Parker O-Ring Handbook.pdf
Parker O-Ring Handbook.pdf
Parker O-Ring Handbook.pdf
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5.16.1 Small Amount of Leakage<br />
1. Examine the O-ring for signs of cutting during<br />
installation.<br />
2. Increase the squeeze on the cross-section of O-ring.<br />
3. Reduce the groove length. A wide groove may cause<br />
leakage because of pumping action of the O-ring. This<br />
is especially possible when the piston is cycled rapidly.<br />
4. Improve the surface fi nish of metal rubbing surface.<br />
5. Check for eccentric machining of gland.<br />
5.16.2 Early Stress-Aging<br />
1. Redesign groove to reduce stretch of the O-ring.<br />
2. Redesign groove to reduce squeeze of the O-ring.<br />
3. Use a more heat-resistant rubber compound.<br />
4. Make certain O-ring is not being twisted during dry<br />
assembly.<br />
5. Use larger O-ring to reduce stretch.<br />
6. Make sure O-rings are not closer than six feet from an<br />
electric motor (operating) during shelf storage. Ozone<br />
causes rapid deterioration of most elastomers.<br />
5.16.3 Low Temperature Leakage<br />
1. Make certain that O-ring compound was designed for<br />
operation at low temperatures.<br />
2. Increase squeeze of the O-ring. Coeffi cient of contraction<br />
of rubber is about 10 times that of steel and several<br />
times greater than aluminum.<br />
3. Spring load the O-ring (see Figure 3-1).<br />
4. Make sure all gland surfaces are smooth enough (see<br />
paragraph 5.3).<br />
Note: Minute leakage is to be expected and is in fact, desirable,<br />
when an O-ring is used as a reciprocating seal. An O-ring<br />
that does not by-pass a little fl uid at each stroke is running<br />
dry and high friction and rapid seal wear will result.<br />
5.16.4 Excessive Swell (above 20%)<br />
1. Replace O-ring with one made from a compound more<br />
resistant to the fl uid being sealed.<br />
2. Increase groove length. If the volume of the groove is<br />
too small, increased friction and excessive stress may<br />
cause premature failure of the O-ring (refer to discussions<br />
of friction and spiral failure).<br />
5.17 Gland Dimensions for<br />
Reciprocating Hydraulic O-<strong>Ring</strong> Seals<br />
For most reciprocating applications in which an O-ring is<br />
sealing a liquid of any kind (the design is not limited to hydraulic<br />
oils), the dimensions of either Design Table 5-1, the<br />
military design, or Design Table 5-2, the industrial design,<br />
would be suitable. Of the two, <strong>Parker</strong> Seal Group normally<br />
recommends the Table 5-2 dimensions because these industrial<br />
designs, in most cases, allow for the use of standard drill rod<br />
<strong>Parker</strong> O-<strong>Ring</strong> <strong>Handbook</strong><br />
X X<br />
Washer must be<br />
tight against<br />
shaft shoulder<br />
Figure 5-18: Floating Gland<br />
E<br />
2<br />
Snap<br />
<strong>Ring</strong><br />
Clearance: X = 0.003 to 0.006 in.<br />
E To prevent extrusion<br />
2 refer to Figure 3-2<br />
or Table 5-1 or 5-2<br />
sizes and standard boring tools. The dimensions in this table<br />
are actually in good agreement with early versions of the<br />
aerospace table. The military dimensions cause less stretch<br />
on the O-rings. The percent reduction is so slight, except in<br />
the smallest sizes, that the effect cannot be signifi cant, while<br />
the cost of the special machined rods and boring tools that<br />
are required could be high.<br />
In reciprocating applications for which neither table applies<br />
because of a predetermined dimension that does not agree, the<br />
following procedure may be used to fi nd gland dimensions.<br />
1. For piston seals, select an O-ring having an OD near to or<br />
preferably slightly larger than the cylinder bore diameter.<br />
2. For rod seals, select on O-ring having an ID closest to<br />
the rod diameter. It may be slightly larger or smaller,<br />
but ID stretch should not exceed 5% as installed for<br />
optimum design.<br />
3. In all reciprocating seals, make sure minimum squeeze<br />
recommendations are considered.<br />
5.18 Floating Glands<br />
Since it is impossible to bore, drill or tap perfect, true holes,<br />
and to machine perfect parts providing perfect alignment,<br />
the engineer should consider the fl oating gland. Eccentricity<br />
(lack of concentricity) is allowable, but it does cause high<br />
unit loads on small portions of bearing surfaces. In turn, this<br />
causes minute scratches on the metal surface on which the<br />
O-ring must rub (with the possible exception of very soft<br />
bearing materials, such as babbitt).<br />
In order to reduce or eliminate the high bearing loads, the<br />
relatively inexpensive fl oating gland should be used whenever<br />
possible. The object of this gland is to allow the piston or rod<br />
bearing (containing the O-ring groove), to pivot, adjust, or fl oat<br />
a small amount, offsetting misalignment. (See Figure 5-18.)<br />
This gland design increases the life of the O-ring and eliminates<br />
many of the spasmodic or unscheduled failures, as well<br />
as reducing the maintenance cost.<br />
<strong>Parker</strong> Hannifi n Corporation • O-<strong>Ring</strong> Division<br />
2360 Palumbo Drive, Lexington, KY 40509<br />
Phone: (859) 269-2351 Fax: (859) 335-5128<br />
www.parkerorings.com<br />
X<br />
Dynamic O-<strong>Ring</strong> Sealing<br />
5-15