Gasket Fundamentals

The Function of a Gasket is to create and maintain a static seal between two stationary, imperfect surfaces of a mechanical system, designed to contain a wide variety of liquids or gases. The gasket must be able to maintain this seal under all the operating conditions of the system including extremes of temperature and pressure.

The performance of the gasket is affected by a number of factors. All of these factors must be taken into consideration when selecting a gasket.

The Flange Load: All gasket materials must have sufficient flange pressure to compress the gasket enough to insure that a tight, unbroken seal occurs. The flange pressure, or minimum seating stress, necessary to accomplish this is known as the “Y” factor. This flange pressure must be applied uniformly across the entire seating area to achieve perfect sealing. However, in actual service, the distribution around the gasket is not uniform. The greatest force is exerted on the area directly surrounding the bolts. The lowest force occurs mid-way between two bolts. This factor must be taken into account by the flange designer.

The Internal Pressure: In service, as soon as pressure is applied to the vessel, the initial gasket compression is reduced by the internal pressure acting against the gasket (blowout pressure) and the flanges (hydrostatic end force). To account for this, an additional preload must be placed on the gasket material. An “m” or maintenance factor has been established by ASME to account for this preload. The “m” factor defines how many times the residual load (original load minus the internal pressure) must exceed the internal pressure. In this calculation, the normal pressure and the test pressure should be taken into account.

Temperature: The effects of both ambient and process temperature on the gasket material, the flanges and the bolts must be taken into account. These effects include bolt elongation, creep relaxation of the gasket material or thermal degradation. This can result in a reduction of the flange load. The higher he operating temperature, the more care needs to be taken with the gasket material selection. As the system is pressurized and heated, the joint deforms. Different coefficients of expansion between the bolts, the flanges and the pipe can result in forces which can affect the gasket. The relative stiffness of the bolted joint determines whether there is a net gain or loss in the bolt load. Generally, flexible joints lose bolt load.

Fluid: The media being sealed, usually a liquid or a gas with a gas being harder to seal than a liquid. The effect of temperature on many fluids causes them to become more aggressive. Therefore, a fluid that can be sealed at ambient temperature, may adversely affect the gasket at a higher temperature.

Both the “m” and “Y” factors will vary with the type of gasket and the thickness of the gasket. Always consult with the manufacturer to determine the “m” and “Y” factors for the gasket material you are using.

In any application, failure to meet the “m” or “Y” factor will result in an imperfect seal and will require a change in the gasket design. This change can sometimes be made by simply decreasing the gasket surface area or by using a thicker gasket. However, since thinner gaskets are generally more effective, changing to a thicker gasket may not be the most satisfactory long-term solution. In some cases, a revision to the flange design may be required.

New gasket design factors being developed by ASME are for bolted joint designs where it is important that a desired level of tightness be achieved. “m” and “Y” factors do not take fugitive emissions into account, whereas the new assumption is that all bolted joints leak to some extent. This “systems approach” focuses on all the components of the bolted joint not just the gasket. A tightness parameter (Tp), is a defined measure of tightness of a joint. A higher value for Tp, represents a lower rate of leakage. See additional discussion under Other Considerations, in the section on Gasket Selection.

We recommend that metal flange faces be machined with a concentric-serrated finish of 125-500 AARH, with 250 AARH being the optimum for non-metallic gaskets. Phonographic serrations can also be used with our materials. It should be recognized, however, that their continuous leak path makes them more difficult to seal

The finish or the condition of the gasket seating surface has a definite effect on the ability of the gasket to create a seal. Sheet gasketing is designed to have a seating stress that allows the gasket material to “flow” into the serrations and irregularities of the flange face. This “bite” aids the gasket in resisting the effects of internal pressure, creep and cold flow.

“Smooth” finishes are usually found on machinery or flanged joints other than pipe flanges. When working with a smooth finish, it is important to consider using a thinner gasket to lessen the effects of creep and cold flow. It should be noted, however, that both a thinner gasket and the smooth finish, in and of themselves, require a higher compressive force (i.e. bolt torque) to achieve the seal.

Therefore, due to the flange design, one may have to resort to a thicker gasket, which requires a lower compressive force to seat the gasket. Another way to seat the gasket, when there is insufficient compressive force available, is to lessen the area of the gasket.

RAISED FACE to FULL FACE. We do not recommend mating a full face flange to a raised face flange especially when the full face flange is cast or ductile iron. Due to the potential for warping the flange, or in the worst case cracking it, the utmost care should be taken.

Even if a spacer that fits on the raised face flange outside the raised face area is used, damage to the flanges can still occur and great care should be taken.

FULL FACE FLANGES. In a bolted joint using ANSI full face (or flat face) flanges it must be remembered that the same bolts used in the corresponding raised face joint are now being asked to seal 3 to 4 times the gasket area with full face flanges. It is almost impossible to create an effective seal and high strength bolts should be considered.

ANSI Class 150 Full face bolted joints are poor design and should only be used for non-critical fluids.

It must be strongly stated that the use of metal based anti-seize compounds in general is not recommended. There are two issues to consider:

  1. Under heat and pressure, the metals in the compound can adhere to the flange surface, causing distortion of the flange and/or fill in the serrations. After a period of time, when this condition has been allowed to progress, no amount of additional torque will allow the gasket to seal.
  2. Anti-seize lubricates the gasket. This isn’t a problem until gasket compression is lost for some reason. Then the lubricated gasket can either be extruded, or forced out of the flange by the internal pressure. Here the friction created by the flange serrations play a role.

For these reasons the use of anti-seize is not recommended. However, if the application of anti-seize is not too liberal and the flange serrations are thoroughly cleaned each time a gasket is changed to maintain their integrity, it doesn’t present as much of a problem. The important thing is keeping the serrations intact, getting good compression on the gasket, and a minimum bolt stress of at least 40% of bolt yield.

As stated previously, the purpose of a gasket is to create a static seal between two stationary flanges. The seal itself is effected by achieving the proper compression on the gasket causing it to flow into the imperfections on the surface of the flange. This results in a tight, unbroken barrier, impervious to the fluid being contained.

In many instances, a good seal is obtained through the limited “swell” caused by the reaction of the inside edge of the gasket material with the fluid being contained.

A certain amount of swell is desirable, as long as it reaches an equilibrium and does not reach a condition of degradation where the gasket begins to breakdown. In many instances, the fluid being contained may “cauterize” the inside edge of the gasket and “seal off” the gasket from further fluid penetration

Bolting should be of sufficient strength to achieve proper compression of the gasket, to not only seal the joint, but to maintain the seal without exceeding the yield strength of the bolts being used. The torque values in our torque tables are based on using ASTM A193 Grade B7 studs and 2H heavy hex nuts lubricated with never seize.

Since sheet gasket materials have micropores, they must be sufficiently compressed to reduce porosity. Without adequate compression the system pressure can force the contained fluid into the gasket and degrade it.

Therefore, when installing the gasket it is important that good technique be followed including cleaning the flanges, inspecting the flange face and the bolts and bringing the flanges together parallel and in stages. Many field problems arise from improperly installed gaskets. Refer to the section on gasket installation.

Proper gasket selection and installation should be based on minimizing torque loss. Torque loss can be caused by the tendency of the gasket to relax or remold after it has been compressed and/or by elongation of the bolts. This loss can be minimized several ways:

  1. Use of a thinner gasket: The surface of the gasket is actually the sealing surface. The internal portion of the gasket is used primarily to insure that the imperfections in the sealing surface are filled. Since it is this internal portion that is primarily affected by creep relaxation, the thinner the gasket, the more effective the seal. However, if the surface to be sealed is pitted or marred or is somewhat distorted, it may not be feasible to switch to a thinner gasket.
  2. Use of a denser gasket: In general, the denser the gasket material, the less creep relaxation will occur. With materials of similar composition, greater density will require greater seating stresses to seal. Therefore, some lighter flanges may not be strong enough to use with a denser material.
  3. Use of conical washer: The elastic effect of a conical washer helps to compensate for some of the loss in gasket resilience. The washer also lengthens the bolt to a slight degree, lessening the effect of bolt elongation.
  4. Greater bolt load: The use of stronger bolts or more bolts can also help in the reduction of torque loss. Care should be taken to insure that the maximum loads on the bolts are not exceeded.

The importance to the environment of selecting the right gasket for today’s services cannot be overstated. With the emphasis on fugitive emissions gaining more and more prominence, selecting the proper gasket involves many considerations.

  • Process safety
  • Environmental concerns
  • Life of service in the flange
  • Maintenance costs
  • Inventory costs

Some things to consider when selecting a gasket are:

  • Chemical compatibility with the process fluid
  • The pressure-temperature (PxT Factor) relationship of the gasket to the service conditions
  • Physical and mechanical properties of the gasket material
  • Other considerations such as fire safety, and gasket design factors

Chemical resistance of the gasket material is important because without it, the other properties of the gasket are irrelevant. It is also important to keep in mind the effect temperature has on chemical resistance.

A chemical resistance chart can be a helpful guide. This information is available but it must be remembered that most chemicals become more reactive at higher temperatures. This must always be considered when selecting the gasket.

In some instances it is only prudent to consider field testing in a controlled application and we encourage this. Samples are available for such purposes. For samples, please fill out and submit a sample request form.

In all piping systems the flanges, valves and the piping itself have a pressure – temperature relationship. This PxT factor is the result of multiplying the operating pressure times the operating temperature to arrive at a numerical value. This value is not constant and is different at each temperature and pressure combination. In the table below the PxT factors for carbon steel piping per ANSI B16.34 and saturated steam are shown. The fact that PxT values exists for piping should indicate that such values also exist for gasketing, and just like piping, those values change with differences in the pressure and temperature.

Pressure-Temperature Relationships
Temp. (Carbon Steel)
Class 150
(Carbon Steel)
Class 300
Saturated Steam
°F psi (P x T) psi (P x T) psia (P x T)
100 285 (28,500) 740 (74,000) 1 (100)
200 260 (52,000) 675 (135,000) 12 (2,400)
300 230 (69,000) 655 (196,500) 68 (20,400)
400 200 (80,000) 635 (254,000) 250 (100,000)
500 170 (85,000) 600 (300,000) 680 (340,000)
600 140 (84,000) 550 (330,000) 1550 (930,000)
700 110 (77,000) 535 (374,500) 3100 (2,170,000)

The chart below graphically represents the information presented above



Now we can look at how sheet gaskets fit. As stated above just like piping, the PxT relationship for gaskets changes with each pressure – temperature combination and therefore is not a constant.

The chart below shows compressed non-asbestos and compressed asbestos gasketing vs. three different pressure classes and saturated steam for reference. This chart shows why, as a general rule, all sheet non-asbestos gasketing should be limited to Class 300 and below.


ASTM F104, the Standard Classification System for Nonmetallic Gasket Materials includes a line call-out encompassing ASTM test methods for evaluating the physical and mechanical properties of non-metallic gasket materials.

Some of these ASTM tests are:

F 36 – Compressibility and Recovery

F 37 – Sealability

F 38 – Creep-relaxation

F 146 – Fluid Resistance

F1574 – Compressive Strength

In addition to ASTM tests, we also do testing to BSI (British Standards), DIN (German Institute for Standardization) and FSA (Fluid Sealing Association) standards. These tests include:

BSI – F125A – Hot Compression

DIN – 3535 – Gas Permeability

FSA – NMG-204 – High Pressure Saturated Steam Test

These tests are outlined in the test methods section.

Additional considerations when selecting a gasket material may include:

Fire safe capability. There is no standard for “fire safe” gasket materials. However, Durlon® 8500 passed a modified API 607 fire test that was done by an independent lab.

API Spec 6BF, Fire Test for End Connections, and API Bulletins, 6F1 and 6F2, do discuss fire testing but for metal gaskets and API rings, not soft gasket material.

Gasket design factors. The m and y values established by ASME and the newer design factors being developed by the PVRC for fugitive emissions, are additional considerations. The m and y values do not take fugitive emissions into account whereas the newer tightness parameters (Tp) do.

These gasket factors recognize that all joints leak to some extent. Therefore, an acceptable level of leakage is defined. A leak rate of 1/2480 lb/hr per inch of OD has been defined as a “standard” acceptable leak rate and is known as T2.

Tp classes and their associated leak rates are as follows:

T1 – Economy – 1/25 lb/hr per inch of OD

T2 – Standard – 1/2,480 lb/hr per inch of OD

T3 – Tight – 1/248,000 lb/hr per inch of OD

Torque values for Durlon® products are calculated using a tightness parameter of T3.

What is Water Hammer?

Water Hammer is the generation and effect of high pressure shock waves (transients) in relatively incompressible fluids.

Water hammer is caused by the shock waves that are generated when a liquid is stopped abruptly in a pipe by an object such as a valve disc.

Symptoms include noise, vibration and hammering pipe sounds which can result in flange breakage, equipment damage, ruptured piping and damage to pipe supports. Whenever incompressible fluids exist in a piping system, the potential exists for water hammer.

The risks of water hammer developing are particularly high when:

  • The velocity of the fluid is high
  • There is a large mass of fluid moving and/or when there are large elevation changes within the piping systems

Since a swing check must rely on gravity and/or fluid flow to help it close, flow reversal must occur before closure begins. When a swing check finally closes, it abruptly stops the flow and causes a pressure surge resulting in shock waves. These shock waves continue until the energy generated from this sudden action dissipates.

Eliminate water hammer problems by installing a spring assisted silent check valve

High pressure shock waves created by the water hammer phenomenon act against the piping and the valve, exerting very high forces. This causes severe stress on the metal and vibrations in the system. If the system is not designed to withstand these high transient forces, the pipe could rupture and/or other components in the system, such as pumps and valves, could possibly be damaged. These problems can be eliminated or greatly minimized by installing a spring assisted silent check valve.

Silent check valves do not rely on gravity or fluid flow for their closure. Instead, as the forward velocity of the fluid slows, the spring assist on the valve starts to close the disc. Due to the spring assist and the relatively short distance the disc must travel, by the time the forward velocity has decreased to zero, the valve disc has reached the seat and the valve is closed. With reverse flow eliminated, the forces necessary to produce water hammer on both the upstream and downstream sides of the valves are substantially eliminated.