education, certification, and thoughts of appreciation to an industry that provides incredible opportunity. The evening culminated with the announcement of the top five awards. The top five students received plaques and scholarships in the amounts of $200 for third place, $400 for second place, and $600 for first place. Jeff Theisen, Chapter 5 president, from Eaton Corporation provided the evening’s Education and Skills Competition Awards Meeting. The Chapter would like to add special thanks the IFPS, the Fluid Power Education Foundation, and John Groot. Plans are being made for the 2011 Minnesota Fluid Power Skills Competition to be held at Hennepin Technical College-Brooklyn Park campus on Thursday, April 21, 2011. www.ifps.org | www.fluidpowerjournal.com

Request more information at www.fluidpowerjournal.com

Tech Directory 2010 | 13

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www.ifps.org | www.fluidpowerjournal.com | Tech Directory 2010 | 17

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18 | Tech Directory 2010 | www.fluidpowerjournal.com | www.ifps.org

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Tech Directory 2010 | 19

By Dan Helgerson, CFPAI, CFPAJPPCC, CFPMT, CFPCC, CFPS Cascade Steel Rolling Mills, Inc. dhelgerson@schn.com

I Know, It Hertz

am pretty sure I am going to get some flack from what I am going to say in this article, but before you conclude that I don’t know what I am talking about, hear me out. It is not my intent to turn people against using one of the most excellent components for accurate control of fluid power systems. In this, as in all the other articles, I want to stimulate your thinking. We all need to be sure that we represent the best in fluid power professionalism. This includes looking at the energy consumption of the systems we use.

One of the favorite valve categories in fluid power is the servo. Since its inception, the servo valve has allowed remarkable control of speed and position in processes controlled with fluid power. I recently had an opportunity to take part, along with a number of Certified Fluid Power Accredited Instructors, in a review of the new Certified Fluid Power Electronic Specialist study guide. As we went through the material, we were reminded that the standard flow rating for a servo valve is determined using a 1000-psi pressure drop through the valve; 500 psi P to A or B, and 500 psi A or B to T. I was half expecting and certainly hoping that there would be a collective gasp of incredulity as this was presented, but then we were all experienced professionals and had come to accept this as normal. The 1000-psi pressure drop is accepted as the characteristic necessary for control. I think that a lot of us do not automatically think of pressure drop in terms of energy consumption. Oh, I know we immediately recognize that there will be some more kilowatts pumped into the system and that will mean more Btu’s to remove. We use our rules of thumb and various charts to select the heat exchanger and the fine filtration. It is simply accepted as the cost of control. Let’s think about that for a moment with energy in mind. In a system where I need 2000 psi at an actuator controlled by a servo valve, I would need to have

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3000 psi available. That means that right from the get-go, I am sacrificing 33% of the energy needed for the system. So the question is this: why do we need the high pressure drop? In the study guide, the servo valves are defined as either “flapper-nozzle” or “jet-pipe” in their control mechanism. High-pressure fluid is used to shift the valve spool and also to develop a high-velocity flow through the jet-pipe or nozzle. The result is that the servo is a very dynamic valve. Like a racehorse waiting at the gate, the spool is excited, just waiting for the command to go. Because of the pressure and consequent high velocity, the spool can move very fast and will respond quickly to subtle changes in the system. This speed is very important in developing the control expected of the servo valve. However, we do not always need the speed. There are times when accuracy and repeatability are the issues and speed is not the biggest factor. There is a class of servo valves that are not often discussed but that could provide an excellent alternative to the customary high delta P valves. These valves are driven by a stepper motor. This is a rotary motor with digital positioning. They require no pressure drop to change the spool position, and because they are digital, some operate at zero hysteresis. I have seen an application where there was remarkable positioning control of a cylinder using this type of servo with only a 75-psi pressure drop through the valve. The downside is that the response time is relatively slow, but we need to ask what response time is necessary for our application. The response times that are listed for valves are based on their ability to jump from one extreme to another in a certain time frame. The distance is typically 90% of the full potential movement of the spool, and it is rated Visit our by how many times it can do it within a span of one second. Some of the Website for flapper-nozzle and jet-pipe servo valves have spools that can travel almost FREE all the way from one side to the other 250 times in one second and are said samples and to have a response time of 250 hertz. The stepper-motor driven valves have literature a much slower response time--about 75 hertz. At 250 hertz, the spool in a Available in Kits. Flaretite, Inc. typical servo valve can leap from one extreme to the other in 4 milliseconds. Phone: 810-750-4140 The stepper-motor driven valve takes 13.3 milliseconds to cover the same distance. To give you an idea of how fast that is, the lights in the room where you are reading this article are probably flickering on and off at 60 hertz, but Request more information at www.fluidpowerjournal.com you perceive it as a continuous light source. These spools can bounce around inside the valve bodies up to four times faster than the light bulb flickers. That is pretty impressive and makes for a good sales presentation. However, for many of our applications, the major activity of the valve1/4 is _9_08flaretite.indd 1 1/15/09 9:48:20 AM within a very narrow band of spool motion. When we are holding a cylinder at some location and want to keep it within one kazilienth of an inch, the spool Typical new oil. Keeping oil clean – It’s your best insurance! usually has to travel a very short distance, modulating to hold the cylinder position. Moving within this narrow band may dramatically reduce the necessary 1 Clean incoming oil – because new is NOT clean oil speed of the spool, and the fact that a valve may provide zero hysteresis may Keep your first fill from starting things off on a dirty be more valuable to the control system. foot. Our systems remove impurities in your new oil. I just thought of something while I was writing and I need to take a tenThese contaminants are the seeds of increased minute break to do some calculations. If some of you want to stick around maintenance costs in the form of downtime, and help out, that would be great. The rest of you can take a break but be wear, and repair. Don’t let your oil back in ten minutes… look like this! For those of you who are staying, I need to figure out the acceleration reKeep oil clean – remove solids AND moisture 2 quired to achieve a 250-hertz and a 75-hertz spool movement before I go too A Harvard Filtration system on your machinery far out on a limb. I am going to assume a total spool travel of one inch. I am will keep your investment clean and operating then going to assume a travel distance of 0.0625 inches for the valve modulaat its peak performance. In hydraulic tion. The result will show the performance differences between the valves in systems, 70-80% of failures are due to Contaminated oil. the critical modulating position. I appreciate your help. The results will be the contamination. The Harvard Constant basis for the next statements when everybody returns. Contamination Control® keeps moisture and Ok, we are ready to resume. This is what we found out: A system capable of contaminants from accumulating in your oil. 250 hertz and with a spool travel of one inch would have to see an acceleration This prevents premature wear, and reduces of about 500 g’s. That is the reason for the high pressure drop. The pressure costs. Let us show you how one company provides the necessary force to develop that rate of acceleration. A 75-hertz reduced their maintenance costs by 40%. The same oil after 48 hours in use with valve with the same travel needs less than 50 g’s of acceleration. Now, let’s take Call us today. a Harvard system. a look at the critical time for both valves to jump 0.0625 inches responding to a -7 command signal. The faster valve will cover the distance in 6.2 x 10 seconds. The slower valve will cover the distance in 6.8 x 10-6 seconds. It is true that Constant Contamination the 250-hertz valve is 11 times faster, but the actual time difference is 0.0062 Control can be applied to engines, milliseconds. This would be considered a tie in a photo finish. transmissions, The point, as always, is this: Choose the components that will do the job hydraulics, turbines, without consuming more than the necessary amount of energy. Don’t be gear boxes, diesel fuels, heat transfer awe-struck by a hertz rating. Figure out what is actually needed. Forget the 800-523-1327 l 608-882-6330 fluids, AND MORE! fudge factor, shun the shortcut, and reject the rule of thumb. Do the math. www.harvardcorp.com Choose the best.

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Tech Directory 2010 | 21

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A & A Manufacturing Company Inc. ABZ, Inc. Activant Adsens Technology, Inc. Air Logic Airline Hydraulics Air Logic Airmo, Inc. ALA Industries, Ltd. All Sensors Corp. Allen Orton LLC Almo Manifold & Tool Company American Aerospace Controls, Inc. American Cylinder Co., Inc. American Sensor Technologies, Inc. AMETEK Automation & Process Technologies Anderson Metals Corp., Inc. Applied Industrial Technologies ARGO-HYTOS, Inc. ASCO Valve, Inc. Ashcroft Inc. ASI Inc. Assured Automation ATOS S.P.A. Attica Hydraulic Exchange Corp. Automation Products, Inc. - Dynatrol Div. Automation Systems Interconnect, Inc. Axiomatic Technologies Corporation Balluff, Inc. Behringer Corp. Beswick Engineering Co., Inc. Bosch Rexroth Pneumatics Brand Hydraulics Bray Controls, Div of BRAY Int’l Inc. Brennan Industries Inc. Bucher Hydraulics Inc. Burkert Fluid Control Systems CADSYM Canfield Connector Central Illinois Mfg. Co. (Cim-Tek) Filtration Clippard Instrument Laboratory, Inc. Coilhose Pneumatics Command Controls Corp. Component Sourcing International LLC Continental Hydraulics Control Enterprises, Inc. Controlled Motion Solutions, Inc. Cox Instruments CPV Manufacturing, Inc. Cross Mfg. Inc. CS Unitec, Inc. Custom Sensors & Technologies (CST) Cyber-Tech, Inc. Dakota Fluid Power DEL Hydraulics DELTA Computer Systems, Inc. Donaldson Company Inc. Duplomatic Div. UHI, Limited DynaQuip Controls EAO Switch Corporation Eaton Hydraulics Electro-Sensors Inc.

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www.ifps.org | www.fluidpowerjournal.com | Tech Directory 2010 | 23

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Electroswitch Elma Electronic Emmegi Heat Exchangers, Inc. Energy Manufacturing Co., Inc. Enfield Technologies Engineered Sales, Inc. Exair Corporation Fabco-Air, Inc. FAMIC Technologies Inc. Faster Inc. FCI Automation Feroy Company, Inc. Flint Hydraulics, Inc. Flodraulic Group Flodyne Controls, Inc. Flow Technology Flow-Tek, A Subsidiary of BRAY Int’l Inc. Fluid Line Products, Inc. Fluid Power, Inc. Fluid Power Products, Inc. Force America Futek Advanced Sensor Technology Inc. FW Murphy Gefran Gems Sensors & Controls GS Hydraulics, Inc. Hach Flow Meter Products & Services HAWE Hydraulics Haydon Kerk Motion Solutions, Inc. Hedland Flow Meters Helium Leak Testing, Inc. Hercules Sealing Products High Country Tek, Inc. Himmelstein, S. & Co. HKX, Inc. Hoffer Flow Controls Humphrey Automation Inc. Humphrey Products Company HUSCO International Inc. Hydac Inc. Hydradyne Hydraulics LLC Hydramation, Inc. Hydraulic Resources, Inc. IFM Efector Inc. Industrial Hydraulic Services Industrial Servo Hydraulics, Inc. Industrial Specialties Mfg., Inc. Innotek Corporation Integrated Hydraulics, Inc. IQ Valves (Formerly Teknocraft) ITT JH Technology, Inc. J.R. Merritt Controls Inc. Kanamak Hydraulics Inc. Kavlico Keller America, Inc. Kraft Fluid Systems, Inc. Kurz Instruments, Inc. La-Man Corporation LCR Electronics Lynch Fluid Controls, Inc. M & M Rogness Equipment Company

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24 | Tech Directory 2010 | www.fluidpowerjournal.com | www.ifps.org

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www.ifps.org | www.fluidpowerjournal.com | Tech Directory 2010 | 25

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Macro Sensors Madison Company Magnetek Maradyne Corp./Marion Fluid Power Div. Mark Hydraulic Company Inc. Marsh Bellofram Max Machinery Moog Motion Industries MP Filtri USA, Inc. MTS Sensors MTS Systems Corporation Murrelektronik, Inc. NBB Controls, Inc. NC Servo Technology Net Motion Inc. Norgren NOSHOK, Inc. Novotechnik U.S. Inc. Nycoil Company OEM Controls, Inc. Oil-Rite Corporation Omega Engineering Optex-FA Panasonic Electric Works Corp. of America PCB Piezotronics Inc. P.E.P. Peter Paul Electronics Pinnacle Systems, Inc. Pneumatic Cylinders & Couplers Inc. (PNEU C&C) Poclain Hydraulics Inc. Pressroom Electronics Pressure Controls Inc. Pressure Systems, Inc. Progressive Hydraulics, Inc. Proportion-Air, Inc. Pulsafeeder, Inc. PWM Controls Inc. Reelcraft Industries, Inc. Rego Cryo-Flow Products Rite pro, Inc., A Subsidiary of BRAY Int’l Inc. Sang-A Pneumatic Corp. Sauer-Danfoss Schmalz Inc. Schroeder Industries Schunk Inc. Scorpion Technologies Ltd. Semiconductor Circuits Inc. Servo-Tek Products Company Inc. SICK, Inc. Sierra Instruments, Inc. Source Fluid Power Spartan Scientific SPC Sang-A Pneumatic Corp. Spectronics Corporation Spencer Fluid Power Suco Technologies, Inc. Sun Hydraulics Corporation Swift-Cor Precision, Inc. Switches Unlimited Switching Solutions Inc. SymCom, Inc.

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26 | Tech Directory 2010 | www.fluidpowerjournal.com | www.ifps.org

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28 | Tech Directory 2010

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Tech Directory 2010 | 29 8/2/2010 1:38:38 PM

Web

www.alloysandcomponents.com Alloys & Components, Southwest

www.ametekapt.com/adwords/ Linear_Position.cfm Ametek

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Browse our Web site for information on the products we offer! • Hard Chrome Plated Rod • Honed ID Cylinder Tubes • Continuous Cast Bronze Bars • Continuous Cast Aluminum Bronze Bars • Aluminum Bars & Ductile Cast Iron • Ductile Cast Iron • Alloy Bars • Heavy Wall Mechanical Tube All the Hydraulic Hardware You'll Ever Need! Contact us at sales@alloysandcomponents.com or call toll free 800-441-1994.

Gemco durable and reliable, absolute linear position products are based on unique technologies, including Magnetostriction. Our sensors come in a variety of packages and outputs, with features not found in competitive units. The Gemco line of Linear Displacement transducers (LDT) are designed to withstand harsh environments. If you have an application requiring linear feedback and control, Gemco has the solution. Call Toll Free 1-800-635-0289

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ARGO-HYTOS manufactures sophisticated filter solutions, mainly applied in hydraulic and lubrication systems as well as in transmissions. The range of solutions that have been implemented extend from stationary industrial plants to mobile applications. Contact us at: ARGO-Hytos, Inc. P.O. Box 28 Bowling Green OH, 43402 Phone 419.353.6070 Fax 419.354.3496 info.us@argo-hytos.com www.argo-hytos.com

Clippard Pneumatic Control Devices

30 | Tech Directory 2010

Clippard’s complete line of Minimatic® Control Devices includes over 5,000 standard products. Some of the many products offered include valves, cylinders, fittings, modular components, push buttons, stainless steel cylinders, electronic manifold cards, circuit analyzers and pre-piped manifold subplates. Visit www.clippard.com to find complete product information and specifications, engineering drawings, ordering information, literature downloads, useful calculators, technical assistance, distributor information and more.

FASTER S.p.A. with over fifty years experience in the hydraulic industry, has designed and manufactured over five hundred million quickrelease couplings, which are covered by twenty patents. Our company is presently developing and producing a wide range of quick release couplers ranging from medium to very high pressures. All FASTER Couplers are designed according to international standards. Please visit our website for more information. www.ifps.org | www.fluidpowerjournal.com

IndustryNews

www.yatesind.com Yates Industries

Midyear U.S. Construction Machinery Exports Up 15 Percent Compared to 2009 Exports of U.S.-made construction equipment increased in the second quarter of 2010, and total construction machinery exports at midyear were $7.4 billion, a 15-percent gain overall compared to January-June 2009 numbers, according to the Association of Equipment Manufacturers (AEM). The AEM off-road equipment manufacturing trade group consolidates U.S. Commerce Dept. data with other sources into global trend reports for members. Exports to Central and South America each gained 14 percent compared to midyear 2009 - $753 million for Central America and $1.4 billion for South America. Asia’s export purchases increased 5 percent to $984 million. European growth was flat with exports totaling $777 million, about the same as JanuaryJune 2009, and exports to Africa declined 20 percent to $423 million. Australia/Oceania took delivery of 37 percent more American-made construction machinery for a total $679 million, and exports to Canada increased 32 percent and totaled $2.4 billion. The top destinations for U.S. construction machinery exports January-June 2010 were: (1) Canada - $2.4 billion, up 32 percent; (2) Australia - $625 million, up 32 percent; (3) Mexico - $549 million, up 8 percent; (4) Chile - $462 million, up 9 percent; (5) Brazil - $376 million, up 74 percent; (6) China - $242 million, up 15 percent; (7) Colombia - $189 million, up 13 percent; (8) South Africa – $173 million, down 25 percent; (9) Peru - $168 million, down 5 percent; (10) Belgium - $153 million, down 31 percent. www.aem.org

Yates Cylinders Offer: • H6 Series - Heavy Duty Hydraulic (3000 PSI) • H4 Series - Medium Hydraulic (up to 1500 PSI) • A4 Series - Heavy Duty Steel Air (250 PSI) • A2 Series - Aluminum Air (250 PSI) • Air/Oil Intensifiers • All Stainless Steel Cylinders • Air/ Hydraulic Welded & Mill Type Cylinders • Special Cylinders per Customer Supplied Prints and Specifications Yates Industries, Inc. Yates Industries South, LLC 23050 Industrial Dr. E. 3401-J Highway 20 St. Clair Shores, MI 48080 Decatur, AL 35601 586.778.7680 ph 256.351.8571 ph 586.778.6565 fax 256.351.8571 fax

www.yuken-usa.com Yuken

PIRTEK Kent Awarded Subcontract to Complete Hose Renewal PIRTEK Kent, based in Seattle, Wash., and owned and operated by United States Army Veteran Gabriel Gilliam, is completing a major project to remove, fabricate, and install over 200 hoses on the United States Coast Guard Polar Sea at Todd Pacific Shipyards. The company bid the project and won the contract by beating competitive quotes from several other local hose shops. Each hose assembly was removed, fabricated, tested, tagged, and re-installed per the requirements of Todd and the U.S.C.G. www.pirtekusa.com/kent

‰

Stonebridge Partners Completes the Acquisition of Attica Hydraulic Exchange Stonebridge Partners completed the acquisition of Attica Hydraulic Exchange on August 2, 2010. Stonebridge is partnering with industry executive Shirish Pareek, who will be the CEO of a new holding company called Hydraulex International, which intends to acquire complementary hydraulics companies to augment the Attica platform company. As part of this transaction, Attica’s top management team will stay in place. William Wildner, Jr. will remain as Attica’s president, P.K. Guha will oversee all sales and marketing activities, Cathy Ayers will continue to be the vice president of operations, and Sam Caruso has been promoted to vice president of materials management. For more information, visit www.stonebridgepartners.com.

The site offers a number of useful tools for customers and for those who wants to learn more about Yuken. We feature a “Members” section for checking inventory and reviewing service manuals, as well as pricing, on either a downloadable price sheet or an interactive resource. Distributors from across the country and our repair and warranty center information are there. Learn about Yuken’s certifications, check out the product literature, and get a peak at new products, all at our helpful website!

www.ifps.org | www.fluidpowerjournal.com

Parker Hannifin and Hydrasun Sign Strategic Partnership Agreement Parker Hannifin and Hydrasun, a UK provider of customized fluid transfer, umbilical, and process control solutions, have signed a strategic partnership for the development, sales, and support of fluid and gas handling and process control technologies. The agreement coincides with the appointment of Hydrasun as Parker Hannifin’s first premier distributor to be appointed in the UK. It also forms part of a long-term program for both companies to develop new and innovative transfer control solutions. www.parker.com

Tech Directory 2010 | 31

PeopleInTheNews

Philippe Halloin

Parker Hannifin Philippe Halloin has been named vice president of operations for the Seal Group. He is responsible for coordination, optimization, and strategic alignment—including additional strategic acquisitions—of the European Seal Group’s three divisions (Packing, O-Ring, and Chomerics), as well as nine Europe-wide locations. Mr. Halloin joined the company’s Hydraulic Controls Division in 1986. www.parker.com

Bill Jarrell

Brennan Industries Bill Jarrell has been promoted to vice president of marketing and procurement. He is responsible for global product procurement, new product development and launches, marketing, media relations, advertising, and the company’s Web site. Jarrell has over 25 years of experience in the fluid connectors and the fluid power products industries. He recently worked as vice president of corporate sales and corporate sales manager at Brennan before his new position. www.brennaninc.com

Promotions, Announcements, & Changes With Professionals

Karl Tragl

Bosch Rexroth Corporation Dr. Karl Tragl has been promoted from executive vice president of sales to president and chairman of the Board. He will take over responsibility for the company’s Industrial Applications unit. He also will implement the realignment of the company. Mr. Tragl has been a member of the Board of Management since 2008. www.boschrexroth-us.com

Ted Moyer

Brennan Industries Ted Moyer has been named vice president of national and international sales. He is responsible for directing and coordinating company sales functions, directly managing major client accounts, and establishing and implementing short- and longrange department goals, objectives, policies, and operating procedures. Moyer most recently worked as national sales manager and regional sales manager at Legris, Inc. www.brennaninc.com

Deb Kling

Lenze Americas Deb Kling has been appointed as manager of distribution programs in addition to her responsibilities as marketing manager. Kling joined the company in 2005. Her motion control career includes positions as distributor sales engineer, as well as product and marketing management roles. Her primary focus will be developing and implementing growth programs with distribution organizations. www.lenze-actech.com

Ed Smiley

Kaeser Compressors, Inc. Ed Smiley has been named director of sales. Based out of the company’s U.S. headquarters in Virginia, he will lead the sales teams for all product divisions. Mr. Smiley has over 17 years of industrial sales and product management experience, and he most recently worked at a European-based pump company where he worked in various sales and marketing management roles. www.kaeser.com

John Kharsa

Fluid Components International LLC John Kharsa has been appointed engineering manager for the Aerospace Division. He is responsible for overseeing instrument design and development. Kharsa has over 25 years of experience in engineering and program management, and he most recently worked as senior program manager for Hamilton Sunstrand. www.fluidcomponents.com

Jeff Worobel

Brennan Industries Jeff Worobel has been named director of finance. He is responsible for managing the financial and tax reporting requirements at the company, as well as maintaining and ensuring appropriate and effective accounting procedures are followed. Mr. Worobel has over 25 years of experience in accounting. He most recently worked as controller at NeTeam Systems, LLC. www.brennaninc.com

• To submit promotions, announcements, & changes with professionals, e-mail us at people@fluidpowerjournal.com • 32 | Tech Directory 2010

www.ifps.org | www.fluidpowerjournal.com

Ernie Parker, AI, AJPP, AJPPCC, S, MT, MM, MIH, MIP, MMH Fluid Power Instructor, Hennepin Technical College, EParker@Hennepintech.edu

This Issue

Problem:

2" x 24" x 1" 3/8" hoses and ports on all components

Regulator is set at 50 PSI

AirTeaser

Supply pressure is 100 PSIG

Previous Problem: (from Manufacturers Directory issue) Calculate the saving for one year by using Circuit “B” over Circuit “A.” • Cost of air is based on $.30/1000 scfm. • Clamping force is 220 pounds. • System operates 12 times/minute. • Extending pressure is calculated using a required force of 220 lbs for Circuit “B.” • Circuit “A” uses ¼" diameter ID hoses that are 10-feet long between the directional control valve and the cylinder. • Circuit “B” has ¼" hose x 10 feet long from the power supply to the regulators. • The DC valve is mounted directly on the cylinder, and consider no length of hose from valve to cylinder. • 20 psi is required for retracting.

Given: Extending pressure is < 10 PSIG. Operating requirements need a minimum of 150 pounds of clamping force and a maximum of 180 pounds of force. The inertia of the cylinder has been taken into consideration with the needed force. The part is crushed each time the cylinder clamps. Turning down the regulators to 40 PSI doesn't change anything. What is the problem? The teaser is posted on the IFPS Web site (www.ifps.org) and also printed in the Fluid Power Journal. Submit your information via the Web site, or fax it to 856-424-9248 attn: Donna Pollander. Anyone who submits the correct answer before the deadline date will have his/her name printed in the Society Page newsletter and in Fluid Power Journal. The winner will also be entered into a drawing for a special gift.

Solution: Circuit “A” Given Pressure 100 psi, Cylinder 2² x 10² x 1² Compression Ratio = (100 + 14.7) / 14.7 = 7.8 C.R. Volume to extend = 3.14 in² x 10 = 31.4 in.³ Volume of hose to extend = 0.049 in² x 120² = 5.88 in³ Total volume to extend = 31.4 + 5.88 = 37.3 in³ 37.3 x 12 cycles / min. = 447.55 cipm for extension Volume to retract = 2.35 in² x 10 = 23.56 in³ Volume of hose to retract = 0.049 in² x 120² = 5.88 in³ Total volume to retract = 23.56 + 5.88 = 29.44 in³ 29.44 x 12 cycles / min = 353.3 cipm for retraction Total CIM = 447.55 + 353.3 = 800.85 cipm 800.85 x 60 times per minute x 24 hours per day x 365.25 days per year = 421,217,294.3 in³ per year ÷ 1728 = 243,760 ft³ per year x 7.8 C. R. = 1,901,328 SCF / year. Cost is $.30 / 1000 SCF 1,901,328 / 1000 x 0.30 = $570.40 / year for circuit “A” Circuit “B” Required PSI to extend = 220# / 3.14 in² = 70 PSI C. R. = (70 + 14.7) / 14.7 = 5.76 C. R. Volume to extend = 3.14 in² x 10 = 31.4 in³ x 12 cycles / min. = 376.99 cim x 60 x 24 x 365.25 = 198,282,248.7 in³ / year ÷ 1728 = 114,746.67 ft³ / year x 5.76 C. R. = 661,379.32 SCF/ year ÷ 1000 x $.30 = $198.41 cost of extension Required PSI to retract = 20 PSI (given) C. R. = (20 + 14.7) / 14.7 = 2.36 C. R.

Comments: Mounting the directional control valves as close to the cylinder as possible and using a regulator will many times greatly reduce air consumption. Once the cylinder is fully extended or retracted, the air regulator will stop putting additional air in the cylinder. Remember that any air that stays between the valve and the cylinder is lost energy. You can also use a larger airline up to the valve for better cycle times without the loss of energy. www.ifps.org | www.fluidpowerjournal.com

Volume to retract = 2.356 in² x 10 = 23.56 in³ x 12 = 282.74 cim x 60 x 24 x 365.25 = 148,711,570.6 in³ / year ÷ 1728 = 86,059.94 ft³ / year x 2.36 C. R. =203,148.29 SCF / year ÷ 1000 x $.30 = $60.94 cost of retraction $198.41 + $60.94 = $259.35 cost of operation Circuit “A” – Circuit “B” = $570.40 - $259.35 = $311.05 over a period of one year. Tech Directory 2010 | 33

ProductReview

A Look At New & Innovative Products

Differential Pressure Gauge

Electronic Valves

Mid-West Instrument The Series 6000 family of low-range differential pressure gauges is available from 0-0.25" H2O to 0-20 psid. Bi-directional models are available in 0.25-0-0.25" H2O to 15-0-15" H2O. SWP is (-20"Hg) to 15 psig with a 35-psig rating for 0-10, 0-15, and 0-20 psid ranges. Temperature limits are -20°F to 140°F (-7°C to 80°C). Accuracy ranges from ±2-4% depending on the DP range. Primary applications are monitoring fan and blower pressure, filter pressure drop, furnace draft, flow measuring in conjunction with orifice plates or averaging pilot tubes, and clean room DP. www.midwestinstrument.com

Clippard Instrument Laboratory, Inc. The EW Series electronic valves, available in 2-way or 3-way, normally closed, or fully ported configuration, feature wire leads out of the top of the valve. The units utilize the same operating functions as the company’s EV/ET line of electronic valves. The new line offers flexibility in design with its offering of either in-line or manifold mount options and several DC voltages. The units have a fast response time of 5 to 10 milliseconds and a power consumption of 0.67 watts. www.clippard.com

Rotary Actuator SCHUNK With a new dampening system, the SRUplus rotary actuator can rotate heavy loads, just like its predecessor, the SRU. The new unit is available in six different sizes, allowing the user to chose between two dampening versions. The soft dampening version ensures shorter cycle times even with the same payloads; the hard dampening version enables the handling of a heavier payload with the same body size. Options include electric and fluid feed through, continuous adjustment of the end positions, as well as pneumatic or locked middle position versions. www.schunk.com

Two-Way Ball Valve

Hydraulic Pressure Gauge

Dwyer Instruments, Inc. The Series MSV compact two-way ball valve comes in a two-body stainless steel or brass design with the choice of either fractional tube fitting or female NPT connections. The unit provides ¼-turn directional control of fluids, and the blowout proof ball and stem provide safety in the event of over pressure. The micro-finished ball and PTFE seats provide a quality seal. The valve can handle pressures up to 1500 psi over a temperature range of -40° to 350°F. www.dwyer-inst.com

WIKA The 213.53 bourdon tube pressure gauges are intended for conditions where pulsating or vibration exists with liquid filling. They are suitable for gaseous or liquid media that will not obstruct the pressure system and are ideal for hydraulics and compressors. With their stainless steel construction, the units can withstand adverse conditions and resist wear. www.wika.com

Shell Molding Precision Castings Perucchini The “full” shell molding process consists of casting liquid metal inside shells with internal cores, both formed with sands treated and coated with thermosetting resins. The process achieves tight dimensional tolerances (ISO 8062-CT6), fine controlled thickness, and rough surface quality (Ra 6,3), reducing the need for machining operations. Advanced pouring software allows for simulation of casting filling and solidification, a reduction of industrialization time, lower costs, and higher quality. www.perucchini.com

34 | Tech Directory 2010

www.ifps.org | www.fluidpowerjournal.com

CCEFP | The Center For Compact And Efficient Fluid Power

ESA | Equipment Service Association

U.S.-Based Fluid Power Research Gains International Recognition Impact of the work done by the Engineering Research Center for Compact and Efficient Fluid Power (CCEFP) was most recently evident at the 6th Fluid Power Net International (FPNI) PhD Symposium held at Purdue University in June. FPNI is a worldwide community for networking in fluid power and fluid techniques, and its PhD symposium provides a forum for engineering graduate students to present their fluid power research on a world stage. Attendees at this year’s symposium included 50 faculty, 160 graduate students (45% of them from the U.S.), 25 undergraduates, and 55 industry participants from 14 countries: Austria, Canada, China, Czech Republic, Finland, France, Germany, Italy, Japan, Poland, Serbia, Sweden, United Kingdom and the United States. Eight of the 72 papers presented at the symposium received special recognition for their merit. Five of the eight presentations receiving these awards were presented by CCEFP graduate students based on their work on CCEFP-funded or associated projects: • Aaron Enes, Georgia Tech: “Toward Shared Control of Hydraulic Excavators” • Richard Klop, Purdue University: “Validation of a Coupled Pump-Motor-Line Model to Predict Noise Sources of Hydraulic Transmissions” • Jonathan Meyer, University of Minnesota: “Energy Management Strategy for a Hydraulic Hybrid Vehicle Using Stochastic Dynamic Programming” • Christopher Williamson, Purdue University: “Stability and Motion Control of Inertial Loads with Displacement Controlled Hydraulic Actuators” • Joshua Zimmerman, Purdue University: “Reduction of Engine and Cooling Power by Displacement Control” CCEFP students and faculty will play key roles in IFPE 2011, scheduled for March 22-26, 2011 in Las Vegas, Nev. Papers based on CCEFP research and presented by Center students and faculty, will be featured as a part of the 52nd National Conference on Fluid Power, March 23-25. The Center will also hold its 5th Annual Meeting in conjunction with IFPE. Industry supporters are encouraged to participate in the meeting, which is scheduled for March 22 in an area immediately adjacent to the IFPE show floor. Following the Annual Meeting, students will present posters describing CCEFP research. More information can be found at www.ifpe.com or www.ccefp.org.

CCEFP Receives Renewal and Major Funding The National Science Foundation (NSF) has announced that it will award the Engineering Research Center for Compact and Efficient Fluid Power (CCEFP) a four-year, $16-million dollar grant. Industry partners will augment NSF funding with cash and in-kind contributions, and the Center’s seven universities will contribute an additional $3.2 million. The Center’s education and outreach program is equally ambitious, with over 20 projects designed to • attract the nation’s pre-college students to science and engineering generally and to hydraulics and pneumatics in particular • educate all mechanical engineering undergraduate students about fluid power and raise the general public’s awareness of the ubiquity of fluid power • increase the diversity of students and practitioners in fluid power research and industry • establish lasting forums where industry and academia can exchange ideas and strategize

New Grant Highlights the Growing Reach and Impact of the CCEFP The National Science Foundation (NSF) awarded a grant to the CCEFP to develop a “Novel Compressed Air Approach for Off-Shore Wind Energy Storage.” The grant is a continuation of the open accumulator research initially sponsored by CCEFP. The four-year, $2-million award is made through the Emerging Frontier in Research and Innovation (EFRI) and the Grant Opportunities for Academic Liaison with Industry (GOALI) programs. The investigators of the research are Perry Li (Principal Investigator) and Terry Simon (Co-Principal Investigator) at the University of Minnesota, Eric Loth at the University of Virginia, James Van de Ven at the Worcester Polytechnic Institute, and industry partner Lightsail Energy. The research proposes to develop a localized method for storing off-shore wind energy before conversion to electricity in high-pressure compressed air vessels. In addition to allowing the storage of wind energy during periods of low demand, the concept will achieve load leveling so that components can be downsized for average instead of peak power. The concept makes use of the comparative advantages of hydraulics and pneumatics in a so-called “Open Accumulator” architecture and an isothermal air compressor/expander design. The interdisciplinary research involves fluid flow, heat transfer, machine design, and systems and control.

www.ifps.org | www.fluidpowerjournal.com

ESA 2010 Fall Technical Conference October 10-12, 2010, Embassy Suites Bloomington, Minneapolis, Minnesota Registration information and schedule can be found by visiting www.2esa.org ESA is your resource for technical training! Plan now to attend, and/or send your service techs, to the 2010 Fall Technical Conference in Minneapolis, Minnesota, October 10-12, 2010. At the Technical Conference, you’ll get highly specialized technical training from leaders in the industry, plus a first-hand experience of four very special plant tours, seminars, and the opportunity to become IFPS Industrial Hydraulic Mechanic Certified.

Shop & Plant Tours: Aggressive Hydraulics, Inc. / Blaine, MN Sauer-Danfoss Company / Plymouth, MN SunSource / Savage, MN OTC / Owatonna, MN

Seminars: “How to Spec a Custom Cylinder” “Piston Pump Disassembly, Inspection, Assembly and Testing” “Operation and Service of Telescopic Tipping Cylinders” “Piston Pump Evaluation and Troubleshooting”

Hotel Information: Embassy Suites Bloomington Hotel: Bloomington, Minnesota Reservations: 1-800-EMBASSY (mention ESA to receive discount.) ESA Discount Group rate - $109.00/ night + tax (if reservations are made before September 24, 2010)

Tech Directory 2010 | 35

AssociationNews

FPDA | Motion & Control Network

Review Your Compensation Plan

firms including health care plans, retirement income programs, end-of-year bonus arrangements, and paid vacations and holiday policies.

with the 2010 FPDA Industry Compensation Study

Available to Members for $300 for both volumes; $425 to non-members. Order at www.fpda.org.

Hiring and keeping good employees is essential to the profitability of your business, especially in today’s economy. To achieve that goal, you must consider your overall employee compensation plan—not just your pay scales but also your benefits program as well—in comparison to other firms in distribution. How does your firm’s employee compensation package stack up in the industry? To help you evaluate your situation, FPDA has released the 2010 Cross Industry Compensation Survey available in two volumes: Volume 1 will provide compensation information on FPDA members as a group and Volume 2 provides cross-industry data from more than 30 distribution-based associations. Data is provided in geographic and sales size breakdowns. Additionally, detailed information on Compensation and Fringe Benefits is provided. Compensation data is broken out into base salary, bonus, and total compensation for executives, operating employees, sales employees, and branch managers. Fringe Benefits provides a review of benefit programs being provided by various size

Help Build Your Profit Base In A Down Environment with the FPDA 2010 Profit Report By almost any measure that can be used, 2009 was a tough year. However, even in the midst of a difficult economy, profit opportunities continued to exist. Just as in good times, some firms didn’t merely survive; they prospered. Understanding just how firms adapted to changing circumstances to keep generating adequate profits provides a basis for both immediate action and for future planning. The recently completed 2010 FPDA financial benchmarking study provides detailed financial and operating benchmarks for the industry. As always, the primary benefit of the report is that it highlights the distinction between the performance of the typical firm and the high-profit firm. The differences are important in normal times; they are critical in tough times.

This industry profitability analysis includes comparisons between typical firms and high performers, management suggestions, and detailed results on ROI, P&L, balance sheet, financial ratios, productivity ratios, etc. Data is detailed based on product-type emphasis (both hydraulic and pneumatic), region, and sales volume. A special Trend Analysis section reviews how performance has changed over time in each of the key performance areas. Available for $100 to members; $200 for nonmembers. Order at www.fpda.org.

Don't Miss Your Chance To Register! FPDA/ISD INDUSTRY SUMMIT! October 5-8, 2010 PGA NATIONAL RESORT & SPA, Palm Beach Gardens, Florida Developed for fluid power, motion control, and automation and sealing technology professionals, attendees will discover the keys to success at the FPDA/ISD Joint Industry Summit, October 5-8, 2010 at the PGA National Resort in Palm Beach Gardens, Fla. For details, visit www.fpda.org or call 410-940-6347.

CalendarofEvents NOVEMBER 1-5 Electronic Certification Cincinnati, OH CFC-Solar, Inc. Contact IFPS at 800-308-6005 8-12 5-day Electrical Maintenance Schematics and Troubleshooting Cincinnati, OH CFC-Solar, Inc. Tel: 513-874-3225 www.cfc-solar.com 8-12 Troubleshooting Maumee, OH Eaton Hydraulics Group Tel: 800-413-8809 http://web.fluidpower.eaton. com 8-12 Industrial Basics Eden Prairie, MN Eaton Hydraulics Group Tel: 800-413-8809 http://web.fluidpower.eaton. com 36 | Tech Directory 2010

9-11 Pneumatic Circuitry Troy, MI Parker Hannifin Tel: 216-896-2577 www.parker.com/training 9-12 Mobile Hydraulic Technology Elyria, OH Parker Hannifin Tel: 216-896-2577 www.parker.com/training 15-19 3- or 5-day Level 2 Pneumatics Cincinnati, OH CFC-Solar, Inc. Tel: 513-874-3225 www.cfc-solar.com 15-19 Hydraulic Systems Engineering Elyria, OH Parker Hannifin Tel: 216-896-2577 www.parker.com/training

15-19 EH Maintenance and Troubleshooting Maumee, OH Eaton Hydraulics Group Tel: 800-413-8809 http://web.fluidpower.eaton. com

DECEMBER

15-19 PLC Elyria, OH Parker Hannifin Tel: 216-896-2577 www.parker.com/training

6-9 Introduction to Hydraulic Systems Modeling and Simulation Milwaukee, WI MSOE Tel: 414-277-7269 www.msoe.edu

29-Dec 3 3- or 5-day Level 2 Industrial Hydraulics Cincinnati, OH CFC-Solar, Inc. Tel: 513-874-3225 www.cfc-solar.com 30-Dec 2 Pneumatic Component Selection Atlanta, GA Parker Hannifin Tel: 216-896-2577 www.parker.com/training

6-7 Introduction to Pneumatics Cincinnati, OH CFC-Solar, Inc. Tel: 513-874-3225 www.cfc-solar.com

6-10 Electromechanical Fundamentals Rohnert Park, CA Parker Hannifin Tel: 216-896-2577 www.parker.com/training 6-10 Wind Turbine Fundamental Hydraulics Maumee, OH Eaton Hydraulics Group Tel: 800-413-8809 http://web.fluidpower.eaton. com

7-9 IFPS Hydraulic Specialist Certification Review Eden Prairie, MN Eaton Hydraulics Group Tel: 800-413-8809 http://web.fluidpower.eaton. com 7-10 Hydraulic Maintenance Technology Buena Park, CA Parker Hannifin Tel: 216-896-2577 www.parker.com/training 13-17 3- or 5-day Basic Pneumatics Cincinnati, OH CFC-Solar, Inc. Tel: 513-874-3225 www.cfc-solar.com 13-17 Mobile Hydraulics 400 Eden Prairie, MN Eaton Hydraulics Group Tel: 800-413-8809 http://web.fluidpower.eaton. com

www.ifps.org | www.fluidpowerjournal.com

AssociationNews

IFPS | International Fluid Power Society

Attention Fluid Power Distributors, Manufacturers, and End-Users! Interested in improved safety, improved reliability, greater efficiency, and reduced liability? Certify your workforce with IFPS certifications! If you have ten or more fluid power or motion control mechanics, technicians, or specialists ready to become certified or who need to recertify, get on board with the IFPS Corporate Package Program. Corporate Package includes • Substantial discount on individual memberships and certification tests • Substantial discount on all books and publications • Discounted advertisements in the Fluid Power Journal Depending on the level of the corporate commitment, companies are entitled to between 10 and 40 individual memberships, and between 10 and 40 certifications tests, which include Specialist tests or any Mechanic / Technician written and a Job Performance test. For additional information, visit www.ifps.org / Membership or contact The International Fluid Power Society at 800-308-6005.

Certification Levels Available: CFPAI Certified Fluid Power Accredited Instructor CFPAJPP Certified Fluid Power Authorized Job Performance Proctor CFPAJPPCC Certified Fluid Power Authorized Job Performance Proctor Connector & Conductor CFPMM Certified Fluid Power Master Mechanic CFPIHM Certified Fluid Power Industrial Hydraulic Mechanic CFPMHM Certified Fluid Power Mobile Hydraulic Mechanic CFPPM Certified Fluid Power Pneumatic Mechanic CFPMT Certifed Fluid Power Master Technician CFPIHT Certified Fluid Power Industrial Hydraulic Technician CFPMHT Certified Fluid Power Mobile Hydraulic Technician CFPPT Certified Fluid Power Pneumatic Technician

IFPS Newly Certified Jared Amundson, PS TRD Manufacturing, Inc. Kenneth Kratz, MHT Henry Maxwell, MHM Nova Scotia Power, Inc. Zhigang Niu, E Toran Power Equipment

Jerry Smith, MIP, MT, PT Gordon Steinmetz, HS Tennant Company Roy Turpin, HS Xiaodong (Alan) Zhao, S, PS Indalco Alloys, Inc.

Jim Robinson, S, PS Hyspeco, Inc.

IFPS Calendar Pneumatic and/or Hydraulic Specialists Review Training Week of October 25, 2010, St. Louis, MO Job Performance Test - Technicians and Mechanics 10/29/10 - Altec Industries Forest Park, GA

CFPHS Certified Fluid Power Hydraulic Specialist CFPPS Certified Fluid Power Pneumatic Specialist CFPE Certified Fluid Power Engineer CFPCC Certified Fluid Power Connector & Conductor

IFPS 2011 Spring Meeting February 23–26, 2011 Orlando, FL

CFPMIH Certified Fluid Power Master of Industrial Hydraulics

IFPE March 22–26, 2011 Las Vegas, NV

CFPMMH Certified Fluid Power Master of Mobile Hydraulics

IFPS 2011 Annual Meeting September 14-17, 2011 Chicago, IL www.ifps.org | www.fluidpowerjournal.com

CFPS Certified Fluid Power Specialist (Must Obtain CFPHS, CFPPS)

CFPMIP Certified Fluid Power Master of Industrial Pneumatics

Tech Directory 2010 | 37

AssociationNews

IFPS | International Fluid Power Society

IFPS Certification Testing Locations

ndividuals wishing to take any IFPS written certification tests are able to select from approximately 265 convenient locations across the United States and Canada. The IFPS is able to offer these locations through its affiliation with The Consortium of College Testing Centers (CCTC) provided by National College Testing Association (NCTA).

To register for an IFPS written certification test: 1. Fill out an IFPS Certification Test Application including your desired location by visiting www.ifps.org. 2. Submit your application with payment to IFPS Headquarters. 3. Upon receipt of your application, you will be e-mailed instructions. Testing dates for any locations listed below are as follows: October 2010 November 2010 Tuesday, 10/5 Tuesday, 11/2 Thursday, 10/21 Thursday, 11/18

December 2010 Tuesday, 12/7 Thursday, 12/16

January 2011 Tuesday, 1/4 Thursday, 1/20

February 2011 Tuesday, 2/1 Thursday, 2/17

March 2011 Tuesday, 3/1 Thursday, 3/17

April 2011 Tuesday, 4/5 Thursday, 4/21

May 2011 Tuesday, 5/3 Thursday, 5/19

June 2011 Tuesday, 6/7 Thursday, 6/16

If you have any questions, please call IFPS Headquarters at 800-308-6005 or e-mail Connie Graham at cgraham@ifps.org.

ALASKA University of Alaska Anchorage Anchorage, AK ALABAMA Alabama A&M University Normal, AL Jacksonville State University Jacksonville, AL University of AL in Huntsville Huntsville, AL University of Alabama at Birmingham Birmingham, AL ARKANSAS Northwest Arkansas Community College | Bentonville, AR ARIZONA Arizona State University Tempe, AZ Arizona Western College Yuma, AZ Coconino Community College Flagstaff, AZ Eastern Arizona College Thatcher, AZ

Fullerton Community College Fullerton, CA

University of Delaware Newark, DE

University of Georgia Athens, GA

Richland Community College Decatur, IL

Irvine Valley College Irvine, CA

FLORIDA Brevard Community College Cocoa, FL

University of West Georgia Carrollton, GA

Rock Valley College Rockford, IL

Valdosta State University Valdosta, GA

University of Illinois at Urbana Champaign, IL

HAWAII BYU-Hawaii Laie, HI

Waubonsee Community College Grove, IL

La Sierra University Riverside, CA National Test Center San Diego, CA National University San Diego, CA Santa Rosa Junior College Santa Rosa, CA Skyline College San Bruno, CA The Taft University System Santa Ana, CA UC San Diego Extension San Diego, CA University of California Irvine, CA Yuba Community College Marysville, CA

Daytona State College Daytona Beach, FL Florida Atlantic University Boca Raton, FL Florida Gulf Coast University Ft. Myers, FL Florida Memorial University Miami Gardens, FL Hillsborough Community College Plant City, FL Miami Dade College Miami, FL Open Campus Florida Community College at Jacksonville, FL Palm Beach Community College North Campus | Palm Beach Gardens, FL Santa Fe Community College Gainesville, FL

Glendale Community College Glendale, AZ

COLORADO Community College of Aurora Aurora, CO

Mesa Community College Mesa, AZ

Community College of Denver Denver, CO

University of South Florida Tampa, FL

Northern Arizona University Flagstaff, AZ

Fort Lewis College Durango, CO

Valencia Community College Orlando, FL

Paradise Valley Community College Phoenix, AZ

Front Range Community College Larimer Campus | Ft. Collins, CO

Pima Community College Tucson, AZ

Pikes Peak Community College Colorado Springs, CO

GEORGIA Albany State University Albany, GA

Rio Salado College Tempe, AZ

Pueblo Community College Pueblo, CO

CALIFORNIA Allan Hancock College Santa Maria, CA

University of Colorado at Boulder Boulder, CO

California Polytechnic State University San Luis Obispo, CA California State University, Fresno Fresno, CA

University of Northern Colorado Greeley, CO CONNECTICUT Yale University | New Haven, CT

Chapman University Orange, CA

DELAWARE Delaware State University Dover, DE

Foothill College Los Altos Hills, CA

Delaware Technical and Community College | Georgetown, DE

38 | Tech Directory 2010

University of Florida Gainesville, FL

Clayton State University Morrow, GA Columbus State University Columbus, GA Columbus Technical College Columbus, GA Darton College Albany, GA Georgia Gwinnett College Lawrenceville, GA Georgia Southern University Statesboro, GA Georgia State University Atlanta, GA

IOWA Hawkeye Community College Waterloo, IA University of Iowa Iowa City, IA

INDIANA Indiana Univ. Purdue University Indianapolis, IN Ivy Tech Community College/ Bloomington | Bloomington, IN Ivy Tech Community College/ Columbus | Columbus, IN

Wartburg College Waverly, IA Western Iowa Community College Sioux City, IA IDAHO Boise State University Boise, ID

Ivy Tech Community College/ Evansville | Evansville, IN Ivy Tech Community College/Gary Gary, IN Ivy Tech Community College/ Indianapolis | Indianapolis, IN

Brigham Young University Rexburg, ID

Ivy Tech Community College/Kokomo Kokomo, IN

College of Southern Idaho Twin Falls, ID Eastern Idaho Technical College Idaho Falls, ID Lewis-Clark State College Lewiston, ID

Ivy Tech Community College/ Lafayette | Lafayette, IN Ivy Tech Community College/ Lawrenceburg | Lawrenceburg, IN Ivy Tech Community College/Madison Madison, IN

University of Idaho Moscow, ID

Ivy Tech Community College/Muncie Muncie, IN

ILLINOIS College of DuPage Glen Ellyn, IL

Ivy Tech Community College/ Richmond | Richmond, IN

College of Lake County Grayslake, IL

Ivy Tech Community College/ Sellersburg | Sellersburg, IN

Illinois State University Normal, IL

Ivy Tech Community College/South Bend | South Bend, IN

John A. Logan Community College Carterville, IL

Ivy Tech Community College Terre Haute, IN

Lincoln Land Community College Springfield, IL

Purdue University West Lafayette, IN

Northern Illinois University De Kalb, IL

KANSAS Johnson County Community College Overland Park, KS

Parkland College Champaign, IL

Kansas State University Manhattan, KS

www.ifps.org | www.fluidpowerjournal.com

University of Kansas Lawrence, KS Wichita State University Wichita, KS KENTUCKY University of Louisville Louisville, KY Western Kentucky University Bowling Green, KY LOUISIANA Bossier Parish Community College Bossier City, LA

MINNESOTA Minnesota State University, Mankato Mankato, MN

Raritan Valley Community College Somerville, NJ

HACC Gettysburg Campus Gettysburg, PA

Texas A&M University-Commerce Commerce, TX

University of Minnesota - Twin Cities Minneapolis, MN

NEW MEXICO Eastern New Mexico University Portales, NM

Harrisburg Area Community College Harrisburg, PA

Texas Tech University Lubbock, TX

University of Minnesota Morris, MN

San Juan College Farmington, NM

MISSOURI Avila University Kansas City, MO

NEVADA College of Southern Nevada Charleston Campus Las Vegas, NV

Metropolitan Community College-Penn Valley | Kansas City, MO

College of Southern Nevada Cheyenne Campus North Las Vegas, NV

University of Louisiana at Monroe Monroe, LA

Missouri Western State University St.Joseph, MO

Nicholls State University, Thibodaux, LA

Southeast Missouri State University Cape Girardeau, MO

College of Southern Nevada Green Valley Campus Henderson, NV

University of New Orleans New Orleans, LA

St. Charles Community College Cottleville, MO

College of Southern Nevada Henderson Campus, NV

MARYLAND Anne Arundel Community College Arnold, MD

State Fair Community College Sedalia, MO

NEW YORK Brooklyn College - CUNY Brooklyn, NY

Carroll Community College Westminster, MD Chesapeake College Wye Mills, MD College of Southern Maryland La Plata, MD

Three Rivers Community College Poplar Bluff, MO University of Central Missouri Warrensburg, MO Webster University St. Louis, MO

Frederick Community College Frederick, MD

MISSISSIPPI Holmes Community College Goodman Campus | Goodman, MS

Harford Community College Bel Air, MD

Mississippi State University Mississippi State, MS

Hagerstown Community College Hagerstown, MD

University of Mississippi University, MS

Howard Community College Columbia, MD

MONTANA Montana State University Bozeman, MT

University of Maryland College Park, MD

Rochester Institute of Technology Rochester, NY OHIO Central Ohio Tech College/OSUNewark | Newark, OH

Rhodes State College Lima, OH

Utah Valley State College Orem, UT Weber State University Ogden, UT VIRGINIA Old Dominion University Norfolk, VA

Austin Community College Austin, TX

Marian University of Fond du Lac Fond du Lac, WI

Collin Community College - Spring Creek Campus | Plano, TX

University of Wisconsin Oshkosh Oshkosh, WI

Eastfield College Mesquite, TX

University of Wisconsin-Milwaukee Milwaukee, WI

El Paso Community College El Paso, TX

UW-Green Bay Green Bay, WI

Clackamas Community College Oregon City, OR

Grayson County College Denison, TX

WYOMING University of Wyoming Laramie, WY

Mt. Hood Community College Gresham, OR

Lamar Institute of Technology Beaumont, TX

Portland Community College Rock Creek Portland, OR

Lamar University Beaumont, TX

Portland State University Portland, OR

Midwestern State University Wichita Falls, TX

RCC-SOU Higher Education Center Medford, OR

Sam Houston State University Huntsville, TX

Southwestern Oregon Community College | Coos Bay, OR

Southern Methodist University Dallas, TX

University of Oregon Eugene, OR

Texas A&M International University Laredo, TX

Henry Ford Community College Dearborn, MI

North Dakota State University Fargo, NC

Kalamazoo Valley Community College Kalamazoo, MI

The University of North Carolina Wilmington, NC

OREGON Central Oregon Community College Bend, OR

Lake Superior State University Sault Ste. Marie, MI

NORTH DAKOTA Bismarck State College Bismarck, ND

www.ifps.org | www.fluidpowerjournal.com

Salt Lake Community College Salt Lake City, UT

WISCONSIN Lakeshore Technical College Cleveland, WI

University of Oklahoma Norman, OK

Mercer County Community College West Windsor, NJ

Davis Applied Technology College Kaysville, UT

TEXAS Abilene Christian University Abilene, TX

North Carolina Central University Durham, NC

Washtenaw Community College Ann Arbor, MI

UTAH Brigham Young University Provo, UT

Western Washington University Bellingham, WA

Ferris State University Big Rapids, MI

Gloucester County College Sewell, NJ

Weatherford College Weatherford, TX

Walters State Community College Morristown, TN

University of Central Oklahoma Edmond, OK

Southwestern Michigan College Dowagiac, MI

Middle Tennessee State University Murfreesboro, TN

Victoria College Victoria, TX

South Seattle Community College Seattle, WA

Mount Olive College Mount Olive, NC

Schoolcraft College Livonia, MI

Trident Technical College Charleston, SC

University of Texas El Paso El Paso, TX

The University of Memphis Memphis, TN

Delta College University Center, MI

NEW JERSEY Brookdale Community College Lincroft, NJ

Technical College of the Lowcountry Beaufort, SC

University of Texas at Arlington Arlington, TX

Olympic College Bremerton, WA

Oklahoma State University-Tulsa Tulsa, OK

Southeast Community College Lincoln, NE

Spartanburg Community College Spartanburg, SC

University of Texas - Brownsville Brownsville, TX

Tennessee State University Nashville, TN

The University of Toledo Toledo, OH

Guilford Technical Community College Jamestown, NC

Michigan State University East Lansing, MI

Piedmont Technical College Greenwood, SC

University of Houston Houston, TX

WASHINGTON Central Washington University Ellensburg, WA

Oklahoma State University Stillwater, OK

Macomb Community College Warren, MI

Orangeburg Calhoun Technical College Orangeburg, SC

Tyler Jr. College Tyler, TX

Southern Adventist University Collegedale, TN

The Ohio State University Columbus, OH

Fayetteville State University Fayetteville, NC

NEBRASKA Bellevue University Bellevue, NE

Midlands Technical College Columbia, SC

TENNESSEE East Tennessee State University Johnson City, TN

OKLAHOMA Northern Oklahoma College Tonkawa, OK

Lansing Community College Lansing, MI

Horry-Georgetown Technical College Conway, SC

Franklin University Columbus, OH

NORTH CAROLINA East Carolina University Greenville, NC

MICHIGAN Baker College Online Flint, MI

SOUTH CAROLINA Coastal Carolina University Conway, SC

York Technical College Rock Hill, SC

University of Akron Akron, OH

University of Massachusetts Boston, MA

Harrisburg Area Community CollegeLancaster Campus | Lancaster, PA

Columbus State Community College Columbus, OH

The University of Montana Missoula, MT

MASSACHUSETTS North Shore Community College Danvers, MA

Harrisburg Area Community College York Campus | York, PA

PENNSYLVANIA Bucks County Community College Newtown, PA

CANADA Lethbridge College Lethbridge, AB Canada Saskatchewan Institute of Applied Science and Technology Saskatchewan, Canada Thompson Rivers University Kamloops, BC Canada

Texas A&M University College Station, TX

Tech Directory 2010 | 39

Classifieds

Tech Directory 2010

Advertiser Index

CIL-MM7 FPJ

3/5/08

11:51 AM

Page

INSERTA®

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