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Magnetek Receives U. S. Patent for Enrange MHR Radio Controller

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Magnetek Inc. was granted U. S. patent 8554378 for its Enrange MHR radio controller. The controller integrates components of a radio receiver and hydraulic controller into a convenient single unit, reducing costs and conserving space. When packaged with one of the company’s transmitters, it provides a total wireless system for operating mobile equipment.

Ben Stoller, director of radio controls for Menomonee Falls, Wis.-based Magnetek, said, “The MHR controller offers the benefits of both traditional hydraulic controls and radio controls in a single unit, providing mobile operators with a control solution for a variety of applications.”

For more information about Magnetek’s Enrange MHR Radio Controller, visit www.magnetek.com/MHR.


Mulcher’s motor provides performance versatility

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Erskine Attachments’ painstakingly designed offerings tackle debris with ease.

Erskine Attachments builds attachments for skid-steer loaders, compact tractors, and excavators. The firm’s heavy-duty forestry-mulcher attachment cuts, clears, and grinds brush, trees, and other vegetation. The attachment can be used for breaking trails, leveling building sites, and removing storm damage. The mulcher housing contains a 14-in.-diameter, 60-in.-wide rotary drum fitted with 30 double-helix, carbide-tipped steel teeth designed to pull material toward the attachment, where it is shredded.

An early design decision was made to drive the mulcher’s drum with a variable-displacement hydraulic motor to give top performance automatically at both high and low cutting speeds. Erskine wanted a combination of speed and torque that could tackle any situation the mulcher faced in the field. To do this, the machine has to cut lighter material at high speed to boost productivity, without sacrificing high torque at low speed for grinding big trees. The firm selected the Parker Hannifin V14-110 bent-axis motor to meet these challenges.

Connected in an open-loop circuit, this nine-piston motor is housed inside the forestry mulcher structure. A belt sheave, mounted directly on the motor shaft, powers a cogged belt to drive the cutting head. The nine pistons provide high start-up torque and smooth operation. This large-frame motor envelope is robust enough that it doesn’t need an overhung load adapter, simplifying the design considerably. This arrangement worked well through all of Erskine’s early testing — even when the mulcher was heavily abused (abuse testing being part of Erskine’s procedures.)

However, one problem arose. The drum that this motor spins in the mulcher weighs 750 lb. When the skid-steer’s directional valve was centered to stop the motor abruptly, the drum’s inertia produced cavitation. This is bad for any hydraulic motor, but especially so for piston motors, where imploding bubbles can cause severe damage. Different plumbing configurations were tried over several weeks to resolve the problem, but none eliminated the cavitation.

Finally, a forestry-mulcher attachment was sent to Parker Hannifin’s Mobile Systems Team in Elk Grove Village, Ill. This team assists Parker distributors and OEM customers with design and performance problems. Its solution to the cavitation problem was to install an accumulator and then add a special check-valve manifold (mounted on the motor).

The accumulator stores hydraulic energy to ensure the motor inlet is always supplied with pressurized fluid. The check valve directs pressurized fluid to the motor and keeps it from flowing back into the motor supply line. Thus, the system is full of oil under any condition — even while the motor winds down to zero speed when the mulcher is turned off or when the loader’s engine speed drops under a heavy load.

Parker rented a skid steer loader to make sure it duplicated exactly what Erskine’s customers would see out in the field when the mulcher is doing real work. The modified design was a success — the cavitation problem disappeared.

The V14-110 motor has other features that make it attractive to Erskine. The motor shift pressure can easily be adjusted at the Parker Hannifin facility, at Erskine’s plant, or in the field — with just a wrench and screwdriver. The adjustment screw is located under a tamper-resistant plastic cap. (However, users should not change the settings without proper training.)

This adjustment feature allows Erskine to purchase one motor with a preset displacement range and then have it tuned for two different shift pressures dictated by the maximum operating pressure of the loader on which it will work. This adjustability helps the firm maintain a smaller inventory and shorter lead times.

The V14-110’s displacement range (minimum to maximum) can be adjusted, a feature not utilized by this application. Instead, two different-sized sheaves are used to change the speed ratio between the motor and cutting head.

One final plus: Due to the motor’s efficiency, no secondary cooler is needed on the cutting head. Coolers add considerable cost and decrease the overall hydraulic system efficiency.

Shane Voxland, Engineering Manager at Erskine Attachments Inc., Erskine, Minn., described this design evolution. Learn more about the company and its products at www.erskineattachments.com

Loading relief valve meets DIN standard

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Almo Manifold & Tool Co., East Tawas, Mich., offers a slip-in cartridge-style, solenoid-operated loading relief valve that conforms to the DIN 24342 (ISO 7368) standard. The design promises faster response and lower leakage rates than larger conventional spool-type valves. These valves accommodate pressures to 5,000 psi and maximum flow from 50 to more than 700 gpm.

The valve incorporates a single-cavity manifold block (with Code-61 or Code-62 flange mounting) that holds a spring-biased poppet-valve insert. A relief cover that mounts over the block contains an adjustable screw-in cartridge relief valve and a two-position, three-way directional-control valve.

While the solenoid is deenergized, pressure on the bottom surface of the poppet overcomes the spring force at the top. The poppet shifts to open a flow path to tank. Pump flow passes freely with minimal power loss.

To load the system’s pump, the solenoid is energized. Pressure then builds in the manifold chamber above the poppet and combines with the spring force to shift the poppet to its closed position. The cartridge-style relief valve in the cover now takes over to maintain the pressure above the poppet at the relief setting. (Orifices in the cover limit flow to the relatively small relief valve.) Any excess pressure above the poppet exhausts through the cartridge relief.

If system pressure below the poppet exceeds the relief setting, the force it generates overcomes the spring and pressure force above the poppet. The poppet then shifts open again to pass pump flow directly to tank.

For more information call Almo Manifold & Tool at (877) 256-6669, or visit www.almomanifold.com.

∆P gauge quickly spots leakage

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Fluid-power assemblies must be tested for leakage. The three traditional, low-tech approaches for doing so are:

  • Filling the assembly with compressed air, then slopping soapy water on it to see if bubbles reveal leaks.
  • Immersing the whole assembly in a water bath, then pressurizing it with air — again, watching for bubbles.
  • Pressurizing the sealed assembly and watching a gauge for pressure decay.

At best, these methods are cumbersome and time-consuming. At worst, they add drying and corrosion problems. All interrupt production flow. A simple, high-speed leakage test, suitable for production work, can be assembled from a differential-pressure gauge, a pair of two-way valves, and a vessel that is known to be leak-free. The circuit is shown in the accompanying illustration.

With the test assembly in place, valve A is opened to pressurize both volumes. The gauge will read zero. Then valves A and B are closed. Because the reference volume holds pressure, any leakage from the test assembly immediately results in a measurable differential that registers on the gauge.

The leakage rate can be calculated from the formula:

L = (∆P× VS)/(PA× t),

where L = flow, in scfm; ∆P = differential pressure, in psi; VS= assembly volume, in ft3; PA = atmospheric pressure, in psi; and t = time, in minutes.

Joe Gordon, chief engineer, Differential Pressure Plus Inc., Branford, Conn., suggested this test configuration. Call him at (203) 481-2545, or visit www.differentialpressure.com.

A heavy dose of learning

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The IFPE Technical Conference will again be held in conjunction with ConExpo. We present the details about the Conference and other educational opportunities being conducted in Las Vegas only a few weeks from now.

IFPE 2014 will be the place to be to learn about all things fluid power. As they have since 2002, IFPE and ConExpo will be held simultaneously at the Las Vegas Convention Center. This year’s Conference is scheduled for Tuesday, March 4 through Saturday, March 8, with the IFPE Technical Conference running Wednesday, March 5 through Friday, March 7. Conference sessions will be held in the South Hall Bridge meeting Complex.

In addition, 4-hr short courses will be conducted Monday, March 3, and a series of free fluid-power seminars will be conducted Wednesday and Thursday, March 5 and 6.

The IFPE Technical Conference will emphasize new technologies and methods related to improved analysis, design, manufacture, and performance of fluid-power components and systems.

Registration for the IFPE Technical Conference is $85, which includes admission to all technical presentations; two keynote presentations; a flash drive with the Conference; and a certificate for PDH or CEUs.

Following is a summary of sessions. This information is subject to change, so visit www.ifpe.com/Education for the latest details.

Wednesday, March 5

W1 8:45 to 10:15

Modeling: Hybrid (Green), PCB Stability, Controls

  • PCB System Dynamic Stability Utilizing Digital Prototyping
  • Innovative Hybrid Modeling Approach to Enhance Green Design Based on Fully Integrated Mechatronic System
  • Using Simulation to Create Real Efficiency in Hydraulic Control Systems
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W2 8:45 to 10:15

Wireless Technology: Applications, Performance, Safety

  • High-Speed Real-Time Industrial Ethernet Technology Revolutionizes Off-Highway Vehicle Automation Architectures
  • Global Navigation Satellite Systems (GNSS) technologies for Off-Highway Agricultural Vehicles: The Benefits of Using State-of-the-Art Mobile Hydraulics Technology
  • Machine Control with Only Two Hoses

W3 8:45 to 10:15

Controls: Analysis, Performance, Systems

  • Servomotion Control with Custom Feedback Increases Operation Uptime, Reduces Maintenance, and Improves Monitoring of Machine Parameters
  • Practical Solutions for Open Circuit System Instability
  • Hydraulic Steering “Jerk” on Articulated Vehicles

Wednesday 1:00 to 2:00

Keynote Presentation

Energy Consumption in Fluid Power

The Impact and Potential Savings in Mobile Machine Applications - Lonnie Love, Ph.D., Group leader of Oak Ridge National Laboratory’s (ORNL) Automation, Robotics and Manufacturing Group

Fluid power is a foundational technology for both the manufacture and operation of mobile machines. However, there are many areas where fluid power can improve. A recent ORNL/NFPA study suggests that between 2 and 3% of U. S. energy consumption is derived from fluid-power components and systems. Furthermore, the average efficiency of fluid-power systems is approximately 21% — although typically higher in mobile machines. Therefore, moderate improvements in efficiency can yield tremendous energy savings. Emerging trends in advanced manufacturing can simultaneously increase efficiency as well as improve competitiveness. Another challenge is workforce development. How can we inspire youth to consider careers in science and engineering, and become knowledgeable about the potential in fluid power?

W4 10:30 to 12:00

Modeling Pumps for Design and Performance

  • Comparison of Steady-State Flow Loss Models for Axial Piston Pumps
  • On the Hydraulic Pumps Modeling for Applications Engineers
  • Mathematical Modeling and Experimental Research on Influence of Improved Stator Curve on the Characteristic of Vane Pump

 

W5 10:30 to 12: 00

Noise Control: Modeling and In-Line Suppression

  • Prediction of the Acoustic Radiation from a Hydraulic Piston Pump Using Flexible Multibody Dynamics
  • Optimization of Dissimilarly Sized Dual In-Line Suppressors

 

W6 10:30 to 12:00

Hydraulic Energy Storage Methods

  • Fluid Power in Transportation
  • Experimental Studies of Viscous Loss in a Hydraulic Flywheel Accumulator
  • Industrial Application of an Intelligent and Efficient Fluid Power Storage System

 

W7 2:15 to 3:45

New Pump Designs (Digital/Discrete) and Applications

  • Midsize Wind Turbines with Hydraulic Transmissions
  • Applications for Discrete Flow Pumps
  • DHTM475: The Evolution of Flow

 

W8 2:15 to 3:45

  • Using Hydraulics for Tier 4 Off Highway Compliance
  • Engine Overspeed Protection for Tier 4 Machines with Hydrostatic Transmissions
  • Modern Hydrostatic Propel Drives Change Wheeled Off-Road Vehicles

 

W9 2:15 to 3:45

Controls: Analysis, Performance, Systems

  • Coordinating Subsystem to Maximize Efficiency
  • Hydraulic Generator Drive Robust Control
  • Pressure Control in Pulsed Electrohydraulic Forming of Sheet Metal

 

W10 4:00 to 5:00

Novel Methodology for Analysis of Pumps and Motors

  • Equations for New Approach to Fluid-Power Components and Systems
  • A Novel Methodology of Displacement Calculation for the Swash Plate Axial Piston Pump with Angle Cylinder Block

 

W11 4:00 to 5:00

Pneumatics: Reusable Energy, Robotics, Orthotics

  • Heat and Efficiency Considerations in Fluid-Powered Co-Robotics Applications
  • Walking Energy Hydraulic Regeneration Potential to Extend Range of Active Orthotic Exoskeletons

 

W12 4:00 to 5:00

W12 Work/Duty Cycles: Determination and Optimization

  • Establishing an Optimal Work Cycle for an Alternative Wheel Loader Concept
  • Drive Cycle Formation Procedures for Off-Highway Vehicles

 

Thursday, March 6

T1 8:45 to 10:15

Fluid Performance: Temperature, Film Thickness, Base Stock

  • Study of Temperature and Lubricant Effects on the Efficiency of a Complete Hydrostatic-Drive System
  • Effect of Base Stock Type on Film Thickness and Performance in Hydraulic Pumps
  • Hydraulic-Fluid Efficiency Effects in External Gear Pumps

Thursday 1:00 to 2:00

Keynote Presentation

Hydraulic Hybrid Excavator: Customers, Diversity Drives Innovation - Ken Gray, Global Product Manager, Large Hydraulic Excavators, Caterpillar Inc.

The fuel-saving Cat 336E H Hybrid was launched in 2013 as the industry’s first hydraulic hybrid excavator. With over 300 patents filed, the innovative hydraulic hybrid technology is a significant departure from the typical hybrid approach. To accomplish such a feat required an acute, intense focus on the customer and a diverse, global team empowered to drive an innovative solution. Learn the story behind the development of this game-changing product from Caterpillar.

T2 8:45 to 10:15

Modeling: Vane Pumps and Valves

  • A Numerical Model for the Simulation of Flow in Radial Piston Machines
  • New Nonlinear Model for a Four-Way Directional Control Servo or Proportional Valve
  • A Nonlinear Valve Model is Applied to a Highly Overlapped Proportional Valve

 

T3 8:45 to 10:15

Wireless Technology: Application, Performance, and Safety

  • Connecting Your Vehicle to the World
  • Applying Wireless Technology to Electrohydraulics: Architecture, Approval, and Safety Considerations
  • CAN Be Safe

 

T4 10:30 to 12:00

Hydraulic Hybrids: Simulation, Design, Performance

  • Control System Development for a Hydraulic Hybrid Lift Truck
  • Comparison of Two Different Electronic Feedback Methods to Increase the Damping in the Simulation Model of Electrohydraulic Hybrid Actuator System for Off-Highway Working Vehicles

 

T5 10:30 to 12:00

Valves: Modeling, Performance, Contamination

  • Control and Stability Analysis of a Practical Load-Sense Systems
  • Improvements in Controllability and Efficiency of Electronically Controlled Valve Systems
  • Servovalve Design for Faster Response in motion Systems and Also Low Contamination Susceptibility

 

T6 10:30 to 12:00

Fluids: Environment, Performance (Including Hybrids)

  • Environmental Lubricants in the Fluid Power Industry
  • The Effects of Fluid Properties on the Efficiency of Hydraulic Hybrid Vehicles
  • Improving Fuel Efficiency, Productivity and GHG Emissions of Off-Highway Equipment Through the Use of Energy-Efficient Hydraulic Fluids

 

T7 2:15 to 3:45

Hydraulic Hybrids: Energy Recovery and Reuse

  • Towards a New Kind of Energy Recovery for Electric Vehicles
  • Hydraulic Hydrostatic System for Swing Energy Recovery and Reuse
  • Series Hybrid Hydraulic System

 

T8 2:15 to 3:45

Fluids: Filter Testing, Water Monitoring, and Control

  • Got Water?
  • Laboratory and Field Investigations of Water-Adsorbing Oil Filters and Relative Humidity Sensors
  • Impact of the Use of Secondary Particle Counter Calibration Samples on Particle Count and Filter Test Results

 

T9 2:15 to 3:45

Hydraulic Fan Drive Systems: Design and Performance

  • Improvements in Reversing Fan Drives
  • Dedicated Closed-Circuit Hydrostatic Fan Drive Control
  • Open Circuit Fan System Stability Analysis

 

T10 4:00 to 5:00

Valves: Adjustment, Modeling, Empirical Evaluation

  • Methods to Adjust the Characteristic Curves of Electrohydraulic Proportional Valves in Mobile Applications
  • Empirical Method Produces Improved Consistency In Variable-Discharge Coefficient Effects

 

T11 4:00 to 5:00

Test Stands and Procedures:  Airborne Noise and Pneumatics

  • Meeting ISO3744 – Determination of Airborne Noise Generated by Hydrostatic Unit
  • Development of a Portable Pneumatic Educational Tool for STEM Education

 

T12 4:00 to 5:00

Sensors: Thermal Properties and Pressure Ripple Energy for Sensing

  • Applications of Thermal Actuation Technologies within the Fluid-Power Environment
  • Pressure Ripple Energy Harvester Enabling Autonomous Sensing

 

Friday, March 7

F1 8:45 to 10:15

Connectors, Manifolds, Cylinders

• Corrosion Protection Methods for Fluid Connectors

• New Process for Improved Seamless Forged Pipes for Hydraulic Cylinders

• Pressure Ratings and Design Guidelines for Manifold Applications

 

F2 8:45 to 10:15

Pneumatics: Performance, Reusable Energy, Seal Friction

  • Two-Phase Heat Regeneration in Hydraulic Accumulators: Efficiency Improvement at Low Cost
  •  Characteristics of Airflow Control Components for the Emergency Breathing System
  • Pneumatic Lip Seal Friction

 

F3 8:45 to 10:15

Air in Fluids: Effect and Elimination

  • Air Bubble Separation and Elimination from Working Fluids for Performance Improvement of Hydraulic Systems
  • Impact of Gas Cavitation in the Instantaneous Flow Provided by External Gear Pumps

 

F4 10:30 to 12:00

Charge Pump, Reservoir Design, Seal Friction

  • Mobile Equipment Reservoir Baffle Innovation
  • Charge Pump and Loop Flush Sizing for Closed-Loop, One-Pump, Multimotor Systems

 

F5 10:30 to 12:00

Modeling: Valves, Analysis, Performance

  • Modeling, Simulation, and Analysis of a Simple Load-Sense System
  • Improving the Position Control Performance of a Proportional Spool Valve, Using 3D CFD Modeling

 

F6 10:30 to 12:00

New Pump Designs

  • Design of a Variable-Displacement Triplex Pump
  • Experimental Characterization of External Gear Machines with Asymmetric Teeth Profile
  • Using Helical Gear Form to Reduce Ripple and Noise in External Gear Pumps

 

F7 1:00 to 2:00

Improved Quality and Safety, Using FMEA and Component Coding

  • Using System FMEAs to Improve Safety, Quality and Performance in Off-Highway Hydraulic Systems
  • Using 3D Color Coding to Communicate Fluid-Power Designs

 

F8 1:00 to 2:00 p. m.

  • Test Stand Design: High-Bandwidth and Impulse Fatigue
  • Design of a High-Bandwidth, Hydrostatic Absorption Chassis Dynamometer with Electronic Load Control
  • Energy-Efficient Impulse/Fatigue Testing

 

F9 1:00 to 2:00

  • Innovative Applications of Hydrostatics for Small Machines
  • Novel Use of a U-style Hydrostatic Transmission to Develop a Low-Power Dual-Mode Transmission
  •  Hydrostatic Baja Vehicle

Smalley receives GM Supplier Quality Excellence award

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For the second consecutive year, Smalley Steel Ring Company has received General Motor’s GM Supplier Quality Excellence award.  The award honors suppliers that contribute to GM’s goal of providing the best overall customer service in the automotive industry.

“For over 50 Years, Smalley has worked with engineers worldwide to develop space saving Wave Springs and Retaining Rings for the most demanding of applications. Our continuous drive to provide our customers with precision components that meet their needs will allow us to be a partner in their successes.” says George Nisbet, Smalley’s Director of Operations.

Smalley is proud to recieve recognition for its commitment to top-quailty service.

Improving Pneumatic Energy Efficiency

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Following some proven techniques can reduce pneumatic system energy costs by more than one-third.

Reducing energy consumption is a priority in most every manufacturing plant and industrial facility, as no company can afford to throw money away using machines and processes that waste energy. Because pneumatic systems are ubiquitous throughout manufacturing and can account for a large share of a plant’s power costs, it is extremely important that they run efficiently.

Unfortunately, many users have the mindset that pneumatic systems are inherently inefficient, and so overlook opportunities for energy savings. In addition, some manufacturers of industrial equipment and robots tend to focus on ensuring the pneumatic systems perform their intended functions, and in the process neglect efforts to reduce operating costs. These OEMS should instead recognize that plant operators are becoming more concerned with total cost of ownership (TCO), of which energy cost is a major component. These customers know that energy usage can account for up to 75% of machine and robot TCO, and they’re looking to suppliers to help them reduce that bill.

The old business model of only caring about performance and not about efficiency is dying. In the long run, OEMs that include energy efficiency as part of the overall performance of their pneumatic systems will be better positioned to succeed than those that neglect TCO.

Fortunately, both OEMs and users can improve the energy efficiency of pneumatic systems, with tactics that range from better engineering decisions in the design stage to adjustments and maintenance on existing systems.

According to data from the U. S. Department of Energy, manufacturers spend over $5 billion each year on energy for compressed-air systems. By optimizing these systems, companies can reduce their compressed-air energy consumption by anywhere from 20 to 35%. (The DOE offers guidelines for determining the cost of compressed air in a plant, as well as tips on how to reduce compressor energy consumption. Visit www.energystar.gov/buildings/sites/default/uploads/tools/compressed_air1.pdf for more information.)

Right-size components

Correctly sizing pneumatic-system components helps cut costs in several ways, as each component can affect other parts of the system. For example, undersized control valves may initially be cheaper than larger, right-sized units, but they require the air compressor to work harder to get the proper pressure to the actuators.

On the other hand, while some oversizing is necessary to compensate for pressure fluctuations and air losses, grossly oversized components account for one of the biggest energy drains in a pneumatic system. If an engineer simply oversizes from a 2 to 3-in. cylinder, for example, required air volume will more than double. Correctly sizing a cylinder can reduce its air consumption by at least 15%, which becomes even more significant in systems with many cylinders that cycle thousands of times over their operating life.

In general, most loads and speeds require only 25% additional capacity to ensure proper operation. While many calculations and considerations go into right-sizing components (such as whether a load is rolled or lifted), software packages, online calculators, and even iPhone apps can assist with computations. By spending a little more time in the design phase, OEMs can deliver substantial energy savings to their customers.

Right-sizing pneumatic components will not only increase customer satisfaction, it lets OEMs cut their own expenses. Larger and heavier components use more energy and create a larger footprint, which no manufacturer likes, and they cost more up front.

Optimizing pressure

As compressed air flows through typical circuits, air pressure drops due to changes in demand, line and valve-flow resistance, and other factors. But many of these losses are simply because the distance between the compressor or supply point and the actuator is longer than necessary.

Designs that use the shortest tubing possible can reduce energy consumption as well as cycle times. Typically, tubing between control valves and cylinders should be less than 10-ft long. Longer lengths require more pressure so that force, speed, and positioning capabilities aren’t compromised.

Another way to eliminate unnecessary consumption is ensuring actuators use only the pressure needed to perform a task. Sometimes, operators on the plant floor increase supply pressure in the belief that it improves performance. However, all this does is waste energy and money. Installing sensors that monitor pressure, and pressure regulators that maintain correct settings, can keep pressure within the minimum and maximum parameters.

Many engineers also design systems that deliver more pressure than needed to the actuator. Regulators that control pressure to individual pneumatic cylinders will increase energy efficiency, in many instances generating savings of up to 40%.

The same holds for complete machines. OEMs typically design standard equipment to accommodate users who need the highest forces. Adding pressure regulators lets OEMs more accurately size components while still meeting a range of performance requirements.

Don’t overlook the return stroke

Another way to conserve energy is by supplying the correct pressure for an actuator’s return stroke. Most applications only move a load in one direction. However, many machines use the same pressure for both the working and return strokes.

For example, a material-handling system that pushes boxes from one conveyor to another needs high cylinder force only in one direction. The working stroke may demand 100 psi to move a box, but the low-force return stroke only requires 10 psi. Using the same pressure in both directions wastes energy. Reducing the pressure on the return stroke saves 90% of the volume of compressed air. Because that conserves compressed air, a lot of energy is saved over the thousands of cycles that the action is performed.

Another important and often overlooked benefit of regulating air pressure to the minimum required level: It lessens wear and tear on the pneumatic and related components. Not overpressurizing the retract stroke reduces vibrations and shock to the machine. Moreover, adding a quick-exhaust valve can reduce cycle times because exhaust rate on the return stroke affects cylinder speed.

Processes with shorter strokes can use single-acting, spring-return cylinders. A control valve ports compressed air to the cylinder for the working part of the stroke, and then exhausts that air. During the return stroke the spring, or sometimes merely the weight of a mechanism, brings the cylinder back to the starting position.

A typical case where single-acting, spring-return cylinders can reduce energy demand involves presses. In this type of application, a cylinder pushes two items together such as a bearing into a housing, or a plug into a hole. The job demands a significant amount of force to press the parts together, but only a small amount to retract. This makes it a good candidate for energy savings by minimizing return-stroke air consumption.

Turn it off

Shutting down a machine when it’s not working seems like an obvious way to save energy. While some elements of a system, such as air bearings, can require pressure even when the machine is off, the required compressed airflow is usually much less than that needed during normal operations.

However, many installations have no automatic way to reduce or stop airflow to idle machines. Reduced staffing often means that manufacturers can no longer send maintenance workers to manually turn off air to specific machines. In these instances, automatic air-reduction controls will lower air pressure or, if appropriate, shut it off completely when the machine isn’t working, more than paying for itself in short order.

Minimize leaks

Leaks are common and expensive in pneumatics systems. Statistics from the U. S. Department of Energy show the average manufacturing plant loses 30 to 35% of its compressed air due to leakage. The good news is many leaks can be prevented or repaired.

There are many points between the compressor and the load where leaks can be fixed, with valves and seals two main areas for improvement. Deteriorated seals and certain valve designs, such as lapped-spool valves with metal seals, have inherent internal leakage that is constant as long as air is supplied to the valve. Switching to valves with soft seals can significantly lower this leakage.

However, it’s important to note that air consumption in lapped-spool and metal-sleeve valves doesn’t vary during operation. On the other hand, during an open crossover when the valve shifts, a soft seal produces hundreds of times more leakage than a lapped spool-and-sleeve valve. Therefore, selecting the right type of valve for an application can minimize air leakage.

It’s equally important to consider environmental conditions such as temperature and humidity, and type or lack of lubrication, as these all affect the leakage rate of a seal. In some instances, hardy and relatively expensive seals like Viton, Teflon, or polyurethane may be the best option.

Systems approach

Pneumatic systems aren’t quite as simple as they might first appear. The engineering concept of actuating valves and moving loads with air is quite straightforward, but optimizing pneumatic-system designs and maintenance involves many variables.

While operating conditions and component selection are large factors in the general inefficiency of these circuits, pneumatic systems can be greatly improved by implementing the concepts discussed here. OEMs play a big part because much of the energy inefficiency of pneumatic systems can be remedied at the design level. Machine users also have a crucial role to play as they are responsible for the overall operation and maintenance of a plant’s pneumatic system.

In today’s world, users are more aware of how energy consumption affects their bottom line. As such, OEMs must consider their customers’ TCO, not just upfront costs.

For more information, call AutomationDirect at (800) 633-0405 or visit www.automationdirect.com.

Pump placement predicates drive method

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Implementing a hydraulic pump drive—crucial to the layout of on- and off-highway equipment — can take one of several approaches.

Myriad mobile machine functions exploit hydraulics technology, ranging from transit drives and swing functions to boom operation and conveyor drives. All these functions rely on a pump located somewhere in the machine to provide the power needed to accomplish the intended work. The pump’s placement within the system depends on the availability of a mechanical rotational power source to drive the pump’s input shaft (Figure 1).

Two separate base-type applications, on and off-highway, offer opportunities and distinct ways for pump-mounting locations and drive inputs. Many options are available, but keep in mind that one input isn’t preferred over another. Usually, the design envelope within which the drive designer must physically fit the pump eliminates some options — maybe even all but one. This makes it important to understand the pros and cons of each input type. 

On-Highway Equipment

On-highway applications — such as concrete-mixer trucks, truck-mounted cranes, and dump beds — rely on traditional mechanical transmissions to move the vehicle. Few options exist to provide the rotational power for these vehicles’ onboard hydraulic pumps.

The hydraulic pump typically is mounted on the side of a transmission-integrated power take-off (PTO). A PTO represents any of several methods that takes power from a power source (such as a running engine) and transmits it to an implement. The most common version involves a splined output shaft that allows easy connection and disconnection of the pump’s input shaft.

In the splined output shaft setup, the PTO is engaged and disengaged via the truck’s pneumatic system. Typically, little space lies between the PTO and the transmission axle, which brings the size and shape of the pump into play. A large displacement pump may be too wide or long for using this input area (because of interference from the axle). Therefore, it’s important to research the pump manufacturer’s options for mounting requirements.

Many pump manufacturers, such as Bosch Rexroth, offer compact pump-mounting flange options or bent-axis pumps (Figure 2) that provide more clearance around the axle. Bent-axis pumps contain pistons mounted at an angle to a driveshaft, which rotates the pistons. This angle, typically around 25°, produces a compact mounting area that maintains a wide range of displacement.

Auxiliary engines (in addition to the main vehicle engine) often reside in truck-mounted applications that require full-engine power and torque. Applications such as large vacuum pumps typically use this method. In these cases, multiple pumps can populate a multipad gearbox that’s driven directly by the auxiliary engine’s output shaft. Beyond carrying multiple pumps, this configuration offers potentially greater flexibility in terms of pump size. Here, it’s important to ensure adequate power is available to the hydraulic pump to meet the performance needs of the function being controlled. 

Off-Highway Equipment

Comparing on and off-highway equipment requires understanding the base design principles for each type of machine. On-highway systems usually use a conventional mechanical drivetrain, whereas off-highway equipment typically does not follow a preexisting drive chassis. Instead, it targets a specific machine purpose or activity. In these cases, designers are able to work with a blank canvas to provide rotational power from a hydrostatic transmission. Such applications usually include certain options: engine bell-housing coupling, engine crankshaft, belt/pulley, single or multipad PTOs, and pumps with built-in through drives. As with on-highway applications, no single method is better than another. Rather, each has characteristics that make it most suitable for certain configurations.

Some pump manufacturers offer bell-housing mounts for their pumps, which enable direct coupling to the diesel engine. Most of pumps driven in this manner — such as the Bosch Rexroth A11VO and A8VO (Figure 3) — are rated for high pressure. One key benefit is that they save space upon installation. Applications usually involve machines that use the hydraulic system as their only means of power for propulsion and to perform work — excavators and feller bunchers, for example. The engine power need not drive an axle, mechanical transmission, or Cardan shaft, thus conserving space.

Many times, however, space restrictions require the pump to be located away from the engine. In these instances, an engine crankshaft can couple the pump to the mechanical drive of the engine. For this type of mounting/coupling, the angle and balance of the connection method to the pump should be monitored to avoid undesired bending forces of the pump’s input shaft. It must be parallel to the engine’s crank shaft; otherwise, it will introduce oscillation to the pump drive speed that can eventually destroy the pump. It’s best to consult the pump manufacturer for the amount of allowable bending and axial forces that can be accommodated by the pump or find ways to avoid derating the pump.

Belt and pulley systems, an alternative to PTO-driven methods, are typically used when there’s obstructed access to the engine PTO or limited area around the engine. Design considerations for this type of input include the amount of power that the mechanical belt drive can transmit to the pump, and monitoring the bending moments with axial and radial loads on the input shaft. These conditions usually limit the maximum possible power transmission and, therefore, pump size.

Space Constraints

The limited space available for a single PTO from a standard engine can complicate hydraulic-pump installation. Depending on the desired pump displacement, the space required to install the pump may prevent easy mounting to the engine PTO. As a result, the manufacturer may need to use spacers or other costly add-ons to mount larger displacement pumps. Once again, it’s best to consult the pump supplier regarding space-saving options for larger displacements.

An example of a potential solution comes in the form of Bosch Rexroth’s A10VNO medium-pressure open-loop pump. The compact unit can fit into small spaces that require high displacement. Another alternative is to use two smaller pumps in a tandem/through-drive package. When combined, they’re smaller in diameter than a single, larger pump, but considerably longer.

To achieve greater flexibility in multipump applications, however, designers may consider multipad PTOs. If multiple pumps need to operate at different input speeds, a multipad PTO will provide different output speeds by changing each pad’s internal gear ratios.

Multiple pumps also can be driven by a pump’s through-drive. Most axial-piston pumps offer a through-drive option that contains a rear output shaft for driving a second pump. To accommodate different mounting flanges, through drives come in a variety of sizes — such as SAE, A, B, C, or other standards. This method can create many different combinations, but you must consider the available maximum torque levels each pump or through-drive can provide to each subsequently mounted pump. Other considerations include maximum limitations of the pump stack’s bending moments, weights, length (long assemblies may require mechanical support at the back end) and available torque limitations at each pad. 

Other Factors Influence Input Choice

Even with the cases mentioned, other elements of the machine’s design should be considered when determining the hydraulic pump’s input method. For one, there’s the impact of Tier IV final emissions on machine design. Additional engine-exhaust-treatment components will occupy more engine compartment space on mobile equipment. This presents new challenges because more pumps with higher power density will be required due to space limitations. These power-dense pumps may operate at higher pressures, which could alter how the pump should be driven within the system.

Moreover, the upcoming Tier IV final engines generate a more demanding torque-ripple effect. Pumps used on direct engine drives and PTOs will be subject to higher angular acceleration fluctuation of their input shaft. Most pump manufacturers publish angular acceleration limits for input speeds.

Jay Edwards is Sales Manager, Agri/Forestry Machines, Bosch Rexroth Corp., Fountain Inn, S.C. Contact him at (864) 228-3011, or visit www.boschrexroth-us.com.


January 2014 Hydraulics & Pneumatics

Parallel pneumatic gripper

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Series GRH parallel pneumatic grippers provide long jaw travel while accommodating long tooling lengths. Available in four sizes, the grippers have an extended support guide system with wide slot jaws to minimize tooling deflection, support large moment capacities, and provide side-load stability. A dual bore provides higher total grip force, and low breakaway pressure allows for gripping of a wide variety of part sizes, including delicate parts. Jaw travels up to 125 mm (4.921 in.) for gripping larger and multiple-sized parts.

PHD Inc., (800) 624-8511, www.phdinc.com/grh

Reasons to Replace PTFE Lined Bushings

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Sponsored by igus

Often times high-performance plastic bushings are confused with PTFE-lined, metal-backed bushings, which are a much older technology. Here are the top four reasons for replacing PTFE-lined bushings with plastic bushings, which offer more design flexibility. Learn more in this technical article from igus®.


Wear Capabilities and Limits of Plain Bearings

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Sponsored by igus

Did you know that plastic bearings cost and weigh less than their metal counterparts? And that they often run longer in harsh environments and under adverse conditions? Learn more from igus® about how plastic bearings outperform metal, their predictable lifetime and common misconceptions in this informative guide.


Parallel pneumatic gripper

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Series GRH parallel pneumatic grippers provide long jaw travel while accommodating long tooling lengths. Available in four sizes, the grippers have an extended support guide system with wide slot jaws to minimize tooling deflection, support large moment capacities, and provide side-load stability. A dual bore provides higher total grip force, and low breakaway pressure allows for gripping of a wide variety of part sizes, including delicate parts. Jaw travels up to 125 mm (4.921 in.) for gripping larger and multiple-sized parts.

PHD Inc., (800) 624-8511, www.phdinc.com/grh

Production boost causes seal leak

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An original-equipment manufacturer of custom automation equipment for the food-processing industry built a large pallet-transfer system to shuttle bins of poultry from a defeathering line to a final processing line. The poultry was placed into bins, 10 at a time, and the bins were stacked 10 high. The 10-high pallet-transfer system consisted of a floor-mounted rack-and-pinion drive system with a gerotor motor driving the pinion to move the pallets. The pallets were then shuttled to one of three locations to be off-loaded for final processing.

An optical encoder provided position feedback to the machine’s motion controller. The motion controller commanded an electrohydraulic proportional valve to drive the hydraulic motor’s motion accurately — to within ±½ in., in front of the correct off-loading point.

The OEM overcame the normal struggle of meeting the cycle time to provide smooth acceleration, deceleration, and positioning of the pallets. The system was tested on the OEM’s shop floor, then installed and commissioned at the poultry plant. Several months of smooth poultry operation ensued.

As usual, a call came in for increased cycle time and higher throughput. The bins were modified to accept 15 poultry bodies, and the original pressures on the system were raised to accommodate the 50% increase in load. The system pressure was raised to 1,800 psi and the cross-port reliefs to 2,200 psi. After a couple weeks, the shaft seal on the motor developed a leak. The motor, rated for 2,500 psi, was replaced. However, the new motor also developed a shaft seal leak in short order.

The motors were disassembled, but technicians found no indication of any internal damage. In fact, the motor manufacturer said they looked brand new and that internal components met
factory-new tolerances. With the rack-and-pinion design, side loading seemed to be the only possible cause for the leakage, so an overhung load adapter was installed to eliminate any side load being transmitted to the hydraulic motor’s shaft. This did nothing except allow the leakage to collect between the adapter and motor.

What do think was the problem?

Click here for solution to problem

Solution to Production Boost Causes Seal Leak:

Gerotor style motors generally do not use an external case drain for pressures lower than 1,500 psi or in non-shock loaded applications. otherwise the shaft seals experience short life. CFC's Jon Rhodes had the maintenance crew connect a case drain line from pump to tank, which solved the problem.

We always use a case drain where ever we can, regardless of the operating pressure. Shaft seal leakage is the major reason why gerotor motors are removed from service. One manufacturer claims that installing a case drain on its motors virtually eliminates shaft seal leaks. Case drains are also great to determine if a motor is worn internally by measuring leakage with the motor running at full load.

Way Too Frigid

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WTF! Way Too Frigid. Another acronym using these same letters would also describe our recent weather, but this is a family blog. This winter is one the entire continent has been touched by, and even normally mild southern states have not been spared the wrath of arctic vortices, a word I hadn’t heard until it became appropriate to describe this year's weather in a unique way … and I’m Canadian!

Hydraulics and pneumatics don’t like ridiculously cold weather. Mobile machines using both hydraulic and pneumatic actuators are especially susceptible to the side effects of tundra temperatures. The reasons hydraulics don’t work well in the cold are different from the reasons for pneumatics, but as long as some foresight is applied, you should be okay.

Hydraulic fluid is the most critical aspect to consider, ensuring your machine will operate – and just as importantly; start working – when it drops to twenty below. A high quality multi-grade fluid with high viscosity index is important even in temperate climes, but unless the components and plumbing on your machine are significantly oversized, it won’t be enough.

Crazy cold requires a crazy hydraulic fluid, and the market has recognized this. Most hydraulic oil manufacturers offer some sort of “arctic blue” type fluid which starts out with a low weight (think like, 12 cSt), and also has impressive viscosity index (the index to reflect an oil’s ability to maintain its test viscosity over extreme cold and heat). This type of oil will prevent the need to start and run machines while they heat up, which wastes both time and money. It should be considered, however, arctic oil may not be the best oil when things get hot, so a summer change-out may be required.

Although air doesn’t freeze, one of the properties of air requires us to think twice. Air contains some water in the form of humidity. Just like humid air can freeze on your windshield, requiring you to risk frostbite to scrap it off, so too the humidity can freeze inside of a pneumatic circuit. It can also pool up as water during operation, and then freeze when the machine is shut down. Frozen water can damage seals or other soft parts of a pneumatic system, but at best, it will block the air line, often requiring cycling to heat the blockage or push it out.

Freezing can be prevented, of course, with air dryers. Dryers can reduce the humidity of the compressed air, and are common in industrial applications, but less so in mobile applications. Sophisticated electric dryers aren’t required, but an inline desiccant dryer will do the trick. Additionally, air filters are often available with water separators, a great last line of defence to liquid water.

If all else fails, and your mobile machine is simply frozen, just take the day off and curl up with an old issue of Hydraulics & Pneumatics. 


Prince Series Cylinders

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Introducing the Prince standard stocked series tie-rod cylinders. This product line is rated at 3000 psi, comes with Royal Plate Plus rod that is warranted against rust and corrosion for 7 years, and we stock many different configurations. Come visit us and check out our offering.

Prince Manufacturing
www.PrinceSeriesCylinders.com

Temposonics® MH-Series Sensors Enable the Next Generation of Vehicle Steering Systems

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Sponsored by MTS Sensors

In the past few years, the agricultural industry has gained new tools that, even 20 years ago, would have seemed more like scenes from a science fiction movie than something found in the field. GPS-guided agricultural equipment has quickly become the gold standard in large crop harvesting operations. These applications use real-time communication with satellites in geosynchronous orbit to guide equipment along extremely precise paths. Download this white paper to learn how MTS Sensors enables the next generation of vehicle steering systems and meets the application’s needs.


Rightsize your electric motors

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Here’s a straightforward approach for matching the size of the electric motor to that of the hydraulic pump.

Contrary to popular opinion, bigger is not always better. A case in point is the electric motor. Pump users tend to want a little extra power, “just in case.” That’s why automobile manufacturers can still sell cars with 300 hp engines, when the speed limit may be less than 70 miles per hour. But, like those gas-guzzlers, oversized electric motors cost more to run — sometimes a lot more. In addi- tion to wasting energy, they often trigger expensive demand charges on utility bills due to low power factor.

Fortunately, it’s easy to determine how much power a pump load requires — without expensive equipment or engineering expertise. In collecting the data, just make sure the pump motor is operating at peak continuous load.

What load is on the pump motor?

The illustration on the next page shows the essentially linear relationship between percent load and current from no-load current to nameplate currentof a pump motor. Notice, though, that zero load does not equal zero current. As- suming it does equal zero will cause mistakes in determining the required power, with the error inversely proportional to the load. That means that the biggest errors will occur when evaluating motors most in need of being matched to the pump load.

Although the percent load a motor carries could be determined from a graph, it is easy (and more accurate) to calculate the actual load using the following equation:

hpr =hpn (1–FLAa–FLAnl)

where hpr is required power in hp,

hpn is nameplate power in hp,

FLAais actual current draw in amperes, and

FLAnlis current drawn at no load in amperes.

To obtain good input data, run the motor uncoupled at no load and measure the current with a clamp-on ammeter. Don’t take any shortcuts here. The no-load current will be higher if the motor is coupled than if uncoupled. Even though the driven equipment (pump) might not be doing any work, some power is required to overcome friction in driving it. To avoid errors, use the uncoupled current.

Next, document the nameplate current and the current at the motor’s actual load. Because an undersized motor presents other problems, the safest method is to measure the current over the entire cycle of operation. If the load is seasonal, record the current during peak load.

A realistic example

It’s not hard to find oversized motors in industry. In one case, a plant had a 40-hp motor driving a hydraulic pump for a molding ma- chine. The motor had a nameplate current rating of 50 A and drew 15 A when operating uncoupled — slightly more than one-third of full- load current. When driving its peak load, it drew 37 A. A quick calcula- tion reveals that the actual peak load was just over 25 hp:

                       hpr= 40 [1–(50–37)/(50–15)]

hpr= 25.1 hp

Substituting the 40-hp motor with a 25-hp one decreased full- load current from 37 A to 30 A. The plant had been paying for, and wasting, a lot of electricity.

How much does the safety margin cost?

Is it better to oversize the motor for a little extra power, “just in case?” Consider this. Utilities often impose demand charges for poor power factor when a motor is seri- ously under-utilized. They also may subject cyclical power users to demand charges based on peak usage. The way it usually works is that one episode of high usage raises the kW/hr cost of electricity for the entire billing period. This imposes severe penalties for start- ing large motors across the line. Identifying oversized motors can help many users reduce peak demand charges.

The letter designations for locked- rotor kV•A / hp as measured at full voltage and rated frequency are shown in the table. To calculate the range of inrush current (locked rotor amps) for a motor, determine its NEMA code letter from the name- plate and solve the following equa- tion for the corresponding kVA/hp values shown in the table:

CLR= CL x hp x 1000/(1.732 x V)

where CLR is locked-rotor current,

CL is kVA/hp from the table,

hp is the motor horsepower, and

V is the voltage.

For a 40-hp motor with letter G designation (5.6 - 6.3 kVA/hp), the locked-rotor current will be 281 to 316 A:

CLR= 5.6 x 40 x 1000/(1.732 x 460)

= 281 A

CLR= 6.3 x 40 x 1000/(1.732 x 460)

=316 A

Based on the previous example, substituting a 25-hp replacement motor (code letter F) for the over- sized 40-hp model not only decreases full-load current from 37 to 30 A, but also drops starting current from 299 to 188 A. These factors help reduce wear and tear on motor starters, contacts, and other parts from unnecessarily high in- rush currents. The substitution also improves power factor appreciably.

Power factor and efficiency

Power factor goes hand-in-hand with efficiency, so it’s no surprise that the power factor for the 3-phase, 40 hp motor in our example is 0.76 when driving the 25.1 hp load:

E= Wout/Win

= 746 x hp/(1.732 x V x A x PF)

=746 x 25.1/(1.732 x 460 x 37 x 0.76)

=18,725/22,404

=0.836, or 83.6% efficiency

By comparison, the replace- ment 25-hp motor operates very efficiently:

E= 746 x hp/(1.732 x V x a x PF)

=746 x 25.1/(1.732 x 460 x 30 x 0.84)

=18,725/20,077

=0.933, or 93.3% efficiency

The power factor can be measured directly with a power factor meter. If a power factor meter is not available, but a watt meter is, the following equation can be used to calculate the power factor of a 3-phase motor:

PF= Win/V-ain

=22404/(1.732 x 460 x 37

= 22404/29479

=0.76

The original 40-hp motor was operating at only about 84% efficiency — nearly 10% below the 93% efficiency of the correctly sized premium-efficient replacement motor. According to the MotorMasterPlus software available from the U.S. Department of Energy (DOE), if the motor operated 8760 hr/yr (that’s 24/7), the original motor would have used more than 196,000 kW•hr per year, versus 176,000 kW•hr/yr for the 25-hp premium efficient model. At $0.07/kWh, that’s a savings of more $1400/yr, every year. Where do you want to spend your money?

Thomas H. Bishop, P.E., is a technical support specialist with the Electrical Apparatus Service Association (EASA), St. Louis, an international trade association of more than 2400 firms that sell and service electrical, electronic, and mechanical apparatus. Call EASA at (314) 993-2220; or visit www.easa.com.

 

 

 

All-Star Lineup of speakers slated for IFK conference

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The 9th Annual IFK will be held in Aachen, Germany, and will feature a diverse range of topics in hydraulic and pneumatic drives and control systems, as well as lectures, excursions, and cultural programs.

The IFK conference happens every two years, alternatively hosted by the Institute for Fluid Power Drive and Controls (IFAS) at RWTH Aachen University and the Institute of Fluid Power (IFD) at the Technical University of Dresden. In addition to being presented all in English, an important feature of this year’s event will be its Digital Fluid Power Workshop, to take place Monday, March 24. This symposium will give researchers from universities the opportunity to present their ideas to various people within the international technical community. The next two days will consist of various lectures, with a scientific poster session throughout. Details can be found at bit.ly/1g3HXRU.

The conference categories include:

Simulation and Validation — Efficient Simulation, Transmission Line Models, New Approaches and Methods, Improved Systems Response through Simulation

Mobile Applications — Mobile Hydraulics, Pneumatics, Aerospace

System — Plug & Play Hydraulics, Digital Hydraulics, Methods for System Analysis, Servo Hydraulics and Pneumatics, Control Systems, Reliability and Robustness

Automotive Technology — Drive Trains, Steering, Comfort, Suspension, Engine Management, Utility Vehicles

Renewable Energy — Wave Energy Converter, Tidal Power Plants, Wind Energy Plants, Energy Storage, Solar Power

Energy Management — Hybrid Drives, Storage Concepts, Control Strategies, New Applications, Energy Recuperation

New Applications — Control Systems, Custom Applications, Rare Materials Production, Injection Systems, Water Hydraulics, Biomedical Applications, Corrosive Fluids

Materials and Fluids — Alternative Fluids, Plastics in Hydraulics, Measurement of Air Content in Fluids, Fluid-Material Compatibility, Oil Maintenance and Mixture Problems, Effect of Environmentally Friendly Fluids on Efficiency

Components — Displacement Units, Production-Oriented Components, Functional Safety, Tank Design, Valves, Resource-Conserving Production, High Speed Rotary Drives, High Pressure Hydraulics, Actuators, Filter Technology, Sensors, Noise Reduction of Hydraulic Equipment 

Pneumatics — Pneumatic Drives, New Drive Concepts, Efficient Systems Design, Vacuum Technology, Miniature Pneumatics, Low-Emission Pneumatics

Condition Monitoring and Diagnosis — Particle Detection, Wear Indication, Effect of Wear on Systems, Fail-Safe Components, Aging Models

With so much to cover, four lecturers will focus on themes drawn from their own professional experience.

  • Head of Corporate Research and Technology at Festo AG & Co. KG, Dr. Peter Post, will present “Smart Pneumatics for Intelligent Manufacturing.”
  • Dr. Win Rampen, founder and Research Director of Artemis Intelligent Power Limited, will present “The Development of Digital Displacement Hydraulics for Renewable Energy Drivetrains (or Necessity is the Mother of Invention!).”
  • Director of Innas B.V., Dr. Peter Achten, will discuss “Innovation in The Fluid Power Industry”.
  • Director of IFAS, RWTH Aachen University, and host of the conference, Dr. Hubertus Murrenhoff will discuss “An Overview of Energy Saving Architectures for Mobile Applications”

All four programs will be presented on March 25. 

Additionally, different excursions and cultural programs will be offered to those who wish to see a bit more of the historic city. A two-day plant-tour trip will be offered March 27 and 28, with partakers visiting Veltin Arena in Gelsenkirchen, Ford Fiesta and Fusion Factory in Cologne-Niehl, and Zollverein Unesco World Heritage—the worlds’ most beautiful coal mine. Three social events will also be held: opening evening on March 24; conference banquet on March 25; and laboratory party on March 26. A full conference schedule can be seen at bit.ly/1enFLzA.

Sun Hydraulics Introduces Sun QuickDesign, Automated Manifold Design Tool

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Sun Hydraulics, Sarasota, Fla., a manufacturer of hydraulic cartridge valves, now offers Sun QuickDesign — a free, Web-based tool that creates custom manifold designs without having to download software. The tool is complete with manifold drawings, drill lists, connection lists, and 2D/3D CAD files. It works with circuits containing up to 12 cartridges and allows you to select the faces you want to place features and components on. Additionally, it offers the benefits of an integrated package. After the user designs a product, cost-saving incentives to ordering are offered. The Sun QuickDesign tool also generates a single part number, which simplifies ordering tracking, and future needs.

Signing up is easy; only a username and password are required to access the automated tool. User activities will be visible to the local Sun distributors so they can assist you with questions, selection, and ordering.

For more information, go to www.sunhydraulics.com/quickdesign or visit Sun Hydraulics at IFPE ConExpo/ConAgg Booth S-80719.

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