Fluid Power Journal July/August 2010

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contents July/August 2010

•

Volume 17

•

Issue 6

Features

10 12 14 20 24 Sophisticated Fluid Analysis Program

Helps Users Extend Life Of Their Hydraulic Systems

By Wasan Shaffou, Eaton Vickers® Fluid Analysis Service

Special Considerations for the Selection and Use of Pneumatic and Hydraulic

Actuators for Marine Applications

How to Avoid a Lawsuit

Understanding the

By Brendan Casey

Part One

Fluid Power a Critical Factor in Offshore Engineering

Hydraulic Vane Pump:

By P.K. Guha, Attica Hydraulic Exchange Corp.

By Rance Herren, CFPS, National Oilwell Varco

By Walter F. Stridick and Noel Laukaitis, Lehigh Fluid Power, Inc.

departments

20

Vickers V2010 Pump

Understanding The hydraulic

10

Vane Pump

4 6 7 8 15 23 28 31 39

Notable Words Math Teaser All About Air IFPS Time Capsule Literature Review Figure It Out Product Spotlight Association News Classifieds

32 24

Official Publication of The International Fluid Power Society

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NotableWords

By Raymond Hanley, CFPE, AI, Emeritus

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

Some years ago I was asked the question, “What is the greatest gift you can give a friend?” I did not have a good answer at the time but later learned the gift was “inviting them to your home.” When you think about it, it is indeed a great gift to be invited to a friend’s home.

And so it was indeed a great gift when I was invited to be part of the IFPS Board of Directors, a new experience for me. I was a newbie at the time, but wow, what a learning experience! That invitation became a big factor in my career. It gave me more than just access to greater fluid power knowledge; it was knowledge and understanding that comes from associating with professionals all over the country.

It seems to me that there is a great opportunity today during the current downturn in our economy for the unemployed. The latest statistic is that there are nearly 9.7% (or more) unemployed professionals, and every year many thousands of high school and college graduates will only add to this problem-not a very optimistic outlook.

This year is the International Fluid Power Society’s 50th anniversary. The Society is more important now than ever, not only to its members but also to every employee in every industry, including those looking for work. The everexpanding certification program is a significant aid to career advancement. Every mechanic, technician, sales engineer, and design engineer has a learning opportunity with the various certifications. Individuals qualified in fluid power are all working, and many companies are looking to add qualified people. Mechanics and engineers are highly valued and sought after more so this year than last.

Many people have never had any exposure or realization of the great career enhancement possibility with the world’s third largest power transmission systems: pneumatics and hydraulics. Opportunities in fluid power are in every industry imaginable but, unfortunately, it still remains the “Hidden Giant” to so many potential candidates.

Every active IFPS member and certainly every Board member has an interesting story to tell about their careers in fluid power. The Society is now 50 years old and growing, and it still provides the future for many progressive professionals in every discipline.

50 Celebrating

years

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

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 Fluid Power Journal (ISSN# 1073-7898) is the official publication of the International Fluid 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. POSTMASTER: Please send Address Corrections to Fluid Power Journal, PO Box 2548, Orlando, FL 32802-9830

4 | July/August 2010

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MathTeasers

This Issue

with Professor P.V. Btfsplk

Problem: Relief Valve Please compute the horsepower loss across a relief valve if it is set for 1000 psi and returns all its flow back to the reservoir from a 20-gpm fixed displacement pump.

Solution: Expansion Tank

(From May/June 2010 Issue)

An expansion tank in a heated system is an oil barrel with an internal diameter of 24 inches and a height of 40 inches. When half filled with water, the pressure equals 30 psig. If the water level falls by 8 inches, what will the pressure of air in the barrel be?

Illustration: John Spisak

P1/ P2 = V2/ V1 =

V1 = 0.5 (Î /4) 242(40) = 9047-in3

V2 = 9047-in3 + (Î /4) 242(8) = 12,667-in3

Therefore:

P1 = 30 +14.7 = 44.7-psia

P2 = P1 (V2/V1) = 44.7 (12,667/9047) = 62.6-psia

The final pressure is = 62.6-14.7 = 47.9 psig

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.

Request more information at www.fluidpowerjournal.com

6 | July/August 2010

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AllAboutAir

Smooth Start

load on a machine that glides on a cushion of air (ground affect bearing).

With limited flow to prevent the load from being tipped or dumped, the pressure to raise the load into the “glide” position will never be achieved. This application and some others require full flow with increasing pressure for a smooth transition. One successful way to control pressure at full flow is with a pilot-operated regulator rather than a valve. This is shown in Figure 2. The pilot section of the regulator is gradually pressurized through an orifice to increase the outlet pressure. The back pressure or lack of it has little effect.

Another possibility to achieve the desired pressure profile would use a current or voltage to pressure, electrically driven regulator to pilot a regulator with more flow. Using an air-piloted regulator with high relief flow offers rapid exhaust of system pressure if that is desired. In addition to controlling conventional or common pneumatic cylinders, air motors etc., pressure control can be effective with robotic automation. Grippers may be controlled to effectively

Actuator

Control

S

ome mechanical motion is intended to accelerate objects rapidly when potential energy is released to produce force and motion. Examples are an arrow from a bow or a pellet from a pneumatic rifle. On the other hand, many items benefit from gradual acceleration as an automobile starting from a standstill or newly energized pneumatic actuators. What happens between Stop and Go can be crucial.

Double-acting pneumatic actuators may be prevented from “Fly Away” acceleration with meter-out flow controls except for “first time today” start up when there is no residual compressed air on the opposing side of the piston or diaphragm. Single-acting or spring return actuators may be more difficult to control at all times. A fixed orifice may slow the flow and motion at start up but will not allow more flow when the “need for speed” may be desired. Several manufacturers offer two-stage pneumatic valves to control compressed air flow for a gradual build up of pressure and then open wide for robust flow. The basic technique is shown in Figure 1, whether it’s a special product or a doit-yourself circuit. The basic technique of filling the downstream volume more slowly to an intermediate pressure and then allowing full flow is fairly common.

Some common start-up conditions may be caused by vertical pneumatic cylinders extended by the force of gravity while the machine is idle and the pressure is turned off. Also, cylinders that are not mounted vertically may be moved from the normal “home” position for cleanup and maintenance. In production, the need to engage a product gently before pushing it at flank speed may prevent spills and breakage. These conventional requirements are often met with the twostage technique that senses back pressure, position, time delay, or a significant event to trigger the second stage.

Some applications may not benefit from the twostage back pressure technique. Imagine a heavy

FIGURE 1

FIGURE 2 pick and place a brick on the first cycle and then handle an egg or a kitten in succession. Controlling each robotic axis with the aid of programmable logic controllers (PLC), real-time computers, or possibly a joystick allows robotic machines to simulate or replicate the fluid motions of the human body rather than a rusty tin man.

Coupling deceleration techniques with some acceleration control techniques may provide efficient graceful motion with mechanical devices and machinery.

Thomas W. Kreher, CFPPT | Applied Pneumatic Controls, Inc. | OIL SMOKE®

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July/August 2010 | 7

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.

Memories of the IFPS Submitted by James Morgan, CAE, PE, 1991-1995 IFPS Executive Vice President and Secretary It was in Normandy’s hedgerows in June 1944 that I first experienced the power of pressurized fluid. I was in the Army Corps of Engineers advance maintenance party. Our job was to keep construction machinery operating under combat conditions. We were trained on all of the construction equipment. The use of hydraulics was unknown.

Our Caterpillar D-6 was a challenging monster of gears, clutches, chains, winches, and cables.

It was called to the front line to make openings in the hedgerows. Unfortunately, the Cat’s dozer blade tended to ride up and over the hedgerows. The mechanic to whom I was helping tried weights. That did not work, so he wanted to try something else.

We removed a pump from a disabled Army tank turret drive. We retrieved a shock absorber cylinder from a damaged artillery piece. With other battlefield junk, we created a single-acting ram to hold the Cat’s dozer blade down. The blade could be raised by the original cable and winch. It now could be held down with the Cat’s full weight. It opened paths for the military to pursue the enemy through the field hedgerows. I like to think that hydraulics won the war.

Enter the FPS: In 1960, I was working in hydraulics and pneumatics—and seized the opportunity to help establish FPS Chapter 2. I became an officer and later chapter president. I made many lifelong friends in our industry. This FPS experience and networking led to my being named technical director and subsequently president of the National Fluid Power Association (NFPA)—a post that I held for 23 years until retirement.

IFPS Reborn: In the early 1990s, several FPS officers and directors, whom I had known for many years through my work for NFPA, were concerned about the Society’s survival. They asked me to come out of retirement and help. Owing my career success to FPS, I accepted the challenge. With a solid headquarters operation and reinvigorated officers and directors, we developed the present certification and education program (thanks for Ray Hanley) and launched the Fluid Power Journal.

IFPS was the centerpiece of my lifelong career in fluid power. I am deeply grateful to Frank Mackin, FPS founding president, and the hundreds of dedicated volunteers and staffers who followed. Their combined efforts helped advance so many careers in fluid power through IFPS’s education, training, and certification program—and networking opportunities.

8 | July/August 2010

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Sophisticated

Fluid Analysis Program Helps Users Extend Life Of Their Hydraulic Systems

By Wasan Shaffou, Eaton's Vickers Fluid Analysis Service

F

our out of five hydraulic component failures are a direct result of dirty fluids and that means they are almost all both predictable and preventable.

Nothing lasts forever, of course, but a rigorous fluid quality maintenance program is one of the best investments a customer can make to ensure maximum practical life and optimum performance from a hydraulic system.

Unfortunately, an in-depth fluid analysis requires specialized equipment and highly skilled personnel, neither of which most hydraulic system users can afford to have in-house.

Vickers established the Fluid Analysis Service in 1991, and Eaton has upgraded and expanded its capabilities since acquiring Vickers in 1999.

Located in Southfield, Mich., the lab supports customers primarily in the United States, Canada, and Mexico, as well as European customers who need its specialized capabilities to identify and resolve difficult fluid contamination problems. The company also maintains a lab facility in Australia to serve customers in that country and its Asian neighbors.

Good Samples = Accurate Results The value of a fluid analysis depends entirely on the quality of the 10 | July/August 2010

sample. That is not a trivial detail; taking a representative sample is a very exact science.

The system should be stable, meaning that it is at operating temperature and the fluid has been circulated sufficiently to produce a representative sample. Obtaining the sample in the return line directly ahead of the return line filter is generally recommended. A well-designed system will have a permanent sampling valve installed there.

Failing that, it’s possible to obtain good samples from the reservoir using a vacuum pump and clean tubing, or from the pressure line immediately downstream of the pump. Both of these locations require a fair amount of skill in taking the sample to avoid including non-representative contaminants, though. That is why the return line location is highly recommended.

Many of the particles we are looking for are sub-micron, and that means the sample jar has to be specially prepared and ultra-clean to avoid introducing contamination.

Many labs use inexpensive plastic sample jars, but they have proved to be less than satisfactory in terms of cleanliness, so only glass is used.

A Comprehensive Battery Of Tests Each sample received is assigned

an individual tracking number and a data sheet that records both sample details and test results. Samples are typically processed in batches of 12 to achieve optimum operating economy from the lab’s test equipment.

Eaton’s customer service standard is to provide 24-hour turnaround on all samples received. Some customers have reported waiting up to three weeks for test results from other labs, which is entirely unacceptable.

You can do a lot of damage to your equipment in three weeks.

The standard bank of tests performed on fluid samples includes • Particle count • Viscosity determination • Water content measurement • Spectrographic analysis • X-ray fluorescence analysis • Photomicrography of the sample • Total acid number determination Viscosity, water content, particle counts, and total acid determinations are reasonably self-explanatory.

Taken together, they give a good overview of fluid condition and overall system health.

The lab uses premium grade analytical equipment including a highquality Canon Viscometer, a Karl Fischer water machine, and a Hach Ultra particle counter. Fieldwork lab personnel use a Vickers Target Pro

2 particle counting system with a high-intensity dual laser light source and photo sensor. Acid content is determined with standard chemical test procedures.

These tests provide a good overview of what’s going on in the system, and they are all a customer gets from many labs. Eaton takes it a couple of steps further to provide information the customer can use to more accurately diagnose and correct the causes of the contamination found.

There are four basic sources of contamination in a hydraulic system:

Contaminated New Oil Although hydraulic fluids are produced under clean conditions, by the time they have been stored, transported, and transferred into a customer’s system, they are nearly always contaminated with metal and rubber particles.

Built-in Contamination This is a problem both with new equipment and equipment that has been repaired in the shop or field.

Any time a system has been opened, or a component replaced, there is a high likelihood of contamination being introduced to the oil.

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Ingressed Contamination A major source of both particulate and water contamination is from the environment. Ingressed contamination typically finds its way into a system through reservoir vents, open access plates, and cylinder seals.

Generated Contamination The most destructive contaminants in most systems are metal particles stripped off the surface of system components by friction. If not found and corrected immediately, these particles quickly create more particles in a cascade effect that dramatically shortens the life of all system components.

The basic tests give the customer a good handle on the first three sources of contamination. Things like water content or plain “dirt” are reasonably easy to track down at the source and eliminate once you know they are present. Factors like viscosity breakdown also have known sources, primarily overheating and oxidation, which are relatively easy to diagnose and remedy.

Beyond The Basics What the more advanced Spectrographic and X-ray florescence tests provide is insight into the

more difficult to diagnose contamination sources and the truly strange ones, as well. For example, knowing the exact chemical make-up of contaminant particles can help the customer determine exactly where in the system they are being generated.

Consider the possibilities in a pump. It may have cast iron end caps, an aluminum body, an alloy steel shaft, gears, bearings, other components of various metals and seals made of a whole range of polymers. It’s not enough just to know the system is generating metal particles. What the customer needs to know is exactly what kind of particles in exactly what proportions.

That information can be used diagnostically to eliminate the source of the problem.

If you know that the system in this example is contaminated with alloy steel, you can be pretty sure it isn’t coming from the end caps or pump body. That level of detail makes tracking down the source a lot easier. And then you always have to be on the lookout for the truly strange things that can get into a hydraulic system…like the egg salad sandwich that was the proximate cause of a pump failure in one case.

Actionable Information All of the information generated is returned to the customer in the form of an in-depth, standardized report.

The report contains both quantitative analyses and graphical representations of the contaminants found to assist the customer in utilizing the information to diagnose and eliminate the sources of contamination found.

In addition to traditional hard copies, a 24/7 Web portal allows customers to access and view their reports online. Both current and pre-

vious reports are available for viewing, giving customers an easy way to monitor and track fluid trends as well as singular anomalies.

The insights provided support both reactive and proactive maintenance strategies. Eaton’s unique position as a fluid analysis laboratory, a hydraulic fluid supplier, and a manufacturer of hydraulic components adds value to the report data by augmenting it with access to “hands-on” technical advice and field support.

The report is as comprehensive as possible. To that end, not only is quantitative data on contaminants like particle size distribution and composition included but also suggested sources for the particular contaminants found. The goal is to provide as much actionable information as possible, as quickly as possible. That’s what the customer needs. We look at ourselves as part of the team that is working to make sure that the 80 percent of hydraulic failures attributable to dirty fluid happen to someone else’s system, not our customer’s.

Wasan Shaffou is Lab Manager at Eaton Vickers® Fluid Analysis Service. For more information, visit www.eaton.com.

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July/August 2010 | 11

By Walter F. Stridick, Sales & Application Specialist, and Noel Laukaitis, Engineering Manager, Lehigh Fluid Power, Inc.

Special Considerations for the Selection and Use of

Pneumatic and Hydraulic Actuators

for Marine Applications

P

neumatic and hydraulic actuators are found in many various offshore and marine applications around the world. You will find shipboard actuators controlling vessel steering mechanisms, hatches, winch brakes, boom cranes, and engine governors. Other marine applications include use on remote-operated underwater vehicles, various uses on drilling platforms, process control valves, and even in tidal/wave action power generation devices.

Standard off-the-shelf steel or aluminum actuators (pneumatic or hydraulic cylinders) are not always the best choice in marine applications. Experience has shown that use of pneumatic or hydraulic actuators in marine applications demand that attention be paid to corrosion prevention and suitability for use in or near saltwater In and around saltwater environments, corrosion is a major concern. As you can very well imagine, it would not be good if a critical actuator failed because the components rusted away. The easiest way to reduce corrosion is the use of corrosion-resistant materials such as stainless steel or plastics. Use of either of these materials has downside potential--stainless steel is expensive and plastics don’t always provide the required material strengths.

Stainless steel is available in various grades, each with differing corrosion resistance and strength properties (Fig. 1). The most common grades of stainless steel used in actuators are: 303, 304, 316, and 17-4PH. 17-4PH is a hardened stainless steel suitable for use as actuator piston rod and tie rod material. While other grades of stainless such as 304 and 316 may have higher cor12 | July/August 2010

rosion resistance ratings, they also have lower yield strengths. This may make 304/316 series stainless ill suited for cylinder parts that require high strength.

Whatever the material you have chosen for the piston rod, chrome plating the rod stock helps increase the seal life expectancy of your cylinder. If stainless steel is not required or deemed to be excessively expensive, composite or carbon steel materials can be used with caution.

Certain fiber-reinforced based epoxy matrix composites will resist corrosion no doubt, but they have pressure and fluid limitations that prevent their use in certain types of cylinders. Another factor that limits the use of some composites are their limited resistance to UV light, which can cause the materials to become brittle or weak.

Carbon steel is the most common material used in actuators and in certain applications, and when combined with stainless steel piston rods and tie rods, steel can be a great, cost-effective alternative material choice, especially when the exterior of the cylinder is coated with marinegrade epoxy paint. When properly applied, this combination provides a durable cylinder that is substantially less expensive than a stainless steel

cylinder. In some instances, epoxy paint can be applied over parts that have been electroless nickel-plated, which increases corrosion resistance even more (Fig. 2).

Corrosion resistance is not the only item to be concerned about when making choices about actuators for offshore and marine use.

Material selection for seals and bearings also needs examination.

The increasing popularity of environmentally safe hydraulic fluids has increased the use of alternative materials for cylinder seals. Industry standard nitrile and urethane seals may not be compatible with certain hydraulic fluids that are used in the marine industry. It is always wise to determine the compatibility of the cylinder seal material with the hydraulic fluid you plan to use.

If your cylinder will be used in a submerged application, it is best to use a rod gland design that resists external pressures and fluids. Doing this will increase the life expectancy of the rod bearings and seals internal

Figure 1

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Figure 3

Figure 2

to the cylinder, which prolongs the cylinder's MTBF rate.

Rod bearings create another potential trouble area for marine actuators. While ductile iron is commonly used in various cylinder rod bearings, corrosion and abrasion are two good reasons to seek alternate bearing material. Bronze rod bearings have been used for many decades in the actuator industry. This material is well suited for use as a rod bearing due to its anti-corrosive

nature and ability to resist wear.

Other materials that are well suited for marine use include composites such as Rulon and Duralon.

In addition to material choices, there are design criteria that need to be considered when employing actuators. Certain applications require extra attention be given to failure modes and fail-safe operation. While not many mechanical devices can be 100% reliable throughout their lives in or near the ocean, thought must

be given to the possibility of pressure loss, hose failure, or other events that would cause damage to the environment or to the safety and welfare of living things.

In these situations, spring cylinders are often employed for safety’s sake.

When engineered and commissioned properly, spring cylinders can provide predictable fail-safe positioning.

Simply stated, spring cylinders are designed to move the piston and piston rod to the fully extended or fully retracted position upon loss of operating pressure.

Process valves such as pinch valves or knife valves often use spring cylinders to ensure that the flow of material is automatically stopped in the event of pressure loss.

Another example of a spring cylinder application in a marine environment is for use with shipboard hatch locks (Fig. 3). If pressure is lost, spring cylinders will automatically close the hatch and engage locking pins ensuring that the hatch will stay locked until pressure is restored or a manual override is employed.

Spring cylinders have also been successfully used to engage braking mechanisms on winches to prevent unintended runaway of the winch

in power loss situations. Pressure is applied to a band brake when the piston rod is fully extended or retracted (depending upon the cylinder and brake design), thus preventing unintentional runaway by the winch spool.

Successful use of spring cylinders is a bit more complicated compared with typical double-acting cylinders. Three critical requirements must be known to ensure the proper design of the spring cylinder: spring preload, spring final load, and minimum operating pressure. Be sure to consult with cylinder personnel that have the experience level required to properly design a cylinder that will meet your specifications.

Whether used in a small-bore pneumatic or large-bore high-pressure hydraulic application, the double-acting, spring extend, or spring retract actuators, when properly designed with the right materials and seals, can provide robust, simple, cost-effective means of movement in many marine applications.

For more information, visit Lehigh Fluid Power, Inc. at www.lehighfluidpower.com.

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July/August 2010 | 13

How to

pounded by the fact that the mechanism for elevating the forks on a forklift typically uses a single-acting, telescopic cylinder with a chain and pulley arrangement.

Among other things, this will result in relative fork movement double that of cylinder movement. Unfortunately, I don’t have room for a detailed discussion of all these issues here.

But the more revealing question and moral to this story for you as a fluid power professional is this: How could this lawsuit (if not the incident) have been avoided in the first place?

What struck me as I reviewed all the facts of this case was the technician who repaired the forklift prior to the incident left the door open to litigation by his failure to do one simple thing.

Had he taken the 5 to 10 minutes necessary to do it, the lawsuit would never have gotten off the ground. It was even spelled out for him, if only he’d looked – or been trained to do so.

I’m talking about following proper procedure, and checking it off.

The aviation and aerial access industries have something significant in common. And that is, if you use a mechanical device to defy gravity, you should leave as little to chance as possible. If a

Avoid a

Lawsuit

By Brendan Casey

I was recently hired by a law firm to review the technical evidence in a litigation surrounding a forklift incident. According to witness reports, a man was riding unrestrained on the forks of a forklift.

While at height, the forks dropped several inches without warning, causing the man standing on the forks to lose his footing and fall to floor. He was seriously injured. The operator was not operating any controls when the forks lost height.

Despite the contributory negligence of the injured party--he was aware that riding on the forks of a forklift without a man cage is not a safe or acceptable practice--a case was brought against a contractor who had performed maintenance work on the forklift prior to the incident.

According to witness reports, the contractor’s service technician had been called in to replace a burst hydraulic hose. As a consequence, the presence of air in the hydraulic system--and therefore the service technician’s failure to properly bleed the system after replacing the hose--was advanced as the cause of the sudden dropping of the forks by the expert witness for the injured party.

Air is problematic in hydraulic systems and can be present in four forms: • Free air: such as a pocket of air trapped in part of a system.

• Dissolved air: hydraulic fluid contains between 6% and 12% by volume of dissolved air.

• Entrained air: air bubbles typically less than 1 mm in diameter dispersed in the fluid.

• Foam: air bubbles typically greater than 1 mm in diameter that congregate on the surface of the fluid.

Of these four forms, entrained air is the most troublesome. Problems associated with entrained air include • increased heat-load • reduced thermal conductivity of the oil • oil degradation through an increase in the rate of oxidation and thermal damage (dieseling) • reduced fluid viscosity, which leaves lubricated surfaces vulnerable to wear • cavitation erosion • increased noise levels • decreased efficiency • reduced bulk modulus, resulting in spongy operation and poor control response (air is 10,000 times more compressible than oil!)

But was air the culprit in this case? Well, as they often are, the technical arguments surrounding this question were complex. Beyond the physics involved, the complexity of the issue is com14 | July/August 2010

jetliner or aerial work platform comes down in an uncontrolled fashion, people get killed or injured.

In the aviation industry, nothing happens by way of aircraft operation or maintenance without a procedure and a corresponding checklist. This is the foundation of the industries’ excellent safety record, which is the premise on which the public’s confidence in air travel is based.

The same can’t always be said about the aerial access industry specifically and the hydraulics industry generally. In the situation above, had the technician looked in the forklift’s operating manual, he would have found a procedure to be followed before the machine was returned to service and after repairs had been carried out on the hydraulic system.

Among other things, this procedure involved carrying out a functional load test. Had the technician followed this procedure and documented it properly, it would have slammed the door shut on litigation arising from improper maintenance. And it’s likely there’d have been no pay day for the attorneys on this occasion!

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 his Web site: www.HydraulicSupermarket. com. You can also learn more by checking out his book, Insider Secrets to Hydraulics.

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July/August 2010 | 19

Part One

Hydraulic Vane Understanding the

By P.K. Guha, Attica Hydraulic Exchange Corp.

P mp 3

V

olumes of textbooks and papers have been written on hydraulic product applications and systems, but rarely have we analyzed or explicitly described how we can get the best out of a hydraulic system and pump. To simplify the process of understanding, this article is being written focusing on the practical aspect of a hydraulic vane pump and its application, and how to obtain the fullest life out of it.

History Early in the 17th century, The French scientist and mathematician Blaise Pascal’s law made today’s hydraulic industry possible. The use of confined fluid in transmitting power led us to invent hydraulic pumps as a prime mover for this phenomenal power (Fig. 1).

The simple example of an early pump is a water tube well, also known as a vertical reciprocating pump (Fig. 2).

Early on in the 20th century, the non-positive displacement and unbalanced type fixed volume vane pumps were designed for low-pressure applications, gardening, and fluid transfer applications. However, between WWI and WWII, the first positive displacement and balanced type vane pump was designed and commercially produced by Harry Vickers.

During last 50 years, the vane pump designs went through continuous im20 | July/August 2010

provement for higher efficiency, flow, and pressure.

Today’s Vane Pumps Most of us in the hydraulic industry know that a pump in a hydraulic system is like a human heart. While each component in a hydraulic system plays a significant role, nothing in the whole system really works if the pump fails.

Pumps are chosen for any hydraulic application, be it mobile or industrial, based upon the system requirement for force and speed. The rest of the hydraulic unit, such as valves, motors, and cylinders in the system are sized depending upon the system flow and pressure dynamics, application requirements, and functions.

1

What is a Hydraulic Pump?

Simply stated, a hydraulic pump is merely a fluid transferring device that transfers fluid from the inlet of the pump to the outlet and to the system.

Some vane hydraulic pumping devices are positive displacement and others are non-positive displacement types.

There are wide varieties of pumps, under two categories: (1) vane, piston, gear, reciprocating, impellor, radial plunger, and screw type and (2) variable and fixed displacement categories. The variable displacement pumps are generally pressure compensated and could be with a variety of different controls, such as horsepower, pressure, and torque-limiting control func-

2

Fig. 1: Pressure Basics Fig. 2: Tube Well Fig. 3: Vickers V10 Pump

tions. All types of vane pumps have a significant field population in variety of industry segments with mobile and industrial hydraulic applications.

Positive Displacement Pumps Most industrial high-pressure pumps that are available in the industry are “positive displacement pumps” (Fig. 3). This category has an internal “positive sealing” between its inlet and outlet ports. In other words, the oil at the outlet port of the pump can’t (or should not) leak/slip back to the inlet port of the pump. This is the reason why in a positive displacement pump if the outlet port is plugged without any safety valve, the oil/fluid has nowhere to go and creates high resistance/force to break something in the pump (generally the weakest component first) and causes failure.

All positive displacement pumps have higher volumetric efficiency as well as high-pressure capabilities.

Currently, most positive displacement pumps have 90 to 95% volumetric efficiency. Better pump efficiency means lower heat generation and less power consumption. Obviously, all this means is better system performance and higher productivity.

When the internal positive sealing between the inlet and outlet port of such pumps starts deteriorating, the internal slippage takes place within the pump. That means that oil at the outwww.ifps.org | www.fluidpowerjournal.com

Fig. 6: Vickers 25V Pump

let port of the pump under load slips out to the inlet port, which is the low presser side with only vacuum pressure. This reduces the pump volumetric efficiency, which in turn generates heat and consequent eventual pump failure. Losing the volumetric efficiency is nothing but converting the mechanical energy into heat energy without taking any work out of it, which in turn obviously does a lot of other damage in the hydraulic system. The end result of this internal leakage is excessive heat in a hydraulic system, inefficient equipment, and added cost.

There could be many other reasons in a system for generating such unwanted heat, however, a malfunctioning pump is the first early source of heat generation in a hydraulic system.

That is why so many design improvements have been implemented in a positive displacement pump to ensure the internal positive sealing mechanism is built in. Different manufacturers have different ways to obtain this internal sealing mechanism between a pump inlet and outlet ports.

Non-Positive Displacement Pumps Some of the early vane pump designs were of non-positive displacement nature, and many industrial pumps for applications below 100 psi come under this category, such as water and other fluid transferring pumps.

This category of pump design does not carry the internal sealing feature between the inlet and outlet ports, thereby, under little resistance at the outlet port, the fluid/oil leaks or slips back to the inlet port of the given pump. Such pumps are commonly used for very low-pressure applications or for fluid transfer purposes because hardly any heat is generated and does not jeopardize the hydraulic system. A water pump used for gardening is a good example of a non-positive displacement pump.

Vane Pumps All vane pumps are further divided into two groups: balanced type (Fig. 4) and unbalanced type (Fig. 5), which are further classified into two more groups: fixed displacement and variable displacement. Almost all industrial vane pumps are of positive displacement and balanced type.

Fig. 7: Continental Hydraulic PVR Pump

Fig. 8: Vickers V2010 Pump

A vane pump could also be of variable pressure-compensated type or of fixed displacement nature. The variable displacement pumps will have built-in features to vary the volume of oil output at the outlet port based on system demand. This feature reduces the pump making additional heat because the input energy is based on system requirement and hence fully used to cause any heat loss.

Whereas in a fixed displacement, the outlet flow of a given size of pump remains constant and is based on fixed input RPM at which the pump is driven. Therefore, the pump is developing a constant fixed flow even though system requirements may not be the same in most parts of the cycle of the operation or application.

In such an event, the flow is blowing over the set relief valve to reservoir without performing any work. Thus, the input energy was used for developing full pump volume to capacity but not fully utilized. This unused energy is then turned to heat energy.

All vane pumps used in mobile and industrial applications are of a balanced type, and pumps for mobile applications are equipped with heavy-duty bearing. The “balanced type” means that there are two inlet and outlets within the pump rotating components. This nullifies any unilateral side load on the pump shaft.

The mobile vane pumps can go for comparatively higher input RPM than a similar pump designed for an industrial hydraulic application, such as machine tools, plastic injection molding applications, etc. The vane pumps for mobile applications are equipped with a rugged spline drive shaft in addition to a heavyduty shaft bearing to handle higher system pressure.

Indeed, in industrial applications there are high-pressure vane pumps of “unbalanced” nature, where the pressure requirement is low, unlike mobile applications.

An unbalanced positive displacement vane pump will generally have a heavy-duty shaft bearing along with self-aligning bearing.

Fixed displacement vane pumps (Fig. 6) will deliver a

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Fig. 9: Vickers 2520V Pump

fixed volume of oil at the pump outlet while running at fixed input shaft RPM and fixed resistance (pressure) at the pump outlet, as described above. In variable displacement vane pumps (Fig. 7), outlet flow can vary while running with a fixed input drive RPM. Rating Vane Pumps Different manufacturers rate their pumps in different ways, based on outlet flow capacity and pressure the pump can withstand. The cubic inches per revolution delivery of oil flow at 100 psi resistance at the outlet port is more standard and common.

The vane pumps can also be rated based on gallon-per-minute (GPM) or liter-per-minute (LPM) while being run at 1200 rpm and 100-psi outlet resistance. This is yet another general standard maintained by most manufacturers under ISO. For example, a five-gallon pump means that the vane pump delivers five gallons per minute flow at 100 psi at the outlet port while input RPM is 1200. Obviously, if a given fivegallon pump, which may be rated to withstand 2000 psi, provides 4 GPM at 2000 psi, the pump is only 80% efficient at the peak pressure. That means 20% of flow in this pump is internally slipped through to the pump inlet at the rated 2000 psi. The hydraulic system designer mostly uses a lower-efficient pump for low-pressure hydraulic applications. Generally most vane pumps, as mentioned above, are 90-95% efficient.

The Vickers V100/200/300/400/500 series pumps (single or double) are all from medium-pressure duty application range up to 2000-psi max. The

Fig. 4: Balanced Vane

Fig.10: Vickers VMQ Pump

pumps are of “thick vane” category, which means larger under vane area.

The system pressure acting under the vane to keep the vanes out tracking the ring contour results in very high and heavy “tip loading” between the ring contour and the vane tip. Therefore, these category pumps could not be operated for higher pressure application beyond 2000 psi because of the pump ring metallurgy.

In Racine PV series pumps, the tip-loading problem is solved the opposite way. In the early Racine design, pump vane-to-ring contour surface contact is very small due to the vane tip angular profile.

V10/20 series Vickers Single and Double Pumps The redesigned V10/20 series pumps (Fig. 8) have thinner vanes compared to V100/200. Therefore, the under vane area, when applied with the similar under-vane pressure will exert lesser vane-to-ring contour loading. The functional concept remained the same; only the performance improved. The pump inlet characteristics were also changed for a better inlet condition, therefore, the series could also handle higher volume with higher input RPM. VHO/VQ series Vickers single and Double Pumps The VHO/VQ series (Fig. 9) has a small vane insert within a larger vane.

This design concept reduces the vane tip to ring contour tip loading by 75%, particularly while the vanes are at the outlet quadrants. VHO (Vane Pump High-Pressure Operation or Very High Operation) and VQ (Vane Pump-Quiet

Fig. 5: Unbalanced Vane July/August 2010 | 21

11

12

Operation or Very Quiet Operation) pumps revolutionize the vane pump applications in the industry. This series has rated system pressure capability up to 2500-4000 psi and in specific models up to 4500 psi.

VFP/VMQ series Vickers Single Vane Pumps This heavy-duty, high-performance Vickers vane pump (Fig. 10) is rated for very high volume and system pressure over 5000 psi.

Racine PVS/PVR/PVQ Series Vane Pumps This was a very popular series of Vane pumps that Racine marketed in the industrial hydraulic market between 1970 through 1995. Therefore, field population of these series of pumps still exists in the market, but they are rarely used for a new application anymore. The rotor and the shaft are an integral part of this single vanetype pump. Therefore, the straight line

22 | July/August 2010

Fig. 11: Bosch Rexroth VPV Pump Fig. 12: Denison T6CC Pump

between the shaft and rotor center line is very critical and very sensitive to input motor shaft to pump shaft alignment. This is one of the reasons why this series uses heavy-duty self-aligning bearing. The bearings are copper/ bronze imbedded with steel design type. Currently, Continental Hydraulic manufactures this series of pumps under license from Rexroth Hydraulics.

Rexroth Vane Pumps Rexroth vane pumps (Fig. 11) entered the hydraulic market much later.

The “Whisper” series pumps are rated for pressure of 3000 psi and have a sizable population in the field in a variety of applications. Rexroth currently has subcontracted Continental Hydraulics to manufacture this series of pumps.

Denison T6/7 Vane Pumps Parker on their own had very little to offer in the vane pump market, however, after they acquired Denison Hydraulics, they emerged into the

vane market. The vane tip loading in the T6 series vane pumps (Fig. 12) are extraordinarily low. Therefore, these pumps can go for very high-pressure applications. The single pumps are rated for max 60 GPM with over 5000 psi. Eaton-Vickers VPF-VMQ is a somewhat improved version of the Denison T6 series pump.

In most mobile and industrial applications and equipment, Vickers “intra vane type” and Denison “vane with pins type” pumps are used widely.

These are all fixed volume high-pressure pumps. Vickers VHO/VQ and Denison T6 series Vane pumps have by far the largest field population in mobile and Industrial hydraulic equipments and machineries.

The material composition, heat, and surface treatment of ring, rotor, vanes, and drive shafts for Vickers and Denison pumps are significantly different than the other manufacturers in the globe. Vickers mobile vane pumps of “VQ” series have flex plates supported by support plates in place of conventional pressure and wear plates in the industrial pumps. The flex plate material composition (Zinc, Copper, and Tin combined with Bronze) has unique physical properties. The plate virtually flexes (contraction and expansion due high sensitivity to coefficient of linear expansion) to suit the ambient tem-

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perature. This property is uniquely suitable for cold start operation, when the pumps are required to start at sub-zero ambient conditions, such as in mobile construction equipment applications.

This equipment is constantly stationed and exposed to outside low ambient temperature during the severe winter.

During the extreme cold start-up condition, oil viscosity is very high (thick fluid) and the fluid takes time to form a lubrication film between the flex plate and the rotor surface. Due to the physical properties of material in the flex plate, the surface becomes somewhat concave to allow thick high viscosity oil to form the lubricating film between the flex plate and rotor. This avoids a pump seizure. As soon as running temperature increases, the flex plate surface straightens enough to maintain the required clearance between the flex plate and rotor surfaces to avoid any unwanted internal slippage.

The vane tip angle and vane bottom surface area play a significant role in vane tip loading in a given pump.

Therefore, designers have ensured that the high-pressure pumps have reduced tip loading, thereby making the pump operate at a higher pressure range and as well with better efficiency.

Look for Part Two of this article in the Manufacturers Directory.

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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:

FigureItOut

Vane Pump Failures on a Compactor

A scrap yard has a metal compactor that is fed by a large metal shredding machine driven by a 1500-hp electric motor. The compactor has a three-bank series manifold with DO5 directional valves incorporating A & B meter-out flow controls. Circuit relief valves are used on all the A & B lines to protect the vane pumps and reduce energy consumption. Only one circuit at a time is engaged during operation and each function operates at a different pressure.

The PLC program was checked and verified that all the interlocks would only let one function operate at a time. The lowest relief valve was set at 600 psi while the highest relieved at 2100 psi.

The idea was to use meter-out flow controls and set the various relief valves approximately 150 psi above the cylinder and motor requirements so the various circuit relief valves would reduce the heat generated when the unit operated. Workers were taught that flow controls cause heat and if possible, it was best to keep relief valves set as low as possible and flow controls as open as possible to get the required speeds.

The workers were having problems with the vane pumps not lasting more than one to two months and sometimes only a week or two. The repair shop determined that the failure was due to excessive pressures. The side plates were “smearing” the ends of the vanes and rotor, as well as destroying the brass coating on the end plates. However, there were no signs of cavitation or aeration, and there wasn’t any scaring on the inside face of the rings or tips of the vanes.

All of the relief valve pressures were verified, and none were found to be out of adjustment.

Any idea what could be causing the problem?

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

Previous Problem:

Molding Press with Intensifier (from the May/June 2010 issue) An aerospace subcontractor used an old modified upward-acting rubber press to mold and cure a rubber-type coating to a part used in the manufacture of the B-1 bomber. The existing hydraulic system of the press was not able to reach the pressures required to keep the mold closed when the material was curing. To increase the pressure, a 4:1 Modern Controls oilover-oil intensifier was added to the circuit (see the basic schematic). They also added a bypass check around the intensifier to allow quick closure until pressure was needed, and then the intensifier completed the cycle.

The unit worked well for about four months, and then the intensifier failed.

On inspection, broken parts were found inside. The maintenance department secured and replaced the unit with a new one, but this unit only lasted four weeks and then failed.

Maintenance workers thought the pump pressure may have been increased, causing the intensifier to fail. (The pump was capable of 1500 psi, and that could have resulted in 6000 psi exceeding the 4000 psi intensifier rating.) They had verified 700 psi at the pump was the correct setting needed from the compensator to result in 2800 psi needed at the mold. They found the safety relief was set at 3500 psi, so they reset it to 850 psi.

The third replacement intensifier failed in six weeks.

SA E" No A" 3 w /4-1 In 1

Sto TOO ck TH

Solution:

The intensifier with a high flow bypass check is a great way to get additional pressure at a small price. Many intensifiers have a limit on the maximum cycles per minute. Turner Hydraulics was called in to troubleshoot the problem and found the needle valve NV-1 was fully open. This allowed the intensifier to cycle far beyond the rated maximum cycles per minute. They adjusted the flow to the proper amount and removed the handle to prevent future problems. As was the case in this situation, operators always want machines to cycle faster, so they adjust valves without understanding the limits. www.ifps.org | www.fluidpowerjournal.com

Request more information at www.fluidpowerjournal.com

July/August 2010 | 23

Fluid Power

a Critical Factor in Offshore Engineering When you are standing at the gas pump fueling up (insert your preferred vehicle type here) do you ever wonder how the gasoline or diesel got there?

Most are aware that the gas station doesn’t make the fuel, but rather it is processed from crude in a refinery and that it was the product of drilling either on land or increasingly, offshore. Have you ever really thought about how the oil is drilled for and the equipment used to bring it to the surface? Have you ever considered the technology that makes this happen?

Pipe Racker

By Rance Herren, CFPS National Oilwell Varco

O

ff s h o re d r i l l i n g – where the drilling rig is not physically situated over land first – began around 1891 in the shallow freshwater of a manmade reservoir in Ohio. Saltwater wells were first drilled around 1896 in the Summerland fields of California on top of piers extending some 300 feet from the beach into the Santa Barbara Channel. Over the next few decades and as technology increased, offshore drilling continued in such places as the Canadian side of Lake Erie and Caddo Lake in Louisiana. Shortly after the turn of the century, the first coastal wells began appearing off the gulf coast of Texas and Louisiana. Through the ensuing decades, drilling activity grew in the shallow continental shelf areas in the Gulf of Mexico, particularly in the waters off the Louisiana coast. To that point, however, all of the wells drilled were well within the sight of land.

I n 1 9 4 7 , t h e K e r r- M c G e e Corporation drilled the first well out of the sight of land from a built-for-purpose fixed barge and platform in 20 feet of water. Within a couple of years, over a dozen fields were discovered in the Gulf of Mexico marking the beginning of the modern offshore drilling industry. Today, offshore drilling in locations hundreds of miles from shore and in thousands of feet of water are routinely and extensively found in the Gulf of Mexico, Newfoundland and Nova Scotia, the coasts of Brazil and Venezuela, the North Sea, Persian Gulf, Southeast Asia, Russia, and West Africa. New seismic technology allows geologists to accurately locate oil reservoirs that have been previously undetectable. Advances in rig design and drilling techniques allow wells to be drilled in locations at one time considered impossible due to the difficulty of reaching them and the prohibitive high cost associated with such an endeavor. Increasingly, these oil reservoirs are being found in offshore areas known as ultra deep water – depths of up to 10,000 feet before the drill bit contacts the ocean floor with drilling distances thereafter of over two miles. The effort to recover crude from these depths is enormous, but new technology and innovation continue to make this possible.

Perhaps the most enduring of technologies used in the drilling for oil and gas is fluid power. There is

scarcely a piece of equipment found on any offshore rig that does not include hydraulic and pneumatic technology of some sort – from the most basic circuit manually operating a fluid motor driven winch to ultrasophisticated closed-loop position, velocity and force feedback systems – controlled via SCADA (Supervisor Control and Data Acquisition) platforms and communicating over digital bus networks complete with zone management and anti-colli-

ing process, both above and below the waterline. Rig floor equipment is used to handle the drill pipe and actually create the well bore. Modern offshore drilling rigs typically utilize what is commonly known as a Top Drive. The top drive provides the rotational power to turn the drill string – which are multiple sections of pipe that are connected together with the drilling bit attached at the opposite end. Although in most offshore applications the main rotary drive is

Top Left and Right: Early Offshore Drilling Rigs Bottom Left: Top Drive Bottom Right: Modern Offshore Drilling Rig

sion detection. Equipment utilizing hydraulic and pneumatic systems, coupled with variable frequency drives, electrohydraulic controls, motion controllers, electromechanical actuators, and programmable logic controllers are becoming commonplace in the industry. Coupled with other advanced technologies, fluid power is most often the control medium of choice. Modern drilling rigs are textbook examples of mechatronics in all of its glory.

In offshore drilling, there are many types of equipment used in the drill-

www.ifps.org | www.fluidpowerjournal.com

electro-mechanical, top drives are rich with hydraulic and pneumatic systems; some even have fully integrated and self-contained hydraulic power units.

Iron Roughnecks are machines used to join one piece of drill pipe to another using low speed, high torque motors in what is commonly called a "spinning wrench" to spin in and shoulder a connection. The final part of the sequence uses hydraulic cylinders in a wrench of sorts to clamp on and torque the connection to a predetermined value. Although

many modern iron roughnecks are manually controlled, a large and increasing number of designs are fully automated and include closed-loop electrohydraulic controls to minimize cycle time and to increase efficiency and repeatability.

Moving drill pipe to and from storage areas and the well center requires the use of various types of pipe handling equipment. These can range from simple belt driven conveyors using radial piston or gerotor motors to complex cylinder actuated horizontal to vertical systems and multi-axis robotic racking machines that manipulate pipe about the drill floor. Again, using closed-loop electrohydraulic and mechanical systems, these machines are maximized for efficiency and safety.

Drill ships and semi-submersible drilling rigs have motion compensation equipment fit with multiple accumulators and banks of auxiliary nitrogen gas bottles to control very large bore and stroke hydraulic cylinders. The accumulators provide for high instantaneous flows and shock absorption, stroking the cylinders to compensate for vertical movement of the rig due to wave-induced heave so that the weight of the drill string on the bit at the bottom of the well bore remains relatively constant.

The challenges of offshore drilling are numerous. Not the least of these challenges are any of the otherwise normal installation, commissioning, maintenance, or repair issues that any piece of mobile or industrial machinery is likely to have. Now consider dealing with those same kinds of issues when that equipment is situated offshore, anywhere from a few to several hundred miles, where even procuring a simple o-ring to repair a leaky valve becomes a major ordeal. The logistics can be incredible. Equipment used in offshore applications is routinely subject to the most demanding requirements in the harshest of environments.

Once on contract to drill, the rig and the supporting machinery are many times operating at a 100% duty cycle for days or weeks on end. The most sophisticated of rigs capable of drilling the deepest wells command rates of $400,000 to $500,000 (and historically even higher) per day. Rig uptime is critical, and the impacted cost of equipment failure can be staggering.

The technology driving the petroleum industry today is a direct reJuly/August 2010 | 25

Top: Iron Roughneck Right: Drill String Motion Compensator sponse to the increasing worldwide demand for oil. The future of oil and gas drilling on land or offshore will continue to be layered with increasing challenges requiring more innovative solutions to problems, which in many cases have yet to be identified. The need for engineers, technicians, and service personnel with multi-faceted skill sets will create opportunities for talented and creative individuals and businesses interested in taking part.

Where high-power density, flexibility, ease of control, and reliability are called

for, hydraulic and pneumatic technologies will continue to play their vital role.

The types of drilling equipment and the technologies covered in this article are but a sliver of those found above the waterline, let alone those found sub-sea or down-hole. For those interested in learning more about the many facets of oil and gas exploration and the types of machinery and processes involved, several Web sites and publications are available: American Petroleum Institute is an industry trade association rep-

resenting the U.S. petroleum industry including exploration and production, transportation, and refining. The API develops equipment engineering and manufacturing standards and provides compliance certification.

Offshore Magazine is a monthly industry publication covering news, trends, and issues related to offshore drilling technology, exploration, and production.

Rig Zone is a Web-based magazine and resource focusing on both land and offshore drilling markets and provides subscribers with daily updates and weekly e-mail newsletters.

Offshore Technology Conference (OTC) is an annual trade show and conference held every May in Houston, Tex. OTC is the world’s foremost event for the development of offshore drilling, exploration, and production, drawing over 55,000 attendees and 2,500 exhibitors from across the world.

In closing, I can’t imagine anyone reading this article who has not been following the human and environmental tragedy that has happened as a result of the loss of the Deepwater Horizon off the southeast coast of Louisiana. Although the true cause leading up to this accident may never be known, the sudden and violent loss of life and the subsequent eco-

logical damage is a stark reminder of the true power of Mother Nature and the respect that she demands. In the years to come, the global thirst for energy will only continue to increase and even as alternate sources are being pursued and developed, the demand for oil and gas will remain a significant part of the energy equation. To meet these crucial needs, the requirement for well-engineered, reliable, and serviceable equipment with the safety of operating personnel and protection of the environment will be paramount. To that end, fluid power will remain at the forefront of technologies that contribute to these efforts.

About the Author: Rance Herren is the manager of Hydraulic Engineering for the Rig Solutions division of National Oilwell Varco, a global leader in technology-driven solutions for the petroleum drilling and exploration industry. He is based in Houston, Tx. Mr. Herren is a graduate of the Industrial Controls program at California State University Fullerton and the Electrical and Electronic Technician program at Chaffey College in Rancho Cucamonga, Ca. He is a Certified Fluid Power Specialist (CFPS) with over 23 years experience in the application of fluid power technology.

He can be reached at rance.herren@nov.com.

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Special Advertising Section • Request more information on Product Spotlight advertisers at www.fluidpowerjournal.com

ProductSpotlight | pumps & motors SOCKET HEAD FLANGE ADAPTERS

ADACONN® PORT CONNECTORS The patented Adaconn® Port Connector provides a compact means to join two flanges or flange ports, when used with Adaflange™ and Adaflangeport™ Socket Head Flange Adapters. Flange ports of the same or different sizes (or even different SAE codes) may be joined together. Prior to assembly the one piece 4-bolt flanges are kept as captive assemblies that are free to rotate 360 degrees about the longitudinal centerlines to facilitate proper alignment.

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The patented Adaflange™ and Adaflangeport™ socket head flange adapters provide the industry’s shortest means to adapt an SAE 4-Bolt flange port to a threaded connection. An internally broached hex provides compact, centerline wrenching. SAE Code 61 and Code 62 flange patterns, in sizes ranging from ½ to 3 inches, may be adapted to JIC 37° Flare, SAE Straight Thread, ORS, and ANSI B1.20.3 NPTF male threaded ends.

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Use of the Adaflange™ and Adaflangeport™ together makes a great union connection. When used with an Adaconn® Port Connector, two flanges or flange ports (of the same or different sizes or SAE codes) may be joined in a compact manner.

Adaconn® Blue Bell, Pennsylvania www.adaconn.com 215.643.1900

Adaconn® Blue Bell, Pennsylvania www.adaconn.com 215.643.1900

H6 Heavy Duty Cylinder

TORQTITE Adjustable Torque Wrenches

The Yates Industries H6 Heavy Duty Cylinder is rated for 3000 PSI and features 1½ to 20” bores standard, 22 different mounting options, is JIC-NFPA interchangeable, and can be customized with nearly limitless combinations of rod ends, cushions, couplers, seals, and ports – all backed by our legendary warranty and repair capabilities.

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Flaretite’s new adjustable openend torque wrenches allow all tube and hose ends to be precisely tightened to their correct torque recommendations. These new wrenches fill a void across all industries where fitting connections are used. Developed to compliment Flaretite’s patented flared seals for 30, 37, and 45 degree flared fittings, these new wrenches are used by quality conscious mechanics in hydraulics, pneumatics, pharmaceutical, chemical, medical and environmental industries.

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Yates Industries 23050 Industrial Dr. E. St. Clair Shores, MI 48080 586-778-7680 www.yatesind.com

ALPC 1/2 and GHPC 1/2 Series Multiple Pumps These “small wonders” feature a reduced axial length allowing easy fit within compact applications. The pumps are available in 2 or 3 segments and offered as a fully aluminum pump (ALPC) or with a cast iron flange/ cover (GHPC) as well as a wide range of flange, shaft and port configurations.

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Contact:

Marzocchi Pumps USA 905 Albion Schaumburg, IL 60193 Phone- 800.924.5404; 847.923.9910 Fax- 847.923.9937 pumps@marzocchipumpsusa.com

Torqtite wrench benefits: • Adjustable torque settings from 10 - 420 Nm (8 – 310 lb-ft) • Adjustable Hex size (jaw opening) from 7/16” thru 3” • Low profile, reversible, spanner design • Precision quality design with +/- 4% accuracy • Supplied with torque rating tables for most common fittings For more information contact:

Flaretite Inc.

Fenton, MI, USA Ph: 810-750-4140 www.flaretite.com

Request more information on Product Spotlight advertisers at www.fluidpowerjournal.com

Marine Duty Electric Clutches

Electric Clutches for Pumps

Ogura electromagnetic clutches provide a quick and easy engagement of a hydraulic pump, winch drives or other marine components. Available torque range is 100 pound feet to 1500 pound feet with single-face friction designs. Multiple disk units can generate torques over 8,000 pound feet. Large bearings, e-coating and a single piece bi-directional spring provide durability in harsh environments.

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Ogura produces a wide variety of electric clutches for mobile applications. These clutches provide simple on/off operation for a variety of pumps. Remotely engaging the pump through the clutch reduces drag on engine start-up, increases pump-life and allows multiple pumps to be used off one engine. Various belt types as well as pump shafts can be accommodated.

Contact:

Contact:

100 Randolph Road | Somerset, New Jersey 08873 Phone: 732-271-7361 | Fax: 732-271-7580 info@ogura-clutch.com

100 Randolph Road | Somerset, New Jersey 08873 Phone: 732-271-7361 | Fax: 732-271-7580 info@ogura-clutch.com

Ogura Industrial Corp.

BSPP, BSPT, ISO 6149 HYDRAULIC FLANGES & COUPLINGS

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Ogura Industrial Corp.

Miniature Quick Disconnects The F-4150 series Quick Disconnect simplifies tubing connections during assembly.

The male-threaded Quick Disconnect is available in three barb configurations: straight, elbow, and tee. Depress the latching pushbutton to remove the barb; re-insertion of the barb locks it into position. The unique design allows the fitting to swivel 360º.

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Air Logic www.air-logic.com Email airlogic@air-logic.com Call (800)558-5950

High Torque, Low Speed Hydraulic Motors MAIN Manufacturing Products, Inc. now stocks SAE, JIS, DIN, and ISO flanges and couplings with metric ports. METRIC TUBE & PIPE sizes in socket weld and butt weld are also available. Many can ship directly from stock. If not part of our 7000+ in-stock products, MAIN can manufacture and ship quickly- (4-5 days) is common from our US facility.

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MAIN Manufacturing Products, Inc. Phone: (800) 521.7918 E-mail: info@mainmfg.com

Western FluiDyne high torque, low speed hydraulic motors are a cost effective, form, fit and function interchange for the common brands of motors. Hundreds of displacements and model variations of the popular “H”, “S”, and “2000” series are in stock. Customer Service is available to provide technical information and assist in model code selection or interchange.

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Western FluiDyne For additional information contact us at: 586-296-7200 or sales@westernfluidyne.com www.wfdyne.com 29

Special Advertising Section • Request more information on Product Spotlight advertisers at www.fluidpowerjournal.com

ProductSpotlight | pumps & motors NEW thread size has been added to our 1/2" ISO 16028 Flush Face interchange. Now available with 7/8"14 female ORB thread, commonly used on a variety of Skid Steer Loaders. All SafeWay Flush Face products are designed, machined and assembled in the USA, by SafeWay. No European private branding.

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JPPS

Low Speed High Torque Hydraulic Motors

FFE49 Series

Contact us for more information.

SafeWay Hydraulics, Inc.

4040 Norex Drive / Chaska, MN 55318 Email: mail@safewayhyd.com www.safewayhyd.com

released just

The Ultra Clean UC-EL 1.25 Economy Launcher

cost low • Combination of drive shaft roller and needle bearings for shaft side load support • Priced to compete with the Gerotor design motors • Interchanges with the Charlynn® "H" and "S", Danfoss DH, and other leading motor manufacturers.

• Displacements from 3.04 to 24.38 cu. in3/rev.

For more Info: Dynamic Fluid Components, 800-988-1276/ Fax: 864-638-0005 2810 Blue Ridge Blvd.

West Union, S.C. 29696 www.dynamicfc.com

The ULTRA CLEAN UC-EL 1.25 Economy Launcher offers a fast, less invasive way to clean contaminated hydraulic lines by shooting an Ultra Clean Projectile through the hose or tube assembly. The Ultra Clean Projectile strips out internal contamination, removing dirt, gunk and oil. Take your best shot with Ultra Clean!

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For more information contact:

Ultra Clean Technologies Corp.

746 Shiloh Pike Bridgeton, NJ 08302 Phone: 800-791-9111 or 856-451-2176 Fax: 856-453-4975 E-mail: sales @ultracleantech.com www.ultracleantechnologies.com

Inc.

Fast Simplified Cylinder Ordering

Hydraulic Suppressor

Peninsular’s model HP, MH and LM cylinder Configurators accessible through Peninsular’s website at www.Peninsularcylinders.com make cylinder ordering easier because customers answer questions from drop down menus eliminating the need for confusing cylinder catalogs and complex engineering data. “Helpful hints” answer all user questions that may arise. A solid model and corresponding part number appear once configured.

Instant solid model and 2D flatline drawings with dimensions may be instantly downloaded and instant quote requests included.

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Peninsular Cylinder Co. Inc. Toll Free: 800-526-7968 | Phone: 586-775-7211 Fax: (586) 775-4545

The small, compact Wilkes and McLean Suppressor makes a BIG difference in reducing hydraulic noise in your systems. The easy to install suppressor is an in-line device that takes out hydraulic pulsations, vibrations and shock. This greatly reduces the noise that these systems can generate.

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Wilkes and McLean 847-534-2000 for information or check our website wilkesandmclean.com

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“A” FLANGE, 2DG SERIES DOUBLE PUMPS Now available from stock…Honor 2DG double pumps.

Honor Gear Pumps Corp. of Taiwan, with U.S. warehouse in Houston, Texas, is pleased to announce the immediate availability of their 2DG series, double pumps. The aluminum body pump, employs cast iron covers for best performance under extreme conditions, and comes standard with viton seals. Displacements from 1.31 to .30 cu.in./rev. can serve many requirements, with working pressures up to 3000psi.

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Honor Gear Pumps Corp.

1601 W. 25th St. • Houston, TX 77008 Toll Free Phone: (800) 984-9727 Local Phone: (713) 984-8144 Fax: (713) 461-9631 Email: service@honorpumps.com View basic specifications at www.honorpumps.com

MODULAR STACK VALVES...D03...D05

Power Valve U.S.A. represents, as factory warehouse and sales office, a Taiwan manufacturer of D03, D05, D08, and their Modular stack valves product line. With inventory in the Houston warehouse, all products are competitively priced, and machine tool quality.

In fact the parent company, Tai Huei Oil Industry Co., Ltd. has been selling valves for over 25 years to the machine tool industry in Taiwan. All standard AC and DC voltages are available, and all standard spool configurations are in stock. Special spools are available. Pressures to 5000psi and flows from 16gpm (D03) to 132gpm (D08) are standard. With inventory on the shelf and very competitive pricing, we invite your inquiry.

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Power Valve U.S.A. Contact the company at 1-888-862-1064 or e-mail to service@powervalveusa.com View basic specifications at www.powervalveusa.com

YOULI HYDRAULIC DIRECTIONAL CONTROL VALVES Pneumatic Operator option…..now available: Youli directional control valves, rated to 4600PSI, monoblock or sectional styles, are now available with pneumatic operators, in nominal flow ratings from 12GPM to 37GPM. Electrical operators are also available. Youli quality is based on 25 years of industrial hydraulic valve manufacturing for the machine tool business in Taiwan. A quality product line with a major commitment to inventory in Houston, Texas, and offered at competitive prices, is our growing reputation.

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Youli Hydraulic Industrial Co., Ltd. Contact the company at 1-888-330-8041 or email to service@youli-america.com View basic specifications at www.youli-america.com

CCEFPNEWS Center Completes 4th Annual NSF Site Visit The CCEFP completed its 4th NSF site visit following a full day of review by the site visit team.

Comprehensive presentations on the Center’s four research test beds were given along with reviews of the Center’s overall research goals and accomplishments, Education & Outreach programs, and Industrial Collaboration efforts. Graduate students presented detailed posters of the Center’s research projects and made short presentations for the site visit team during the poster show.

In addition to the posters, researchers from Georgia Tech brought along a portable version of their excavator simulator allowing users to experience operating an excavator using both traditional and haptic controllers. Representatives from the Science Museum of Minnesota were on-hand to provide interactive demonstrations of both their cutaway swashplate pump and their hydro-table.

Also on display were several other E&O hands-on displays including the portable fluid power demonstrator, regenerative pedicab, hydraulic arm wrestling machine, energy storing orthosis, pneumatic haptic interface, pneumatics kit, and hydraulic AFO simulator. The Center’s outreach efforts were well represented by students in the gidaa program from the Albrook School (Cloquet) who attended to showcase their interactive robotics projects.

Students Host Interactive Fluid Power Exhibit CCEFP students at the University of Illinois at Urbana-Champaign (UIUC) hosted an interactive fluid power exhibit during the annual student-led Engineering Open House (EOH), which took place March 12-13. Featured in the display was the CCEFP portable fluid power demonstrator, developed by Dr. John Lumkes and Jose Garcia at Purdue University to educate the public on basic fluid power concepts. Visitors at the open house were given the opportunity to try one of the two demonstrators on-hand after receiving a basic lesson on how the hydraulic cylinders worked. During the event, several hundred visitors passed through the CCEFP display ranging for small children to adults. In addition to the demonstrators, research on hydrophobic materials and the fluid power assisted orthosis was presented. CCEFP member company Festo was also on hand at the event and wowed audiences with their pneumatically powered Airmotion ride driving simulator.

The UIUC Engineering Open House features two days of exciting exhibits and competitions that showcase the talent and ingenuity of engineering students.

The exposition attracts thousands of visitors to the Illinois campus each year and stands as the largest event of its kind in the country. EOH brings together students, faculty, and corporate sponsors to feature cutting-edge innovation in the fields of science and technology to inspire the next generation of engineers through engaging hands-on demonstrations.

For more information, visit www.ccefp.org.

July/August 2010 | 31

AssociationNews

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NFPA | National Fluid Power Association

Growing the Fluid Power Challenge in 2010

he NFPA Fluid Power Challenge is a skills competition that teaches fluid power, engineering and teamwork to students in the eighth grade.

Last year, the NFPA Fluid Power Challenge was expanded to four locations in Wisconsin, Illinois and Minnesota, with nearly 200 students from 26 middle schools competing. To keep the momentum going, a shift has been made in the way that future challenges will be organized and run.

In the next several months, complete challenge instructions will be available online on NFPA’s Web site. This will give schools, universities and member companies the ability to organize local challenges on their own, greatly increasing the number of challenges held around the country. Previously, event competitions were coordinated with the help of NFPA staff.

The online instructions will contain detailed information for coordinators, facilitators, teachers, teams and judges, including rules, forms, checklists and budgets. It will even include information on how to order the challenge kits, Tshirts and trophies, and how to promote the event. NFPA staff will monitor and maintain the Web site materials, track downloads, provide support and answer inquiries from organizations interested in having their own challenges.

Another change is the addition of three new classroom exercises. New kits for a pneumatic lifter, rotational arm and pneumatic clamp will be relatively inexpensive, and will allow classroom teachers to experiment with hydraulics and pneumatics before entering teams in a challenge event. The new kits demonstrate linear and rotational movement, key principles of fluid power applications. Our goal is to have 20 challenges—through event competitions or in the classroom— in the year ahead. Two have already taken place, and two more are scheduled.

NFPA’s 2010 Industry and Economic Outlook Conference August 17 – 18, 2010 Westin Chicago North Shore • Wheeling, IL

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oin NFPA at the intersection of marketing and strategy for the highly acclaimed Industry and Economic Outlook Conference, August 1718, 2010, at the Westin Chicago North Shore Hotel. This day-and-half event offers hard data and expert analysis on tomorrow’s economic environment with an additional focus into the technology advancements likely to impact the fluid power supply chain in the years ahead.

A conference like no other, this year’s Industry and Economic Outlook Conference will offer critical insight into economics, market forecasts, technology, plus unparalleled networking opportunities.

Companies that sponsor the Fluid Power Challenge in 2010 will help fund the development of the new classroom exercise kits. In addition, as funds become available, grants will be awarded to middle school teachers to cover program material costs. Read more about sponsorship opportunities or make a donation at http://www.nfpa.com/education/nfpafluidpowerchallenge.asp.

For further information, contact Carrie Tatman Schwartz, Program Manager, at ctschwartz@nfpa.com.

Calendar of Events Supplier Golf Invitational August 16, 2010 Chevy Chase Country Club, Wheeling, IL NFPA 2010 Industry and Economic Outlook Conference August 17 – 18, 2010 Westin Chicago North Shore, Wheeling, IL

Conference highlights include • Global economic trends Alan Beaulieu, Institute for Trend Research (ITR) • Fluid power customer market overview Eli Lustgarten, ESL Consultants, Inc. • Fluid power market forecast Jim Meil, Eaton Corporation • Regulatory Landscape Aric Newhouse, National Association of Manufacturers (NAM) • Mobile and industrial market breakout sessions • Advances across the supply chain • Power of Association reception and dinner is a conference networking highlight, providing the best possible opportunity to interact with the entire conference delegation.

• Supplier tabletop exhibits, which feature networking opportunities with industry suppliers demonstrating product.

NFPA’s Economic Update Webcast October 28, 2010 10:00 am Central By: Alan Beaulieu, Institute for Trend Research

IFPE 2011 March 22 – 26, 2011 Las Vegas Convention Center, Las Vegas, NV co-located with CONEXPO-Con/AGG. Please check www.ifpe.com for more details.

August 16 – 17, 2011 NFPA 2010 Industry and Economic Outlook Conference Renaissance Schaumburg Hotel, Schaumburg, IL

2011 NFPA Annual Conference February 16 – 19, 2011 Hyatt Regency Coconut Point, Bonita Springs, FL

Don’t miss out on one of the “Can’t Miss Events of 2010!” To learn more about the conference visit www.nfpa.com or call 414-778-3344.

32 | July/August 2010

www.ifps.org | www.fluidpowerjournal.com

FPDA | Motion & Control Network

ESA | Equipment Service Association

FPDA Releases 2010 Compensation Report The FPDA Motion & Control Network has released its 2010 Employee Compensation Report, an analysis of 2009 compensation practices.

The Compensation Report is a bi-annual analysis of both executive and employee compensation including salaries, bonuses, commissions, and perks. It also includes details about fringe benefits such as health insurance, retirement programs, and employee time off. FPDA co-sponsored this study along with 30 other distribution organizations. The Report is prepared by Profit Planning Group of Boulder, Co. The complete results are presented in two documents. Combined, they provide the most complete source of information available about compensation and benefit practices for distribution industries.

• Volume 1: FPDA Detailed Report – a full analysis of participating FPDA firms. Where appropriate, FPDA results are compared with results of all participants.

• Volume 2: Industry Report – this report presents an analysis of all participating firms – 1,176 firms representing 7,000 locations are included. Firms were categorized into over 20 sales volumes and over 100 geographic areas.

FPDA participating member companies received a personalized report with individual recommendations to improve their bottom line. The 2010 PROFIT Report will be available for purchase from the FPDA Web site, www.fpda.org, in June 2010.

FPDA offers a variety of tools to its Distributor and Manufacturer members that focus on profitability and efficiency enhancement, compensation, business growth, and best-practice development and deployment. Visit www.fpda.org for information on these programs.

For more information, please contact FPDA Headquarters by e-mailing Info@fpda.org; you may also contact Profit Planning Group directly at (303) 444-9245.

2010 ESA Fall Tech Conference October 10-12, 2010 Embassy Suites Bloomington Minneapolis, MN www.2esa.org

Directional control SolenoiD ValVeS

D03..D05..D08..MoDularS

• QualitY • Price • noW! Power Valve U.S.A. Houston, Texas www.powervalveusa.com service@powervalveusa.com 888-862-1064 Tai Huei Hydraulic Co., Ltd. ...machine tool quality from Taiwan Request more information at www.fluidpowerjournal.com

www.ifps.org | www.fluidpowerjournal.com

Request more information at www.fluidpowerjournal.com

July/August 2010 | 33

AssociationNews

IFPS | International Fluid Power Society

Certification Levels Available:

IFPS 2010 Annual Meeting and 50th Anniversary Celebration

CFPAI Certified Fluid Power Accredited Instructor

Sheraton Society Hill • Philadelphia, PA

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

September 15-18, 2010

Please join us September 15 - 18, 2010 as we hold the IFPS 2010 Annual Meeting and 50th Anniversary Celebration at the Sheraton Society Hill, Philadelphia, Pa. This is a great way to network with professionals in the fluid power and motion control industry.

An anniversary dinner will be held on Friday, September 17, 2010, where many Society friends and past presidents will help the IFPS celebrate its 50 years. Two optional tours of Philadelphia are also available.

In addition to committee and board meetings, a technical workshop, “Watts It All About? The Use & Misuse of Energy in Fluid Power Systems” will be held on Saturday, September 18, 2010. Participation in this workshop contributes towards reaccreditation requirements.

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

Registration Fees

Registration must be received by August 31, 2010 (after August 31, 2010, a $25 late fee will be applied).

• Delegate: $200.00 (includes reception, business meetings, and anniversary dinner) • Spouse: $150.00 (includes reception and anniversary dinner) • Technical Workshop: IFPS Members: $125/Non-Members: $150 (both rates include lunch) • Walking Tour of Philadelphia: $20.00/per person • City Bus Tour & Philly Cheesesteak Experience: $25.00/per person

Hotel Reservations

A discount hotel rate of $150.00 + tax/night has been secured for all IFPS members attending the meeting. In order to take advantage of the discounted rate, hotel reservations must be made by August 31, 2010 and can be made by calling the Sheraton Society Hill at 1-800-325-3535. (Be sure to mention IFPS to secure the group discount.) You may also make hotel reservations online by visiting www.ifps.org.

Meeting Schedule Date

Start Time

End Time

Function

Wednesday - September 15, 2010

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

8:00 a.m.

9:30 a.m.

Strategic Planning Committee Meeting

9:30 a.m.

12:00 p.m.

Marketing Committee Meeting

12:00 p.m.

1:00 p.m.

Lunch (on own)

CFPHS Certified Fluid Power Hydraulic Specialist

1:00 p.m.

2:30 p.m.

Membership Committee Meeting

2:30 p.m.

4:00 p.m.

Finance Committee Meeting

6:00 p.m.

7:00 p.m.

Welcome Reception

CFPPS Certified Fluid Power Pneumatic Specialist CFPE Certified Fluid Power Engineer CFPCC Certified Fluid Power Connector & Conductor CFPMIH Certified Fluid Power Master of Industrial Hydraulics CFPMMH Certified Fluid Power Master of Mobile Hydraulics CFPMIP Certified Fluid Power Master of Industrial Pneumatics

34 | July/August 2010

7:30 p.m.

Optional City Bus Tour

Thursday – September 16, 2010 8:00 a.m.

12:00 p.m.

Certification Committee Meeting

12:00 p.m.

1:30 p.m.

Lunch

1:30 p.m.

4:00 p.m.

Education Committee Meeting

6:30 p.m.

9:00 p.m.

50th Anniversary Dinner

8:00 a.m.

11:00 a.m.

Board of Directors Meeting

11:00 a.m.

12:00 p.m.

Strategic Follow Up

Friday – September 17, 2010

Optional Philadelphia Historical Walking Tour

1:00 p.m.

Saturday – September 18, 2010 8:00 a.m.

4:00 p.m.

Technical Workshop: “Watts it all About”

8:00 a.m.

12:00 p.m.

FPEF Meeting www.ifps.org | www.fluidpowerjournal.com

“Watts It All About?”

The Use & Misuse of Energy in Fluid Power Systems

HII offers: Air Driven Liquid Pumps for: • Pressure Testing • Operating Hydraulic Jacks • Powering Crimping & Riveting Tools • Bolt Tensioning • Hydraulic Clamping • Autofrettage of High Pressure Components

Saturday, September 18, 2010 8:00am – 4:00pm Sheraton Society Hill – Philadelphia, PA IFPS Members: $125.00 Non Members: $150.00 Visit www.ifps.org to register

Air Driven Air Pressure Air Amplifiers for: • Tire Curing Presses • Air Pressure Boosting • Pneumatic Clamping

Join Dan Helgerson, CFPAI, and Jon Jensen, CFPAI, for a look at methods and measures to be taken in realizing energy savings in fluid power systems.

Air & Electric Driven Gas Boosters for: • Accumulator Charging • Pressure Gauge Calibration • Gas Transfer • Gas Recovery • Airbag Inflation Charging • Oxygen Charging of Life Support Bottles

Dan Helgerson will address the savings to be found in hydraulic systems including topics on • • • • • •

Flow Control Right Sizing Prime Movers Pressure Reducing Valves Accumulators Pressure Compensated Pumps Load Sensing

Jon Jensen will lead the class in a look at common issues found in pneumatic systems, including examples and solutions for the top target areas of energy savings in pneumatic systems: • • • • •

Leaks Air Blow Excessive Pressure Intermittent Demand Inappropriate Usage of Compressed Air

Interested in Becoming an IFPS Accredited Instructor?

IFPS supports career advancement through ongoing education and training. Our Accredited Instructors are certified professionals who educate and prepare candidates for IFPS Certification Programs. If you are interested in becoming an IFPS Accredited Instructor please visit www.ifps.org and click on Education/Training.

Upcoming Instructor Training Workshop August 2 - 4, 2010 Hennepin Technical College • Eden Prairie, MN Registration Deadline: July 1, 2010 Fee: $ 350.00 Job Performance Training Workshop (optional) August 5, 1020 Fee: $160.00 Visit www.ifps.org for more information or call 800-308-6005. www.ifps.org | www.fluidpowerjournal.com

gas Boosters & air Pressure amPliFiers

liquid PumPs

Visit our web site:

Hydraulics International, Inc. 9201 Independence Ave., Chatsworth, CA 91311, USA Tel: +1-818-407-3400 Fax: +1-818-407-3428

www.hiipumps.com © 2009 HII HYD-1554

Request more information at www.fluidpowerjournal.com

Avert Fluid Leak Disasters!

Some industrial fluid systems operate under extremely high pressure. So leaks can not only lead to equipment breakdown and production delays, but serious personal injury as well. Fortunately, there’s the Spectroline® OPK-340 Leak Detection Kit. It’s the most effective, efficient and safest method for finding leaks in hydraulic, oil, water and water/glycol-based industrial systems. And best of all, it finds these leaks long before disaster strikes!

Kit includes: • OPTIMAX™ 3000 super-high intensity cordless, rechargeable blue light LED leak detection flashlight • 16 oz twin-neck bottle of patented OIL-GLO™ 44 concentrated fluorescent dye for synthetic and petroleum-based oils and hydraulic fluids • 16 oz twin-neck bottle of WD-802 concentrated fluorescent dye for water-based systems • 8 oz spray bottle of GLO-AWAY™ dye cleaner • Smart AC and DC chargers, fluorescenceenhancing glasses and a rugged carrying case.

To learn more, call 1-800-274-8888 or visit: www.spectroline.com

ISO 9001:2008 CERTIFIED COMPANY

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July/August 2010 | 35

AssociationNews

IFPS | International Fluid Power Society

IFPS Newly Certified Craig Acuna, MM, PM El Paso Electric Co.

Mark Dennis, PS Norgren, Inc

James Amelung, IHM Hagglunds Drives Inc.

Todd Durnin, PM The Boeing Company

Thomas Anderson, S, HS

Daniel Durrance, PM The Boeing Company

Jeff Arbogast, S, PS, HS Hennepin Technical College Dan Bader, HS Haldex Hydraulics Corporation Kyle Bahl, HS Minnesota West Community & Technical College Zachary Ball, MHM Pennsylvania College of Technology

Scott Erickson, MHM Southern California Edison

Justin Kolander, S, PS Minnesota West Community & Technical College Kenneth Kratz, MHM C.W.C.C./DCE Adult School Keith Langner, HS Eaton Corporation Mike Lauzon, HS Boart Longyear

Liza Esterly, S, HS Benjamin Flygare, S, HS Mark Frankena, S, HS, PS Minnesota West Community & Technical College

Kathryn Lawson, S, PS Parker Hannifin Corporation Michael Loveless, PM The Boeing Company

Keith Percin, PS Norgren, Inc

Jonathan Steuter, S, HS Controlled Motion Dynamics, Inc.

Rigoberto Perez, MHM Southern California Edison

Mark Templeton, MHM Altec Industries, Inc.

Ross Peterson, S, HS

Steve Tlachac, HS Nott Company

Joseph Pizio, MHM Pennsylvania College of Technology

Steven Torres, MHM Southern California Edison

David Rajala, HS Eaton Corporation

Matthew Traunero, HS Brush Wellman

Steven Ralston, MHM Southern California Edison

William Troxell, MHM Altec Industries, Inc.

Kerry Reinhardt, S, HS TRD Manufacturing, Inc.

James True, S, PS, HS Hennepin Technical College

Lena Richards, S, PS Parker Hannifin Corporation

Roy Turpin, MMH, MIH, MIP, CC C.W.C.C./DCE

Ron Freedle, MHM Southern California Edison

Anthony Mackedanz, HS Minnesota West Comm. & Technical College

Russell Fry, PM Kellogg

Bradley McManus, HS Caterpillar

Kurtis Bassett, MHM Pennsylvania College of Technology

Seth Gilstrap, S, HS Oklahoma State University

Murdock McNickle, HS Minnesota West Community & Technical College

Alan Bergstrom, Sr., MHM IUOE Local #478

Nathan Glover, MHT Hennepin Technical College

Cory Besel, S, PS, HS Hennepin Technical College

Josh Gramentz, S, HS, PS Minnesota West Comm. & Technical College

Ernesto Mendez, HS Lovat, Inc.

Jeffrey Greene, MHM The Raymond Corporation

Ken Mieding, HS Motion EFX.

Robin Sand, S, HS

Jeffrey Gullick, S, HS, PS

Steven Miller, HS Haldex Hydraulics Corporation

Brian Sanders, MHM Southern California Edison

John Montoya, MHM Southern California Edison

Daniel Scaminace, PS Parker Hannifin Corporation

Jason Moore, S, PS Parker Hannifin Corporation

Nick Schroeder, S, HS, PS

Derek Balzer, HS Eaton Hydraulics

George Medeiros, MHM Altec Industries, Inc.

Joshua Boltz, S, HS, PS Jay Brewer, PM Kellogg Kent Campbell, PS Parker Hannifin Corporation Zhaodi Chen, S, PS Maclean Engineering and Marketing Co. LTD T. Parker Cook, S, PS Parker Hannifin Corporation

Jesse Hartmann, HS Eaton Hydraulics T. Benjamin Hayes, PM Kellogg

James Cooper, III, HS Hydraquip Corporation

Robert Hestness, S, HS

Jamie Cordova, MHM Southern California Edison

Edward Ingram, PM Kellogg

Carroll Crum, MHM Altec Industries, Inc.

Eric Itow, S, HS

Jacob Dauer, S, HS, PS Minnesota West Community & Technical College Edward Day, PS Norgren, Inc

Scott Jackson, PS Parker Hannifin Corporation Chad Johnson, HS Eaton Corporation Thomas Johnson, Jr., MHM Altec Industries, Inc.

Douglas Morrill, PS Norgren, Inc Cody Mouret, PS Norgren, Inc Tim Multerer, HS Haldex Hydraulics Corporation Matthew Nagy, PS Parker Hannifin Corporation Tom Nguyen, PS Norgren, Inc Brian O'Reilly, HS Womack Machine Supply Co. Andrew Paquette, HS

Gregory Jones, PM Kellogg 36 | July/August 2010

Robert Robertson, PS Norgren, Inc Kevin Robinson, HS Progressive Power & Controls, Inc. Brett Ryder, MHM Altec Industries, Inc.

Charles Schulte, ECS Fluid-Tech, LLC

Ryan Vaughn, HS The Knapheide Manufacturing Company Brett Webb, HS Haldex Hydraulics Corporation

Charles Werdehoff, PS Norgren, Inc. Nathan Wilsford, HS Progressive Power & Controls, Inc. Dennis Wilson, PM Kellogg Michael Wilson, PM The Boeing Company

Todd Scott, PS Parker Hannifin Corporation Michael Shimek, PM Kellogg

Hansruedi Wintermuth, PM The Boeing Company Jeff Witucki, HS Force America, Inc.

Jon Siegle, S, HS Hennepin Technical College Alan Skaggs, HS Walt Disney Company

James Word, HS Walt Disney Company Mickey (Michael) Yarger, PM Kellogg

Nicholas Spanhak, PS Parker Hannifin Corporation Charles Stack, PS Norgren, Inc

Ashlee Tyler, S, PS Parker Hannifin Corporation

Rob Weddon, S, PS Kriha Fluid Power

Anthony Hallberg, S, HS

Joseph Herder, S, HS, PS

Andrew Dammann, S, HS

Brett Riske, S, HS Hennepin Technical College

Xiaodong (Alan) Zhao, HS Indalco Alloys, Inc. Jason Ziegler, PS Parker Hannifin Corporation

www.ifps.org | www.fluidpowerjournal.com

IFPS Certification Testing Locations

I

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: July 2010 August 2010 September 2010 Tuesday, 7/6 Tuesday, 8/3 Tuesday, 9/7 Thursday, 7/15 Thursday, 8/19 Thursday, 9/16

October 2010 November 2010 Tuesday, 10/5 Tuesday, 11/2 Thursday, 10/21 Thursday, 11/18

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

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

www.ifps.org | www.fluidpowerjournal.com

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 Wartburg College Waverly, IA Western Iowa Community College Sioux City, IA IDAHO Boise State University Boise, ID Brigham Young University Rexburg, ID College of Southern Idaho Twin Falls, ID Eastern Idaho Technical College Idaho Falls, ID Lewis-Clark State College Lewiston, ID University of Idaho Moscow, ID ILLINOIS College of DuPage Glen Ellyn, IL

INDIANA Indiana Univ. Purdue University Indianapolis, IN Ivy Tech Community College/ Bloomington | Bloomington, IN Ivy Tech Community College/ Columbus | Columbus, IN Ivy Tech Community College/ Evansville | Evansville, IN Ivy Tech Community College/Gary Gary, IN Ivy Tech Community College/ Indianapolis | Indianapolis, IN Ivy Tech Community College/Kokomo Kokomo, IN Ivy Tech Community College/ Lafayette | Lafayette, IN Ivy Tech Community College/ Lawrenceburg | Lawrenceburg, IN Ivy Tech Community College/Madison Madison, IN Ivy Tech Community College/Muncie Muncie, IN 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

July/August 2010 | 37

AssociationNews 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

IFPS | International Fluid Power Society 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

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

Ferris State University Big Rapids, MI

North Carolina Central University Durham, NC

University of Oklahoma Norman, OK

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

38 | July/August 2010

Middle Tennessee State University Murfreesboro, TN

Weber State University Ogden, UT

WISCONSIN Lakeshore Technical College Cleveland, WI

University of Central Oklahoma Edmond, OK

Mercer County Community College West Windsor, NJ

Utah Valley State College Orem, UT

TEXAS Abilene Christian University Abilene, TX

Mount Olive College Mount Olive, NC

Washtenaw Community College Ann Arbor, MI

Salt Lake Community College Salt Lake City, UT

Western Washington University Bellingham, WA

Delta College University Center, MI

Southwestern Michigan College Dowagiac, MI

Davis Applied Technology College Kaysville, UT

Walters State Community College Morristown, TN

Oklahoma State University-Tulsa Tulsa, OK

Gloucester County College Sewell, NJ

Trident Technical College Charleston, SC

UTAH Brigham Young University Provo, UT

South Seattle Community College Seattle, WA

Guilford Technical Community College Jamestown, NC

Schoolcraft College Livonia, MI

Technical College of the Lowcountry Beaufort, SC

Weatherford College Weatherford, TX

The University of Memphis Memphis, TN

MICHIGAN Baker College Online Flint, MI

NEW JERSEY Brookdale Community College Lincroft, NJ

Spartanburg Community College Spartanburg, SC

Victoria College Victoria, TX

Olympic College Bremerton, WA

Oklahoma State University Stillwater, OK

Southeast Community College Lincoln, NE

Piedmont Technical College Greenwood, SC

University of Texas El Paso El Paso, TX

Tennessee State University Nashville, TN

The University of Toledo Toledo, OH

Fayetteville State University Fayetteville, NC

Michigan State University East Lansing, MI

Orangeburg Calhoun Technical College Orangeburg, SC

University of Texas at Arlington Arlington, TX

WASHINGTON Central Washington University Ellensburg, WA

Boston, MA

Macomb Community College Warren, MI

University of Houston Houston, TX

Southern Adventist University Collegedale, TN

The Ohio State University Columbus, OH

OKLAHOMA Northern Oklahoma College Tonkawa, OK

NEBRASKA Bellevue University Bellevue, NE

Midlands Technical College Columbia, SC

TENNESSEE East Tennessee State University Johnson City, TN

NORTH CAROLINA East Carolina University Greenville, NC

Lansing Community College Lansing, MI

Horry-Georgetown Technical College Conway, SC

Franklin University Columbus, OH Rhodes State College Lima, OH

Tyler Jr. College Tyler, TX

University of Texas - Brownsville Brownsville, TX

SOUTH CAROLINA Coastal Carolina University Conway, SC

York Technical College Rock Hill, SC

University of Akron Akron, OH

University of Massachusetts

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

www.ifps.org | www.fluidpowerjournal.com

Classifieds

July/August 2010

Company Page Adaconn......................................................................................28 Adaconn......................................................................................28 Air Logic......................................................................................15 Air Logic......................................................................................29 Atos...............................................................................................9 Attica..................................................................................... 18-19 Attica...........................................................................................15 Clippard.................................................................................... CIV Clippard......................................................................................15 Dynamic Fluid Components......................................................30 European Industrial Products....................................................27 European Industrial Products....................................................15 Flaretite.......................................................................................26 Flaretite.......................................................................................28 Fluid Power Training Institute....................................................33 Gates Corporation..................................................................... CII Gates Corporation......................................................................15 Heinrichs USA LLC.....................................................................26 Hercules Sealing Products.........................................................16 Honor Pumps U.S.A...................................................................23 Honor Pumps U.S.A...................................................................31 Hydraulics International Inc.......................................................35 Hydraulics International Inc.......................................................16 IFPE...............................................................................................5 La-Man Corp...............................................................................16 Lehigh Fluid Power.....................................................................13 Lehigh Fluid Power.....................................................................16 Main Manufacturing Products...................................................16 Main Manufacturing Products...................................................29 Marzocchi Pumps..................................................................... CIII Marzocchi Pumps.......................................................................16 Marzocchi Pumps.......................................................................30 Midwest Instrument....................................................................14 Ogura Industrial Corp.................................................................29 Ogura Industrial Corp.................................................................29 Oil-Rite Corp...............................................................................17 Peninsular Cylinder Co. Inc........................................................22 Peninsular Cylinder Co. Inc........................................................30 Power Valve................................................................................33 Power Valve................................................................................31 Safeway Hydraulics Inc..............................................................28 Simerics......................................................................................17 Simerics........................................................................................7 Spectronics Corp.......................................................................35 Sunfab North America................................................................11 Super Swivels.............................................................................17 Ultra Clean..................................................................................30 Western Fluidyne..........................................................................3 Western Fluidyne........................................................................17 Western Fluidyne........................................................................29 Wilkes & McLean Ltd.................................................................11 Wilkes & McLean Ltd.................................................................30 Yates Industries Inc......................................................................1 Yates Industries Inc....................................................................17 Yates Industries Inc....................................................................28 Youli.............................................................................................13 Youli.............................................................................................31 CIL-MM3 3/17/08 9:27 AM Page Young Powertech.........................................................................6 Young Powertech.......................................................................17

RefuRbished bendeR and flaRe machines pRiced to move!

10 pcs MGW 624 Table bender asseMblies complete with Rolling Stand, ½”, 5/8”, ¾” and 1” Tooling

Olsen MOdel 50 - 37 deGree flarinG Machines Contact Bill Mechanic for details Checker Industrial Ltd. 3345 Wyandotte St. East Windsor, Ontario (519) 258 – 2022

bmechanic@checkerindustrial.com www.checkerindustrial.com

FPJclassified2010:Layout 1 11/11/09 4:18 PM Page

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July/August 2010 | 39

1

Classifieds

July/August 2010

Serious About Surplus!

Fluid Power Executive Recruiters As veteran recruiters who focus in the Fluid Power Industry, we need outstanding professionals to fill opportunities in: -Engineering -Design -Manufacturing -Sales -Marketing

Seriously! We’ll Make You The Best Offer on:

• Hydraulic cylinders, valves, motors & more • PTO shafts, universal joints & gear boxes • Bearings of all kinds, roller chain, sprockets, tires, wheel assemblies, seats, engines, most anything related to lawn & garden and off road Larry Leggett 1-800-800-1810 Ext.3202 Fax: 1-800-800-1811 email: LLeggett@baileynet.com

Contact: Eric C. Bergsman, Sales/Marketing Dave Sevel, Engineering William Radke, Manufacturing/Operations Marvel Consultants, Inc. 28601 Chagrin Blvd., #210, Cleveland, Ohio 44122 www.marvelconsultants.com recruiters@marvelconsultants.com Tel: 216-292-2855, Fax: 216-292-7207

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HYDRAULIC FLANGES and COMPONENTS THE “SPECIAL” YOU WANT IS PROBABLY ON OUR SHELVES MAIN Mfg. Products, Inc. 800.521.7918 fax 810.953.1385 www.MAINMFG.com/fpj

22

Hydradyne Hydraulics LLC www.hydra-dyne.com An ISO Certified Company

Hydraulic Hose and fittings sales positions available With 22 locations in 8 states, Hydradyne Hydraulics is a well-established, respected and growing hydraulics distribution and repair company selling and repairing top branded products.

need a cHange? we Have an opportunity for you!

Opportunities for: Inside sales people or hose technicians/mechanics looking for an opportunity to go into outside sales.

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Or you can use our application found in the employment section of our web site.

40 | July/August 2010

An Equal Opportunity Employer. www.ifps.org | www.fluidpowerjournal.com

If there’s one thing we understand at Marzocchi Pumps USA, it’s that when it comes to your applications, size is everything. That’s why we developed the ALPC1/2 and GHPC1/2 series multiple pumps. Thanks to their reduced axial length, they can fit easily into the most compact spaces. They’re especially ideal for applications that utilize one motor to drive numerous pumps.

Our multiple pumps come in 2 or 3 elements and are available as a fully aluminum pump (ALPC) or with a cast iron flange and cover (GHPC) in a wide range of flange, shaft and port configurations. Try one of our small wonders today.

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For more information, call us at 800-924-5404 or visit www.marzocchipumpsusa.com Request more information at www.fluidpowerjournal.com

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