Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
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The valve of this invention is of the high pressure, rising stem
gate valve type as disclosed in our United S~ates patent Number 4,029,294
issued June 14, 1977, entitled "High Pressure Valve".
The valve construction of the present invention is ~he same as that
disclosed in the United States patent except for the stem sealing means.
The stem sealing means of the present invention is related to the
seals for tubing hangers disclosed in our United States patent Number 4,056,272
issued November 1, 1977, entitled "Seal".
This invention relates to valves and more par~icularly to extreme
temperature, high pressure, balanced, rising stem gate valves with super pre-
loaded, stacked, solid lubricated metal-to-metal stem seals.
A non-rising stem gate valve with separable seats and automatic plas-
tic sealed gate-seat and seat-body interfaces is disclosed in United States
patent number 2,433,638 - Volpin. A similarly sealed valve of the rising
stem~ balanced type intended for high pressureuseis disclosed in United
States patents number 3,538,938 - Volpin, and 3,696,831 Fowler et al.
In the latter two patents stem packing compressed by annular screw plugs
is employed for the stem seals.
A valve known as a "Graygate" appears to employ plural but
; 20 separated metal~plastic-metal sandwich seals around the valve stem and in a
bonnet pocket but the valve is of the non-rising stem type wherein the
problem of an axially moving skem does not exist, the metal rings are not of
the dished type, are not coined at their peripheries when in use.
It is believed that the valve of the present invention can be used
without leakage in environments of higher pressure and over a wider temperature
range than the valves discussed above.
Stacked dished packing rings for a pipe hanger are disclosed in
; United States patent number 2,417,181 - Sandilands, but here again there is
no relative axiaI motion of ~he members being sealed, just a static seal, and
the seal does not comprise rings of solid luhricant between dished metal rings ~:
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that are flattened by the compression means, the latter appearing to be
correlative in shape to that of the packing rings.
Difficulties experienced with dished metal-to metal seal rings of
the type disclosed in United States Patent No. 2,992,840 to Reynolds et al
are discussed in Quraforementioned United States Patent No. 4,056,272.
The tubing hanger seals disclosed in Patent No. 4,056,272 are of
various forms, including frusto conical metal rings flattened to some extent
by compression means, but only a static seal is formed, there being no
relative motion of hanger and well heat. In one embodiment ~sold over a
year prior hereto) the seal is between an inner cylindrical surface and an
outer conical surface, there is only one metal ring and no non-metallic
ring, and the metal ring is rounded and coined on both its inner and outer
peripheries adjacent its convex surface. Other embodiments disclosed in
this patent are not believed to have been offered for sale over a year
prior hereto and also differ in various respects from the seal of the
present application.
According to one aspect of the invention, there is provided a valve
including a hollow body having a flow path therethrough, balanced rising
stem gate means in the body reciprocable to control fluid flow through the
body and including actuator and balance stems extending through ports in
the body from the inside thereof, there being an annular pocket having a wall
in the body around each stem, each of said walls being substantially parallel
to the corresponding one of said stems, seal means in each pocket, and plug
means engageable with each seal means for compressing said seal means, each
seal means including at least one dished metal ring gasket and one sandwich
ring adjacent thereto made of a more compliant material, each of said
: dished metal ring gaskets being deformed at its peripheral edges into metal-
: to-metal sealing engagement between the corresponding actuator and balance
stems and said walls of said pockets upon compression of said seal means by
said plug means.
According to another aspect of the invention there is provided a
valve including a hollow body having a flow path therethrough and a port
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therethrough, rising stem gate means in the body reciprocable to control
fluid flow through the body and including an actuator and a stem extending
through the port in the body from the inside thereof, there being an annular
pocket in the body around the stem, the pocket having a wall, said wall
being substantially parallel to said stem, seal means in the pocket, and
a packing gland engageable with the seal means for compressing the seal
means, the seal means including at least one dished metal ring gasl~et and
one sandwich ring adjacent thereto made of a more compliant material than
the metal ring gasket, said dished metal ring gasket being deformed at
its peripheral edges into metal-to-metal sealing engagement between said
stem and said wall upon compression of said seal means by said packing
gland.
For a detailed description of a preferred embodiment of the
invention reference will now be made to the accompanying drawings wherein:
Pigure 1 is a vertical section through a valve embodying the
~ invention; -
Figure 2 is a fragmentary sectional schematic view taken in the
same plane as Figure 1 but to a larger scale and showing a modified form
of the actuator stem seal means in which the stack of frusto conical metal
seal rings point away from the pressure inside the valve;
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Figure 3 is a fragmentary vertical sectional view through the
actuator stem seal means of a modified form of valve in which the stem seal
means employs only two frusto conical metal seal rings;
Figure 4 is a view similar to Figure 3 except showing the balance
stem seal means of the modified form of valve;
Figures 5 and 6 are fragmentary sectional views of the modified
form of valve but to a larger scale and showing the pocke~s of the seal means
for the actuating stem and balance stem respectively;
Figures 7 and 8 together form an elevation of the actuator stem
of the modified form of valve (the blanace stem is similar as respects the
subject seal means and is not illustrated separately);
Figures 9 and 10 are an axial sectional view and an end view of the
seal compression plug for the balance stem seal means;
Figures ll and 12 are axial sectional views of the compression ring
and support ring for the stem seal means ~both actuator stem and balance stem
seal m~ans) of the modified form of valve;
`Figures 13 and 14 are plan and side elevational views of an elastic
ring of solid lubricant, e.g. "Molly-Teflon" (trademark) dimensioned for the
modified form of valve shown in Figures 3 through 12;
Figures lS and 16 are an axial sectional view and an enlarged
fragmentary sectional view taken on the same plane showing a frusto conical
metal seal ring dimensioned for the modified form of valve shown in Figures 3
through 14; and
Figure 17 is a schematic view depicting the mode of operation of
the stem seal means of the invention.
Referring now to Pigure 1 there is shown a val~e including a hollow
body having a chamber part 21 and a bonnet part 22 secured thereto by studs
23 and nuts 24; and sealed by suitable sealing means 25. Passages 26, 27 in
the chamber part provide a path for fluid flow into and out of the chamber.
Seats 29, 31 mounted at the inner ends o~ passages 25, 27
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cooperate with a pair of ported gates 33, 35 which control flow of fluid
(eOgO water~ oil~ gas) through the valveO Plastic sealant material is
stored in reservoirs 37~ 39 and sealant is automatically supplied through
the sealant distribution passages 41g 43 to the gate-seat and seat neck-
body interfaces to effect sealing, as described in the above mentioned
B patents~ ica-~-}~. The valve is rated at 257000 psi working
pressure and may be tested at up to 37~500 psi~
me gates are reciprocated by generally cylindrical actuating
stem 45 between the closed posi~ion shown in Figure 1 and an open position
in which the gate ports 47~ 49 and the bridge ring 51 thereacross are in
register with the ports 53~ 55 in the valve seats. The upper end of
the actuating stem extends out of the valve chamber through port 57 in
the bonnetO Seal means 59 in accordance with the invention seals between
the stem and a cylindrical pocket 61 in the bonnetO Seal means 59 is
compressed in pocket 61 by means of screw plug 63 which is screwed into
internally threaded neck 65 on the top of the bonnetO Bleed port 67
allows fluid to escape from between the pocket and the plugr
The exterior of bonnet neck 65 is also threaded and receives a
bearing cap 69 screwed thereto~ Actuator nut 71 screwed onto the threaded :~
upper end of actuator stem 45 has a flange 73 disposed'between axial thrust
bearings 75~ 77; the bearings engaging also the top of plug 67 and the,
upper end of cap 69. Cap 69 is sealed to the nut 71 by 0 ring seal 730 :
Hand wheel 75 has a noncircular aperture 77 fitted over a correlatively
shaped portion 79 of the actuator stemO The wheel is held in place by
retainer nut 81 screwed to the upper end of actuator nut 71. A bleed port
83 allows fluid to escape ~rom between the actuator nut and the upper end
85 of the actuator stem~
To the lower ends of the gates is connected a generally
cylindrical balance stem 91 which extends out of the valve chamber through
port 93`. S~al means 94 in accordance with the invention seals between
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the balance stem and a cylindrical pocket 95 in the valve body~ Seal
means 94 is compressed in pocket 95 by means of screw plug 97 which is
screwed into threaded socket 99 coaxial with port 93 and pocket 95. A
bleed port 101 allows fluid to escape from between the end of the plug
97 and the end of the balance stem.
When hand wheel 75 is turned~ actuator nut 7 turns and causes
actuator stem 45 to raise or lower the gates 33~ 35 to which it is connected
by Tee head 103, This in turn causes balance stem 913 connected to the
gates by loose fitting head 105~ to move up or downO There is thus relative
axial motion between each of the stems 45, 91 and the respective one of
the stem seals means 59~ 940 The seal means must remain tight during such
relative motionO Seal means 59~ 94 therefore fall in the class of sliding
seal means as distinct from the static seal means 25 between the bonnet and
chamber parts of the valve body where no relati~e motion occurs.
Seal means 59~ 94 are alikeg so only one need be described in
further detail. Seal means 94 includes a stack of three frusto conical
metal ~ing gaskets 111 between which are sandwiched elastic solid lubricant
rings 113 of lower elastic modulus than the metal ring gaskets~ the
latter preferably being made of steel, as described in the aforementioned
20 patents ~-d- pp~DeetD~t~ in the bottom of the pocket and adjacent the
compression plug 97 are provided base and follower adapter rings 115~ 117
which engage flush with and are correlative to the bottom of the pocket and
the end of the plug and whose opposite faces are cones having the desired
angles for the metal ring gaskets in their final assembled condition~
As will be explained in more detail hereinafter~ in their relaxed states
the metal ring gaskets are more sharply conical~ iOeO have smaller cone
angles~ than in the assembled condition shown in Figure lo If desired~ one
or both of the adapter rings may be omitted~ the bottom of the pocket and/
or the end of the plug being provided with a conical surface of the desired
cone-angle and area.
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The me~al ring gaskets should be made of softer metal than the valve
stems in order not to gall the stems. For like reason, the metal gaske~s
should not be flattened during assembly more than just enough to reduce their
inner diameters and expand their outer diameters into moderate coining
engagement with the pocket and stem and the coined sdge of the inner periphery
of each metal gasket is rounded, preferably with a radius equal to about half
the gasket thickness, e.g. O.n2 inch radius for a gasket that is 0.04 inches
thick.
Some examples of materials suitable for the sandwich rings 113 are
sold under the ~rademarks "Teflon" (te~ra fluorethylene polymer), "Molly-
Teflon" (like Teflon but including about 15 percent MoS2 (molybdenum sulfide)
and "Graphoil" ~compacted graphite). These materials rub off onto the stem,
filling the low places and forming a film overall and lubricating the areas
of contact between stem and metal gaskets. It may be noted at this point that
it is only the seal between stem and ring gaskets that is a sliding seal~ the
seal between gaskets and pocket being static.
Since the sandwich rings will be subjected to the temperature and
chemical activity of the fluid being controlled by the valve as well as to the
ambient temperature and medium in which the valve is to operate, the sandwich
material should be resistant to expected chemical action and expected tempera-
ture ranges, e.g. 300 degrees Fahrenheit down to ten degrees below zero F. or
even lower. Materials suitable for a range extending down to 75 degrees below
zero F. would be desirable.
; The sandwich material must be sufficiently elastic to withstand,
without breaking up, the stresses required to flatten the metal gaskets.
Preferably the sandwich rings are initially of rectangular configuratioll, for
ease of manufacture, rather than of their final assembled cross-section, so
they must deform (preferably elastically but at least plastically~ without
disintegration sufficientl~ to allow such change of shape.
Although the coined metal ring gaskets form metal-to-metal
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seals with the stem and pocket, it will be understood that upon motion of the
stem the gasket inner peripheries will not instantaneously and perhaps never
Xurther flow plastically to conform to the newly adjacent stem surface and
that during the interim the sandwich material may flow into an~ temporary gaps
to prevent leakage. The sandwich material should therefore preferably have
the ability to flow elastically, like rubberJ into such gaps. An elastomer
such as "Teflon" is therefore the preferred material. If lubrication is deemed
less important, a material such as "Hi Car"* could be employed. Although
elastic material is preferred for the sandwich material, soft plastic metal
such as lead might be employed. A composite stack, e.g. of "Molly-Teflon"*
and "Graphoil"* may be used.
It will be noted that in ~igure 1 the metal gasket cones point
toward the pressure being sealed against. ~or a stem seal this may be pre-
ferred, although when sealing between parallel surfaces the inner and outer
peripheries of the seal are similarly engaged and hence reversible. The
inner and outer peripheries of the ring gaskets may be viewed as forming lip
seals adapted respectively to seal against pressure directed against the
convex and concave faces of the gaskets. By pointing the cones toward the
pressure, the inner peripheries o the cones become effective as lip seals
and it is at the inner peripheries where a sliding seal must be formed.
The sandwich rings 113 should make an interference fit with both
the stem and pocket, e.g. several thousandths of an inch diametral inter-
ference. The pocket and stem need employ only ordinary smooth machine finishes
comparable with those ordinarily used for elastomer packings.
~ lthough it is preferred to use a stack of three metal gaskets with
two elastic lubricant rings sandwiched therebetween (triple decker) in order
to provide back up, a pair of metal gaskets (as shown in the modification
described hereinafter) works well. I~ an open sandwich, i.e.
*Trademark -8-
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one metal gasket and one elastomer lubricant ring is employed disposed on
the fluid pressure side of the metal gasket, a seal can be effected but
the elastomer tends to flow into the crack between the stem and the port
in the bonnet or chamber part of the body~ necessitating tightening of the
compression plug at intervals~ Use of plural gasket rings wholly enclos-
ing the sandwich rings prevents such extrusion since there is 7ero gap
between the metal ring gaskets and the stem and pocketO
In order to prevent leakage despite cycles of high and low
pressure the compression plugs are tigh~ened to preload the seals to a
stress higher than the highest expectant fluid pressure will cause. Since
in the case of a quick temperature change~ eOg. the sun coming out in the
artic or in the desert9 the metal expands faster than the elastomer~ the
preload should be even greater than that required to equal the stress of the
pressure fluid~ e~gO twice that stress~ in order to prevent relative move-
ment of the gasket rings~ sandwich rings~ and the pocket and stemO Such
a high preload may be called a super preload~ Typical makeup is with a
torque of 600 to 900 pound-feet on the compression plugs, hereinafter
depicted in more detail0
The tolerance for the diameters of the stem and gaskets and pocket
may be plus or minus 0.005 inch.
The ring gaskets are not Bellville springs~ which would be too
hard and would gall the stemsO Rather they are~ eOg~ annealed (austenitic)
stainless steel (316 etcO)~O They must be able to coin without imprint on
the stem (which may be only 30 Rockwell hardness~~O
The adapter rings 115~ 117~ if used~ may be of fairly hard
material such as 4140 steel~ but should make a close fit with the pocket to
insure non-contact with the stem upon turning of the compression plug.
The stem material may~ for example be K-Monel~ but a comparable
steel would be suitablea
The body (chamber part and bonnet part) may be made of any steel
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conventionally used for high pressure valves.
Referring now to Figure 2 there is shown a schematic view of a
reverse pointing triple gasket actuator stem seal, the half of the drawing
at the left depicting the seal in unloaded condition~ the half of the
drawing at the right showing the seal as it appears when loadedO Parts
similar to the parts of Figure 1 are given like numbers but primed. The
follower ring 117~ is provided with sockets 118 to facilitate removal~
Referring to Figures 3 and 4 there is shown the stem seal
constructions of a modified form of valve wherein but two metal gasket
rings and one sandwich ring are employed for each stem sealO These are
numbered the same as in Figure 1 except double primedO
Figures 5-16 show typical materials finishes~ tolerances and
dimensions for the pockets~ stems7 seal compression plugs~ adapter rings~
sandwich rings7 and metal ring gaskets~ for the stem seal means of the valve
of Figures 3 and 4O
Figure 17 is a schematic view of a stem seal means employing only
two metal ring gaskets 1111~ and one sandwich ring 11311', without any
adapter rings~ the faces 201~ 203 of the pocket and compression plug being
formed with cone angles the same as desired for the ring gaskets when
assembled and loadedO The rounded edges 205 on the inner edges of the metal
rings on their concave sides appear clearly in this figure at the left
hand side depicting the unloaded condition of the seal means~. The change
in shape of the sandwich ring and the metal rings to conform to the conical
faces of the pocket and plug is illustrated by comparing the left hand
side of the figure with the right hand side which illustrates the loaded
condition of the seal means~ Note also that the metal rings do not engage
the stem or sides of the pocket prior to loading and that the outer
periphery of the sandwich ring is initially smaller than the pocket inner
diameter~ but the sandwich makes a tight (interference) fit with the stem
even before loading~ e.g~ several thousandths of an inch diametral
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interference. Figure 17 also illustrates the coining (plastic metal flow)
which takes place on both the inner and outer peripheries of the metal
ring gaskets, i~e~ not only at 205 but also at 2070
While preferred embodiments of the in~ention have been shown and
described~ many modifications thereof can be made by one skilled in the
art without depar~ing from the spirit of the inventionO For example seal
means employing a stack of more than three metal gaskets with interposed
sandwich rings could be used. Auxiliary hydraulic loading means can be
pro~ided for further coining the metal ring gaske~s without further turning
of the screw plugso
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