Parker O-Ring Handbook.pdf
Parker O-Ring Handbook.pdf
Parker O-Ring Handbook.pdf
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Dynamic O-<strong>Ring</strong> Sealing<br />
5-10<br />
Related to the working conditions:<br />
• Working pressure;<br />
• Velocity of movement;<br />
• Type of material and surface fi nish of surfaces;<br />
• Working tolerances;<br />
• Axial loads and wear bands on pistons.<br />
These factors cannot be quantifi ed because they overlap and<br />
act cumulatively.<br />
At the beginning of a stroke the seal goes through three<br />
friction phases. Initially the seal is in direct contact with the<br />
sealing face with few lubricated fi elds, e.g., µ = 0.3. Then<br />
follows a wider area of mixed friction where the coeffi cient<br />
of friction can drop as low as 0.06 to 0.08 according to the<br />
proportion of lubrication/non-lubricated areas (Figure 5-11).<br />
Finally, pure hydrodynamic friction which does not allow<br />
direct contact between the seal and the running surfaces is<br />
rarely reached.<br />
As complete lubrication (= fl ooding) occurs, loss of fl uid<br />
from a system increases.<br />
Friction depends on a compound's sliding properties. Hardness<br />
and deformation of the seal infl uence the seal pressure.<br />
Specifi c seal pressure is in general related to, but not strictly<br />
proportional, to the system pressure.<br />
The working pressure controls the width of clearance gaps<br />
and thereby the thickness of the lubricating fi lm. The result<br />
depends on the geometry of the seal. Friction caused by Orings<br />
increases with increasing pressure. Lip seals are more<br />
sensitive to pressure, friction increases quicker than with seals<br />
without a lip. This shows that the geometry of a seal directly<br />
affects the amount of friction.<br />
Friction is proportional to the working pressure and therefore<br />
it is necessary to keep seal friction low, especially at<br />
low pressures.<br />
Unfortunately, reduction of the sealing force also results in an<br />
increased tendency to leakage. This relationship can be modifi<br />
ed within certain limits by selection of the seal geometry.<br />
Coefficient of Friction μ<br />
Vμmin. Figure 5-11: Stribeck Diagram<br />
Stribeck diagram<br />
Break-out friction<br />
Mixed friction<br />
Hydro-dynamic friction<br />
Velocity V<br />
<strong>Parker</strong> O-<strong>Ring</strong> <strong>Handbook</strong><br />
Normally the decision must be made between lower friction<br />
and high leakage.<br />
Additionally, an unstable seal geometry due to swelling in<br />
the medium plays a role. Swelling means increase sealing<br />
force and increased friction.<br />
When the medium is mineral oil it would seem that suffi cient<br />
lubrication is assured. However, the seal geometry once again<br />
plays a role when, for example, a wiper seal scrapes a shaft<br />
dry. Leakage at a wiper seal will not occur until the seal wears.<br />
On the other hand lubrication can cause leakage amounting<br />
to the thick lubricating fi lm with every stroke.<br />
The optimum condition is a relatively thin lubricating fi lm<br />
with suffi cient adhesive properties.<br />
The dynamic piston actually causes less friction with increasing<br />
velocity. In absolute terms there are very large discrepancies<br />
according to the thickness of the lubricating fi lm. The<br />
reduction of friction with increasing velocity stems from<br />
the hydrodynamic properties of the lubricating fl uid. This is<br />
also true for harder compounds. At low pressures the friction<br />
varies to the piston speed. At high pressures friction is seen<br />
to be more or less constant.<br />
Friction is directly infl uenced by the seal diameter because the<br />
wear-area is greater. The greater the metal surface roughness,<br />
the more the contact surface consists of metallic “islands”<br />
and therefore again mixed friction occurs.<br />
As in many other areas break-out friction of elastomers<br />
is signifi cantly higher than running friction. Apart from<br />
compound type and seal geometry, tendency to adhesion,<br />
deformation, the down-time and the surface fi nish play a role<br />
in increasing break-out friction. The longer the down-time,<br />
the more lubrication is squeezed from between the seal and<br />
the running surface resulting in a non-lubricated vacuum. In<br />
this condition the level of starting friction approaches that<br />
for dry friction and is up to 10 times that found in running<br />
friction (Figures 5-12 and 5-11).<br />
Coefficient of Friction<br />
1.2<br />
0.8<br />
0.4<br />
Level of Starting Friction<br />
Dependant Upon Time and Compound<br />
10 sec. 1 min. 1 hr. 1 day 1 wk. 1 mo.<br />
Downtime<br />
Compounds: a) Polyurethane b) NBR<br />
Figure 5-12: Level of Starting Friction Dependant Upon Time<br />
and Compound<br />
a)<br />
b)<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