Showing posts with label Technical. Show all posts
Showing posts with label Technical. Show all posts

Tuesday, 23 July 2013

Understanding Pump Curves # 3, Centrifugal Pumps in parallel

By Ron Astall, Union Pumps Australia

Centrifugal pumps are frequently operated in parallel to achieve higher system flows, to enhance system flexibility or to provide greater pump redundancy and hence better system availability.  For very large projects, limited availability of sufficiently large pumps or limits on driver size or electrical starting current may dictate the use of multiple pumps. There are traps for the unwary.  Simply running an additional pump in parallel may not provide the expected results.

In our last article Stable & Unstable Curves, we looked at what makes a centrifugal pump curve "stable or "unstable". We also discussed the importance of understanding your system and, in particular, how the system will only operate where the pump curve intersects the system curve, and the differences between "steep" system curves and "flat" system curves. These preceding concepts are absolutely crucial to understanding many of the issues associated with operating pumps in parallel.

To begin, we will define parallel operation and outline how to predict system performance when two or more pumps are operated in parallel. We will discuss selection rules for parallel operation and then look at how different system characteristics react to parallel pump operation.

Parallel operation
"Parallel" operation means that two or more pumps are operating with common inlet and outlet systems. This means that each pump will have the same differential head. The total flow is the sum of the individual pump flows. See Fig 1.

Predicting performance
To predict the system performance, a combined curve for all pumps can be produced by adding the individual flows from each pump curve at a common head. This is illustrated in Fig 2 below :
As with any pumping system, the system will operate where the combined curve intersects the system curve.

In this example, the Pump curves used are not identical and this highlights a likely serious operating problem. Because Pump 'A' has a higher head at zero flow, this pump will overpower Pump 'B' at low system flows. This is highlighted in Fig 3.

In this scenario, the pump with the lower head will be stalled, and assuming that a non return valve has been fitted, it will be running at closed valve with all the attendant risks and damage.

Matching pump curves for parallel operation – selection rules
The primary concern when running centrifugal pumps together in parallel is that pumps share the load safely at lower flows.

This does not mean that pumps must have identical characteristics. Groups of low flow pumps and high flow pumps are often operated together in parallel to match variable system demand. The aim is that all pumps have matching heads at low flow to prevent pumps being stalled or blocked in by the others.

  1. It is most important that the zero flow or "shut valve" heads are matched for pumps that will operate together in parallel.
  2. Unstable pump curves must be avoided for parallel operation, particularly where there is any chance of operation anywhere near their point of instability. Unstable pump curves present a very real risk of surging when operating in parallel.
  3. Steeper pump curves are preferred for parallel operation to assist with load sharing at low flows. Pump curves that are very flat at low flow are prone to wide flow variations with minor changes in head and may make load sharing difficult. See Fig 4.

4. Be aware of minor performance variations that may change the suitability of otherwise well matched pumps. If one pump has had more use and is worn, its curve may no longer match the other pumps. Pumps using different drivers such as a steam turbine driven pump operating in parallel with an electric motor driven unit may operate at sufficiently different speeds to cause mismatch of pump curves at low flow.

Will parallel operation suit your system?
This depends on what you are trying to achieve.

If the aim is to increase and decrease system flow by operating one, two or more pumps in parallel to meet changing demand then it is important to understand the type and limitations of your system.

If your system curve is relatively "flat"; ie. mostly static difference in levels and minimal pipe friction, then operating pumps in parallel will provide a useful performance variation.

If your system is mostly friction resistance (a steep system curve) such as a closed loop circuit or a lengthy pipeline, then performance variation will be minimal. This may be a good or a bad thing depending on what you are trying to achieve.

Flat system curves
Refer Fig 5.
When the system resistance is relatively flat (not much friction), operating additional pumps in parallel will produce a useful flow increase. Incorrectly, many operators expect that flow will double if two pumps are running in parallel. This cannot happen because, when added together, the combined pump curve intersects the system curve at a higher head due to increased frictional resistance and hence each pump will be operating at a higher head and lower individual flow than when operating alone.

Steep system curves
Refer Fig 6.
When the system curve is steep (mostly friction) this steep increase in friction head as system flow increases, means that each pump will be running at a significantly higher head and the individual pump flows will be much less than in single operation. Overall, the change in flow will be small when additional pumps are switched on.

This may be frustrating if you want to increase or vary system flow by switching pumps on and off.

Conversely, this particular aspect of steep systems; such as long pipelines and closed loop recirculating systems; is very useful to pump users that need to maximise system reliability.

These users will often specify multiple combinations of pumps operating in parallel to minimise system disruption in the event of a pump failure.

Typically, in critical applications such as cooling water circuits, three pumps may be installed with the normal operating mode being two running in parallel and the third being a standby unit. If it becomes necessary to shut one of the operating pumps down, the remaining operating pump will still provide a high percentage of the system flow until the standby pump can be started.

Is parallel operation good for you?
Installing pumps to operate in parallel can be an excellent strategy.

It is however very important to understand the aim of the exercise.

Parallel pump installations are a great idea in the following circumstances:

  1. Where limited availability of sufficiently large pumps or limits on driver size or electrical starting current dictate the use of multiple pumps.
  2. When flow needs to be varied according to varying system demand and when the system resistance characteristic is reasonably "flat".
  3. Where the use of multiple combinations of pumps operating in parallel in a "steep" system resistance will minimise potential system disruption in the event of a pump failure.

Remember:

  1. It is most important that the zero flow or "shut valve" heads are matched for pumps that are to operate together in parallel.
  2. Unstable pump curves must be avoided for parallel operation.
  3. Steeper pump curves are preferred for parallel operation.
  4. Be aware of minor performance variations that may change the suitability of otherwise well matched pumps.

Most important of all; understand your system.


Sunday, 21 July 2013

Ceramic lined materials


Ceramic lined materials provide the extra protection of ceramic, which is particularly effective in applications requiring impact and sliding abrasion resistance. These ensure wear-resistant ceramic cylinders to resilient rubber or urethane, to create tough, durable lining systems that extend wear life on your production line, while reducing maintenance and downtime. Well-suited to the rigors of crushed rock, mineral concentrates, and other abrasive materials, the lining systems are ideal for heavy-wear and impact applications.

General features:

  • High pressure and heat during the vulcanizing process creates an incredible bond between rubber and ceramic.
  • Ceramics will stay in place until completely worn.
  • Thickness and formulation can very to create a custom system for your installation.
  • Urethane/Ceramic liners can be an alternative solution in applications where chemicals in contact with liners can adversely affect rubber compounds.
  • Can be engineered to change size, placement, and spacing of ceramic cylinders to meet the right impact level and abrasion resistance for your particular application.

-Ceramic is good for sliding abrasion

-Rubber is excellent for impact abrasion

-The combination is ideal for sliding/impact abrasions




Abrasion-resistant Coatings

Abrasion-resistant Coatings help to avoid the wearing away of parts and equipment due to mechanical or contact related forces. Abrasion, also known as grinding or wearing away due to friction, is a factor on any industrial part, no matter the hardness. Abrasion resistant coatings help to minimize the effect of friction on the outer surface of metal parts. These offer four different options for your abrasion restant coating solutions: With the help of abrasion resistant coatings, hardness is only the beginning. Each of its four options help components maintain more conformity with specified dimensional tolerances, while maintaining a profitable mix between bond strength, coverage reliability, dimensional stability and cost effectiveness.

Conventional abrasion-resistant coatings often feature metal oxide particles incorporated within the resin film to suppress marring, scratching or abrading of the coating. Alumina is the preferred oxide for this purpose due to its extreme hardness (9 on the Mohs scale), and relatively low cost. The drawback to such alumina-containing films is that, although the abrasion resistance is often improved, the transparency of the coating is compromised due to the light scattering of the micron-sized alumina particles used.

However, the use of nanometer-sized alumina in such coatings offers a solution to this problem since the particles are less than 100 nm in diameter, and thereby greatly reduces haze from light scattering. In addition, the alumina particles produced in the PVS process are spherical, which, combined with their small and uniform size, yields a more even film surface to further enhance the scratch resistance of the coating.

The abrasion resistance properties of nanocrystalline alumina were evaluated by incorporating the particles in a crosslinked melamine-formaldehyde resin. Because melamine-formaldehyde resins are transparent and very hard, they are often used as protective coatings on non-flexible surfaces such as furniture and flooring. The alumina was first dispersed in water to disrupt the loose powder agglomerates, and then surface treated to attach functional groups to the oxide surface. The surface functionalization process was designed to prevent particle agglomeration during the film curing process.

A TEM image of the coated alumina particles is shown in Figure 1. As the image shows, the spherical alumina particles are each coated with a thin uniform layer approximately 0.5-1 nm thick. The coated alumina particles were blended with the aqueous melamine-formaldehyde resin system at the desired concentration, from which films were drawn down on glass substrates at 1 mil thickness and cured by heating at 150oC for 15 minutes. The cured film thickness was 9.6 mm.



Saturday, 20 July 2013

Mouvex Eccentric Disc Pump


Mouvex's A Series eccentric disc pumps have incorporated a variety of upgrades to meet growing global demand, including the implementation of ISO PN16/ANSI 150 flanges. The A Series has also doubled its maximum differential pressure from 5 bar (72 psi) to 10 bar (145 psi), enabling it to be used in the safe transfer of viscous, non-lubricating, volatile or delicate fluids in a variety of new applications. The Mouvex A Series, previously available in cast iron construction, is now available in ductile iron construction—an upgrade suited for companies in the petrochemical industry, for example, who are integrating ductile iron systems into their processes. The upgraded A Series also features the availability of both Mouvex or standardized mechanical seals, which helps expedite installations regardless of location. The mechanical seal is positioned behind the piston and provides efficient shaft sealing. Mouvex A Series positive-displacement pumps enable product transfer up to 250 C (482 F). The pumps have maximum speeds to 750 rpm, maximum flow rates to 55 m/h (242 gpm), as well as suction and discharge ports from 1" through 4" in size. The A Series are positive displacement pumps and utilize eccentric disc technology, which enables self-priming and run-dry capabilities while maintaining constant flowrate regardless of changes in viscosity and pressure. Mouvex A Series pumps also maintain their initial performance over time and are ATEX-certified for use in potentially dangerous environments with the ability to run-dry for up to three minutes.


Monday, 24 June 2013

MSS publishes revised and new valve standards


The Manufactures Standardization Society (MSS) has announced the following six revised standards and one new publication:

Updated/Revised Publications

  • MSS SP-42-2013, Corrosion-Resistant Gate, Globe, Angle, and Check Valves with Flanged and Butt Weld Ends (Classes 150, 300, & 600)
  • MSS SP-61-2013, Pressure Testing of Valves
  • MSS SP-81-2013, Stainless-Steel or Stainless-Steel-Lined, Bonnetless, Knife Gate Valves with Flanged Ends
  • MSS SP-123-2013, Non-Ferrous Threaded and Solder-Joint Unions for Use with Copper Water Tube
  • MSS SP-126-2013, In-Line, Spring-Assisted, Center-Guided Check Valves (Carbon, Alloy Steel, Stainless Steel, & Nickel Alloys)
  • MSS SP-130-2013, Bellows Seals for Instrument Valves

Note: SP-81-2013 and SP-126-2013 includes a revised title.

New Publication

MSS SP-145-2013, Metal Ball Valves for Low Pressure/Low Temperature Plumbing Applications

Summary: This Standard Practice establishes requirements for ball valves with CWP ratings; including pressure-temperature ratings, materials, design, dimensions, marking, and testing.



Tuesday, 18 June 2013

Flowserve Plug Valve Design Eliminates Maintenance

Flowserve Corporation introduces a breakthrough plug valve designed for high-pressure applications in the seawater reverse osmosis (SWRO) desalination industry. The corrosion-resistant Flowserve Durco PlugSeal allows for quick and easy repair without requiring removal of the valve from the process line, or the need for special equipment and specially trained technicians.

The unique PFA-coated plug design, an industry first, eliminates the need for a sleeve that is often difficult and expensive to remove or replace during repairs. Flowserve Durco PlugSeal can be repaired quickly — without being cut from the process line. If the valve's plug becomes worn it is easy and inexpensive to replace.

MORE INFO: www.flowserve.com



Regards,

Anup Shah

Adroitt Flow Control Pvt Ltd

Cell +91 9820501463

anup@adroitt.net

anup.adroitt@gmail.com


Sent from my iPhone

True Meaning of Double Block & Bleed Valve


It's time to do maintenance on a section of process. You don't want to shut down the entire facility, so you decide to block off and depressurize just the section you're working on. Just upstream is a double block and bleed valve—a trunnion-mounted ball valve with self-relieving seals and a bleed valve to vent the cavity. You close the ball valve and open the bleeder. Now you can de-pressurize the line downstream and open it up to work on it.

No so fast, says Rudy Garza. You may think that valve gives you double isolation, but it doesn't—and that could be dangerous.

On March 4 Garza, Mechanical Lead—Static Equipment Engineering Group at ExxonMobil Development Company, gave a presentation at the VMA Technical Seminar in San Antonio entitled "Isolation Philosophies" in which he asserted that many people take the term "Double Block & Bleed" (DBB) to mean the same thing as Double Positive Isolation" (DPI). While this may seem like a small matter, he says, it means that some users may think they've achieved positive isolation when they haven't. Part of the problem, he goes on, is that designers and users don't always understand the capabilities of the valves in question. And, he adds, the design of a particular valve can vary from one manufacturer to another.

Garza stresses that his presentation shouldn't be taken as holy writ, but as how his particular branch of ExxonMobil (i.e. Upstream) looks at the situation in its own industry and the practices it uses. Other companies (including within ExxonMobil) and industries may do things differently and it is up to the users to determine the safety and suitability of a particular practice to their application, he says.

The key message is that a user should look at the design of a particular valve, and find out exactly what the manufacturer means by the term "double positive isolation" or "double block and bleed.", to make sure it's really what's needed in a particular application.

Many users, says Garza, have taken "double block and bleed" as a generic term, and tend to use it when they really mean (and the applicable specification—API 6D, Specification for Pipeline Valves, requires) the use of double isolation and bleed. The key to understanding, Garza says, can be found in API 6D. That specification wasn't always as clear as it could have been in spelling out the difference between DBB and DPI, but the addition in 2008 of several notes has clarified it.

API 6D defines a double-block-and-bleed valve (DBB) as a "single valve with two seating surfaces that, in the closed position, provides a seal against pressure from both ends of the valve with a means of venting/bleeding the cavity between the seating surfaces." The 2008 note points out that this valve does not provide positive double isolation when only one side is under pressure.

By contrast, API 6D defines a double-isolation-and-bleed valve (DIB) as a "single valve with two seating surfaces, each of which, in the closed position, provides a seal against pressure from a single source, with a means of venting/bleeding the cavity between the seating surfaces." The note adds that this feature can be provided in one direction or in both directions.

The job of a double isolation and bleed is to stop process fluid from getting into an area where work is being done. Both in-line valves would be closed, then the bleeder would be opened. If any fluid leaked past the first valve the bleeder would drain it off before it pressurized the cavity—the space between the upstream and downstream valves, and at the same time would act as a tell-tale to indicate the leakage. If the bleeder (which is smaller than the in-line valves and may, in fact, be a needle valve) were to be plugged the downstream valve would keep process fluid from getting past it.

So why is the difference between DBB and DIB important? Let's consider a typical trunnion-mounted ball valve with self-relieving seats. API 6D defines this as a double block and bleed valve, not a double isolation and bleed valve. Under normal conditions (Figure 1) there is pressure on the upstream seal, which (along with an internal spring) keeps it energized. There's no pressure on the downstream side, so the only thing energizing the seal on that side is a spring. The bleeder valves are open, and the cavity in the ball is at atmospheric pressure.

But it's not uncommon for a valve that's been in service for a while to leak a bit. Figure 2 shows what happens then. The upstream seal is leaking a little, but this should not be a problem because the leakage will be carried away by the bleeder—except when the bleeder is not working, either because one or both of the bleeder valves is closed, or because there's a clog in the bleed line. The pressure in the valve cavity can then possibly reach as high as 200 psi, which overcomes the spring on the downstream seal and forces it off its seat, discharging fluid downstream to where people may be working. This is clearly not a double isolation and bleed valve.

So where should this type of valve be used? Figure 3 shows a situation that might occur when the valve is used in a bypass loop for proving a flowmeter, for example. The valve is closed and the bleeder is open. This time there is pressure on both the upstream and downstream seals, keeping them fully energized. This is the configuration that the API 6D definition of "double block and bleed" intended when it referred to "two sealing surfaces." But it's not true double positive isolation and bleed, as far as ExxonMobil Upstream is concerned, and in certain services, it shouldn't be used to isolate a section for maintenance.

To prevent confusion ExxonMobil Upstream sorts valves into four categories—A, B, C and D—according to the physical flow blocking capabilities of the valve and then provides guidance based on the minimum isolation requirements for a particular application, such as long vs. short term, segregation for meter proving, etc.

  • Type A is a single block valve with a single mechanically energized seal and no body bleed required.
  • Type Bis a double block and bleed (as defined in API 6D, but not always by industry). It requires pressure on upstream and downstream sides simultaneously to energize the respective seals. It's the type shown in Figures 1 through 3 (see end of article).
  • Type Cis a true double isolation and bleed (DIB) per API 6D. The valve is a single body with dual positive seals; it has a single obturator (gate, plug, etc) and dual positively energized seals (upstream and downstream) with cavity bleed port between them. It requires a cavity overpressure protection device in expansive fluid services).
  • Type D is a true double positive isolation and bleed valve arrangement, with two independent obturators (sealing members) in the same or separate bodies and two separate actuating mechanisms (i.e. independent stems). It can be made up of a pair of certain Type A, B, or C valves, either separate or built into one body. It must have a bleeder in the middle (between the two valves and between each valve's seals if Type C valves are used).

Table 1: Example valve type classifications

Type

EM Class

Ball - Floating

A

Ball - Trunnion, SRS

B*

Ball - Trunnion, DPE

B*

Ball - Rising Stem

A

Globe - (Excluding Control Valves)

A

Plug - Standard

A

Plug - Mechanically Energized Seats

C

Gate - Expanding

C

Gate - Slab

B

Gate - Sliding

A*

Gate - Solid Wedge

B*

Gate - Unported Flexible Wedge

B

Butterfly (all types)

A

* Denotes potential for exceptions based on configuration of valve and/or manufacturer

"SRS" = self relieving seats; "DPE" = double piston effect seats

Table 2 is a generic example of a filled-in requirements table. Usually there's a temperature threshold (T1, T2, etc), then a fluid characterization (flammable, non-flammable, etc.), then a pressure class (All, C1, C2, etc.), and then a size range (All, D1, D2, etc.). On the far right is the type of valve designated for that particular service (A, B, C or D). The application of the table is driven primarily by the individual facility's "isolation philosophy." The valve Type shown is risk and experience based, and it requires well documented definitions (management endorsed) for each type of valve (including variations thereof). In addition, the definition of "flammable" and "toxic" is likely to vary by company and/or location.

Table 2: Sample positive isolation format

Fluid
Design 
Temp

Fluid (examples)

Pressure or Class

Size (NPS)

Min. Valve Type (examples)

Isolation for Condition 1 (e.g. Long-Term Maintenance)

≤T1

Flammables

All

All

D

Nonflammables

>C1

All

D

≤C1

All

B

>T1

Flammables

All

All

D

Nonflammables

>C2

All

D

≤C2

All

B

Isolation for Condition 2 (e.g. Short-Term Maintenance)

>T1

All

All

All

D

≤T2

Toxic & highly 
corrosive materials

All

All

C

Flammable materials

≤C3

All

B

C4, C5 and C6

≤D1

B

Instrument connections 
with flammable 
materials

≤C7

≤D2

B

>C7

≤D2

D

Water, air and other
non-flammables

≤C8

≤D3

A

>C8 but ≤C9

All

C

All

≥C10

All

D

Isolation for Condition 3 (e.g. meter provers)

All

Specify as needed

All

All

B

Isolation for Condition 4 (etc.)

All

Specify as needed

All

All

D

Note: A "blind" can be substituted as one of the isolation points (i.e. 1 of 2 in DIB)

Remember that local regulations vary and must be kept in mind when making any valve selection.

Summary

Garza is quick to point out that the Type A, B, C and D designations are not aligned with the API 6D classifications or those of other industry standards, and are simply practices that ExxonMobil Upstream has adopted for its own use, but they bring out an important point: although block valves can stop flow, the way in which they achieve this varies and hence when specifying a valve for isolation service, don't inadvertently use a double block and bleed valve when you really need a double isolation and bleed type.

Reach Peter Cleveland at pcleaveland@earthlink.net. A longer version of this article will appear in a future issue of Valve Magazine. All images are courtesy of Rudy Garza and ExxonMobil Development Company.

Figure 1 (below). In this trunnion-mounted ball valve with self-relieving seats (which API 6D defines as a double block and bleed) there is pressure on the upstream seal, but no pressure on the downstream side, so the only thing energizing the seal on that side is a spring.

true meaning figure 1


Figure 2 (below). If the upstream seal should leak, and the bleeder is closed or clogged, the pressure in the valve cavity can overcome the spring on the downstream seal and force it off its seat, discharging fluid downstream to where personnel may have the piping opened for maintenance.

true meaning figure 2


Figure 3. This type of valve is best used where there is pressure on both the upstream and downstream seals, keeping them fully energized, as in a bypass loop for proving a flowmeter, for example. This is the configuration that the API 6D definition of "double block and bleed" intended when it referred to "two sealing surfaces," but it's not double positive isolation, as far as ExxonMobil Upstream is concerned, and it shouldn't be used to isolate a section for maintenance.

true meaning figure 3


Ready for Low - E Valve Technology


With an estimated 60% of fugitive emissions attributed to valves it is easy to see EPA's attention is on valve emissions reduction. Traditionally valve stem leakage was a visible event. Improvements in packing materials and design lead to non-visibly leaking valves.

In today's world, government regulations drive measurement of valve leakage to the molecular level in parts per million (ppm). These extremely low vaporous emissions required packing manufacturers to evaluate their product performance to the latest EPA standards for Low E Valve Packing Technology.

 


Definition

 

The terms we have become familiar with are "Certified Low-Leaking Valves" and "Certified Low-Leaking Valve Packing Technology" as defined by the EPA in consent decrees. In more current consent decrees, new valves entering will be required to be certified as "Low E Technology". A "Low-E Valve "is defined as:

"A valve (including its specific packing assembly) or valve packing for which the manufacturer has issued a written warranty that it will not emit fugitives at greater than 100 ppm, and that, if it does so emit at any time in the first five years, the manufacturer will replace the valve; provided however, that no valve shall qualify as "Low-E" by reason of written warranty unless

(i) the valve (including its specific packing assembly) either:

(a) first was tested by the manufacturer or a qualified testing firm pursuant to generally-accepted good engineering practices for testing fugitive emissions and the results of the testing reasonably support the warranty; or

(b) is as an Extension of another valve that qualified as "Low-E";

(ii) A valve (including its specific packing assembly) that:

(a) Has been tested by the manufacturer or a qualified testing firm pursuant to generally-accepted good engineering practices for testing fugitive emissions and that, during the test, at no time leaked at greater than 500 ppm, and on Average, leaked at less than 100 ppm; or

(b) Is an Extension of another valve that qualified as 'Low-E'."

This current definition of Low E Valve Technology adds test documentation to this requirement. Manufacturers have offered this warranty without supporting test data. Today there are reputable packing and valve manufacturers that can meet these low emission level requirements and documentation to assist valve manufacturers in achieving Low E requirements.


Test Protocols

Many existing test protocols are designed to measure the performance of valves and packing products. The two most commonly used protocols are API standards and ISO 15848-1. The API standards utilize methane as the media and Method 21 to measure emissions while the ISO test typically uses helium as the media with vacuum as the leak detection method. It is important to note the EPA only recognizes emission testing conducted utilizing Method 21.

API 622 fugitive emissions test protocol evaluates the performance of a valve packing in a specified test fixture, number of strokes and temperature cycles while monitoring emissions in ppm. This protocol allows for average leakage measurements up to 500 ppm and one retorque throughout the test. The test is not a pass or fail, but determines if a packing completed the test without exceeding these limits.

The API 624 valve fugitive emissions test protocol is soon to be published. This standard sets the limit of 100 ppm emissions from the valve and no retorques are allowed. The standard also requires valve manufacturers to use an API 622 tested and qualified packing in this test. Not all API 622 qualified packings will be able to meet the API 624 requirements.

Starting with a valve packing qualified to API 622 with a maximum leakage of below 50 ppm and no retorques is important. Factors such as surface finish, tolerances and valve design will affect packing performance. When selecting a packing that has a maximum leakage of below 50 ppm allows for these factors and gives the valve manufacturer a better chance of meeting the API 624 requirements.


Converting to Low E Technology

As a valve manufacturer, adapting the Low E Technology as a standard for your equipment puts you in the position to provide the latest in valve packing sealing. Since Low E packings seal to such a tight standard, using them for all services allows you to offer the latest in sealing technology to all your users. A few forward thinking valve manufacturers have taken the lead to convert all their valves to Low E Technology. This is a benefit to their customers with a variety of valves ( some requiring Low E technology, while others are exempt as they are not in VOC and VHAP services). This standardization minimizes confusion and the need for the customer to keep two sets of valves (one for Low E services and one for all others). It also prevents installing the wrong valve in a Low E Technology required process.

Valve and packing manufacturers have the opportunity to be proactive in supplying Low E Technology to their customers. The EPA is knowledgeable of the current state of Low E technology and will no longer accept the argument that low emission valve technology is unavailable. Incorporating Low E Packing in your valves addresses the growing need in the emissions valve market as more consent decrees are issued and EPA enforcement is stepped up.


Walter S. Moquin is currently Manager of Business Development for Mechanical Packings and Gaskets with the A. W. Chesterton Company where he oversees the business for pump and valve packings. Moquin has conducted technical equipment reliability seminars and training regarding process systems and components. He was also responsible for field testing of new products, failure analysis, and application engineering. He currently is involved with Chesterton's Valve Emissions Program and working with the EPA, end users and valve OEMs to better understand Low E packing technology. He can be contacted at moquinws@chesterton.com