Self adjusting energized valve seal

A seal and seat for ball valves is a circular, elastomeric open torus which is fitted between the ball element and the housing. The open torus has within it, a substantially "v" shaped spring that is fitted within the "u" shaped opening of the torus. In normal operation, the spring member is slightly compressed between the ball and the housing and the ball can "float" between a pair of substantially similar seals on the input and output sides of the ball valve, respectively.

The present invention relates to valve seals and, more particularly, an 
improved, dynamic self adjusting seal for a ball valve that establishes a 
predetermined contact pressure between the ball and the seal that is 
substantially independent of the fluid pressures in the lines controlled 
by the valve. 
BACKGROUND OF INVENTION 
Conventional ball valves are mounted in a rigid seat or seal, which is a 
primary seal and which may be backed by O-rings to act as a secondary 
seal. Alternatively, other, specially configured elastomeric rings of 
special geometry can be used to insure that the ball remains sealed during 
operation of the valve. In many valves, however, only the seal on the 
pressurized side of the valve is maintained in contact with the ball while 
the other seal tends to "float". 
When employed in an aircraft lavatory system, the ball valve seals may both 
be under pressure at different times and accordingly, these seals must be 
kept in close contact with the ball valve surface at all times, which 
tends to increase the drag or frictional resistance to the actuation of 
the valve. 
An additional problem encountered by the seals that are utilized in 
aircraft lavatory systems is the hostile environment created by the 
chemicals that are found in the flushing solutions and other fluids that 
are found in such a system. These chemicals frequently react with the 
conventional elastomers heretofore in use in the valve seats and seals and 
cause swelling and possibly disintegration of such seats and seals. 
The swelling of the seats or seals increases any existing drag or friction 
and therefore increase the requisite actuation forces. This may result in 
exceeding the allowable operating limits of the actuation or linkage 
mechanisms which have been designed to open and close the valve. 
BRIEF SUMMARY OF INVENTION 
What is needed and what is provided by the present invention is a 
combination of a thin-walled primary seal with a lip and spring member, 
and a secondary body seal that will resist attack from the environment in 
which it operates. Further, it is desirable to have a primary and body 
seal combination that is dynamically self adjusting to accommodate 
pressure differentials on both sides of the valve, so that a higher 
pressure can be applied to either side of the valve and so that the valve 
functions when subjected to low pressure and vacuum conditions. 
Where prior art devices could employ a solid seat with an elastomeric seal, 
the present invention employs a thin-walled primary seal with lip and 
spring member, in combination with a secondary "body" seal. The primary 
seal is provided by the combination of a thin-walled elastomeric membrane 
draping or jacketing (by means of "lips" in the thin-walled "jacket") a 
"v-shaped" cantilever spring that assures a positive seal under all 
operating conditions. 
A gallery in the valve housing holds the elastomeric jacketed spring. The 
leading edge of the membranous jacket contains a slight bulbous thickening 
which bears against the ball. The resultant jacketed spring with a 
thickening on the leading edge can compress or expand, depending upon the 
forces to which it is subjected. The "v-shaped" spring supports the 
membranous elastomeric "jacket" tends towards an open position; thus 
keeping the leading edge in sealing engagement with the ball of the valve. 
The dimensions of the valve are chosen so that the ball is in equilibrium 
between the seals on both sides of the ball and floats in place. Any 
pressure differential experienced by the valve, when closed, is partially 
absorbed by the elasticity of the membranously jacketed spring. 
The stiffness of the spring is chosen to permit easy actuation of the ball 
valve, under all fluid operating pressures that are to be encountered. 
This also provides the dynamic "self-adjusting" feature of the seal. 
Further, the fluid pressure may be considered an "energizing" factor that 
contributes to the integrity of the seal at all times. The resultant force 
between the primary seal and the ball, at the contact area assures 
positive sealing. Since the ball is permitted a limited amount of float in 
the seals, the operating force needed will remain more or less constant 
under a wide range of operating conditions i.e. vacuum low, and high 
pressure. 
The novel features which are characteristic of the invention, both as to 
structure and method of operation thereof, together with further objects 
and advantages thereof, will be understood from the following description, 
considered in connection with the accompanying drawings, in which the 
preferred embodiment of the invention is illustrated by way of example. It 
is to be expressly understood, however, that the drawings are for the 
purpose of illustration and description only, and they are not intended as 
a definition of the limits of the invention.

DETAILED DESCRIPTION OF THE DRAWINGS 
Turning first to FIGS. 1 and 2, there is shown a typical ball valve 10 such 
as is used, for example, in the waste system of an aircraft. An operating 
handle 12 is attached to the ball 14 and can rotate through approximately 
90.degree. to "open" and "close" the valve. 
As shown, the ball valve is asymmetrical with different fittings on the 
ports 16, 18 of the valve. For convenience in description, the port 16 on 
the left in FIGS. 1 and 2 may be considered the input port and the port 
18, on the right is then considered the output port. 
According to the present invention, the choice is completely arbitrary 
although in designs of the prior art, the seals on the input and output 
sides of the ball were different, thereby dictating which port was which. 
As seen in FIGS. 3A and 3B, there is a cylindrical aperture 20 that goes 
through the ball 14 with an axis that is orthogonal to the rotational axis 
as defined by the handle 12. As the handle 12 rotates the ball 14, the 
aperture 20 is either aligned with the ports 16, 18, in which event the 
valve is "open" (as in FIG. 3B), or is orthogonal to them, in which event 
the valve is "closed" (as in FIG. 3A). 
Both the inlet port 16 and the outlet port 18 have seal retaining grooves 
22, 24, respectively. Within the grooves 22, 24 are placed seal elements 
26 which have a base portion 28 in which is placed a slot or groove 30 for 
holding O-rings 32. The O-rings 32 provide the secondary, body seal by 
means of O-ring 32 sealing the walls of groove 30 and the gallery 24. The 
primary seal is the dynamic combination of the convex edge 34 of a folded 
over thin-walled jacket 36 in conjunction with the supporting spring of 
the seal element. A pocket is formed in the thin-walled elastomeric 
jacket, inside of which is placed a generally v-shaped spring element 38 
which supports the top 34. 
Preferably, the spring element 38 is of stainless steel and is arranged to 
have the arms of the "v" extending outwardly so that the primary seal 
convex edge or tip 34 is biased into engagement with the ball 14. 
The dynamic self adjusting energized seal of the present invention is best 
seen in FIG. 4, which is an enlarged sectional view of a groove 22, 24 in 
which the seal element 26 is carried. As noted above, the convex edge or 
tip 34 of the thin wall or membrane jacket 36in combination with the 
spring element 38 is considered the primary seal and the O-ring 32 is the 
secondary or body seal. To hold the spring 38 in place, a first shoulder 
40 is provided in the base portion 28 of the seal element 26, and a second 
shoulder 42 is provided in the inner surface of the thin-walled jacket 36. 
The first and second shoulders 40, 42 are positioned so that the spring 
element 38 is permitted some movement within the pocket created between 
jacket 36 and the base portion 24. 
As seen in FIG. 4, the sealing element 26 can accommodate movement of the 
ball 14 under the pressure differential that may exist between the intake 
and outlet ports. However, the primary seal is under sufficient spring 
force from spring element 38 to maintain a fluid tight engagement with the 
ball 14 to prevent any leakage, not only at the convex edge 34 but through 
the O-ring 32 body seals, as well. 
To achieve a suitable bias spring 38, one may start with a flat strip of 
spring steel 50 as shown in FIG. 5. Alternating cuts are made from 
opposing edges. As shown, first cuts 52 are made from the top down, and 
second cuts 54 are made from the bottom up. Adjacent first cuts 52 are 
spaced apart by the same amount as adjacent second cuts 54. Preferably, 
each cut removes a very narrow strip of material so that a normally 
straight strip can easily be formed into curves without deformation of the 
strip. 
Obviously, the process to make the first and second cuts 52, 54 can be 
automated and an endless flat strip of spring steel can be produced. The 
flat strip 50 with the first and second cuts 52, 54 is next bent into a 
"v" shape. A length of spring, roughly equalling the circumference of 
interior of the "u" shaped jacket 36 of the primary seal is cut and is 
inserted into the interior of the jacket 36. The alternating first and 
second cuts 52, 54 give the finished spring 38 sufficient flexibility 
without substantial stress so that the spring 38 tends to remain in place 
with the aid of the first and second shoulders 40, 42. 
The width of the first and second cuts 52, 54 can vary as a function of the 
circumference of the circle that is to be occupied. The primary task of 
the spring thus produced is to support the folded over jacket portion 36 
of the seal element 26. As can be seen, a plurality of interconnected, 
side-by-side "v" shaped incremental spring elements are disposed about the 
interior of the jacket 36 of the elastomeric sealing member 26. 
The perspective view of FIG. 6 shows the cut spring member 38 after the 
bend but before assembly and insertion into the jacket 36 of the seal 
element 26. While this is a preferred embodiment and highly susceptible to 
automated production and assembly, this is not the only possible 
embodiment. Alternatives will occur to those skilled in the art and, 
accordingly, the invention should be limited only to the scope of the 
claims appended hereto.