Background of the Invention This invention relates to a ball valve and more partiσularlv to an improved metal seat desi n for a so-called floating ball valve. Floating ball valves include a spherical ball -"-alve member mounted within a valve chamber of the valve bodv ^f or limited floating movement between upstream and downstream seats on opposed sides of the ball valve member. As compared with so-called trunnion mounted ball values in which the spherical ball valve member is mounted on upper and lower trunnions for rotation and thus is fixed against anv axial movement along the longitudinal axis of the flow passages, a floating ball valve moves in a direction along the longitudinal axis of the flow passages between opposed seats and is limited by such seats to a relativelv small predetermined axial movement. As a result, when the ball valve member is in closed position and a high inlet fluid pressure exists, the ball valve member is moved against the downstream seat under a substantial force proportional to the inlet fluid pressure.

One of the problems associated with metal seat designs for floating ball valves is in the design of a seat which seals effectively at low fluid pressures, such as 5 psi, ^or example, and also seals effectivelv at high fluid pressures, such as 2000 psi, for example.

Heretofore, various tvpes of metal seats have been provided for floating ball valves including metal seats which shift or rock into a sealing relation upon the application of a high fluid pressure against the ball member, with the seat recess being formed or shaped to accommodate or assist such movement. For example, U.S. Patent No. 4,385,747 dated Mav 31, 1983 shows a metal seat mounted within a recess for facilitating movement of the seat under certain pressure conditions. A.n example of another metal seat construction for a floating ball valve is shown in U.S. Patent No. 4,557,461 dated December 10, 1985 which has a metal seal of a substantial solid cross-section with a tapered and flexible lip extending therefrom for sealing against the ball valve member at low temperatures. While the lip is flexible, the remainder of the metal seal does not appear to be flexible to anv significant degree.

SUMMARY QV THE INVENTION The present invention is directed to a floating ball valve having an improved metal seat design and an improved mounting means for the stem utilized for rotating the floating ball valve member. The metal seat design includes a one-piece metal seat mounted within a valve bodv recess defined bv a pair of surfaces at right angles to each other. The metal seat comprises a rear bodv portion of a generallv uniform thickness between parallel planar faces or surfaces and acting in a manner similar to a Belleville spring. A lip about the inner circumference of the metal seat bodv portion is spaced from a rear planar shoulder of the recess under low pressure conditions but engages the ball valve member in sealing relation.

A high pressure bearing portion of the metal seat extends from the body portion in a direction longitudinallv of the flow passage and is spaced from the ball valve member at low pressure conditions but engages the ball valve member under high pressure conditions to provide a sealing relation while also acting as a stop for limiting floating movement of the ball valve member. A relativelv small thickness

connecting portion of the seat which extends between the body portion and the bearing portion flexes upon the ball valve member engaging the bearing portion at high pressure conditions and exerts a seating force against the bodv Oortion for tightlv sealing the rear surface of the bodv Oortion against the rear shoulder of the recess in metal-to-metal relation. The bearing portion of the metal seat is spaced from the ball valve member a distance less the spacing of the lip from the shoulder of the recess therebv to protect the lip from excessive force exerted bv the ball valve member under verv high fluid oressures. A.s indicated, the bodv portion of the metal seat acts as a Belleville spring and its inner lip provides sealing against the ball al e member at low fluid pressures as low as around 1 Dsi while spaced from the adiacent shoulder of the recess.

Another feature is in the stem mounting means in which aligned openings in the valve bodv and the outer plate for receiving the stem include an inner packing about the stem and an adiacent Belleville washer exerting a continuous generallv uniform compressive loading against the packing. The opening in the outer plate outwardly of the Belleville washer and packing has an outer thrust bearing therein about the stem and is compressed independently of the packing under a predetermined light loading between a stem shoulder and the outer plate bv an adiusting nut threaded onto the stem. The thrust bearing mav be easilv inserted or replaced without disassemblv of the packing and is not exposed to lading within the valve chamber since mounted outwardlv of the packing.

It is an obiect of this invention to provide a one piece metal seal for a floating ball valve which functions in a manner generallv similar to a Belleville spring and fits within a recess in the valve body formed between a pair of surfaces at right angles to each other.

It is a further obiect of the invention to provide such a one piece metal seat for a floating ball valve in which the seat has a body portion of generally uniform thickness which includes a low pressure flexible lip about its inner

circumference for sealing against the ball valve member at low fluid pressures and a high pressure flexible bearing portion extending from the bodv nortion for sealing at high fluid pressures while spaced from the ball valve member at low fluid pressures.

Another obiect of this invention is to provide an improved stem mounting means for a floating ball valve utilizing a Belleville spring for exerting a σompressive loading against an inner packing, and an outer thrust bearing outwardly of the Belleville spring and packing positioned between a shoulder on the stem and an outer plate.

Other ob ects, features and advantages of the invention will become more apparent after referring to the following specification and drawings.

BRIEF DESCRIPTION OF THE DRAWINGS Fiσure 1 is a longitudinal section view of a ball valve structure comprising the present invention;

Figure 2 is an end elevation of the ball valve structure shown in Figure 1 taken generallv along line 2-2 of Figure 1;

Figure 3 is an enlarged sectional view in perspective of the upper portion of the valve illustrating the stem and adiacent parts; Figure 4 is an enlarged fragment of Figure 1 showing the ball valve member in sealing engagement with the metal seat under a low fluid pressure condition; and

Figure 5 is a view similar to Figure 4 but showing the ball valve member in engagement with the metal seat under a high fluid pressure condition.

DESCRIPTION OF THE INVENTION Referring now to the drawings for a better understanding of this invention, a spherical plug or ball valve comprising this invention is indicated generallv at 10 including a main body portion 14 and an end body portion 1?. bv a pluralitv of threaded bolts 16. For connecting ball valves or ball valve structure 10 within a flowline, flanges

18 of a flowline 19 fit on opposed ends 20 of body portions 12 and 14 and nut and bolt combination 22 clamp ball valve structure 10 tightlv therebetween.

Body portion 14 has an inlet opening 24 and bodv portion 12 has an outlet opening 26. An inlet flow passage is indicated at ^* >P and an outlet flow passage is indicated at 30. Body portions 12 and 14 define an enlarged diameter valve chamber at 32 and a ball valve member 34 is mounted within chamber 32 for floating movement. A stem generallv indicated at 36 has a handle 38 mounted thereon and is adapted to rotate ball valve member 34 between open and closed positions relative to flow line 19.

Ball valve member 34 has a spherical outer surface 40 and a central bore 42 therethrough which is in axial alignment with the longitudinal axis of flow oassages 28 and 30 in open position. A slot 44 is provided in the upper surface of ball member 34. Stem 36 has a lower end 46 fitting within slot 30 and permitting longitudinal movement of ball member 34 in the closed position thereof. Coacting flats defined by slot 44 and lower end 46 effect rotation of ball member 34 upon rotation of stem 36.

Stem 36 includes an intermediate large diameter stem section 48 adjacent lower end 46, an intermediate diameter stem section 50 adiacent stem section 48 defining an annular shoulder 52 therebetween a cvlindrical threaded section 54 adiacent stem section 50, and an upper end threaded section 56 adjacent cylindrical threaded section 54. Upper end threaded section 56 has a pair of opposed planar or flat surfaces 58 connected bv arcuate externally threaded surfaces 60.

Valve body portion 12 has an upper opening or bore receiving valve stem 36 defining a small diameter intermediate portion 62, an intermediate diameter inner portion 64, and an enlarged diameter outer portion 66. A flange 68 is formed between intermediate bore portion 64 and large diameter bore portion 66. A collar 70 integral with stem 70 is spaced from flange 68 and remains spaced from flange 68 even under the application of high fluid pressures within valve chamber 32.

For holding stem 36 within bodv portion 1° and slot 30, an outer clamp plate 2 is secured to bodv portion bv a plurality of threaded bolts 74. Plate 72 has a bore therethrough defining an inner large diameter bore portion 78, and an outer small diameter bore portion 80. For sealing about stem 36, a packing 82 fits within enlarged diameter bore portion 66 of bodv portion 12 about large diameter stem section 48. A follower 84 is positioned over the outer end of packing and a pair of Belleville washers 86 fitting within large diameter bore portion 76 of plate 72 are positioned between follower 84 and plate 72 for continuously exerting a downward or inner force against follower 84. Washers 86 have inner marginal portions 87 exerting a downward force on follower 84 and outer marginal portions 89 exerting an opposed force on plate ⁷ with follower 84 compressing packing 82 between shaft 36 and bodv portion 12. Washers 86 are of an outer diameter substantially larger than the outer diameter of packing 82 and exert a pressure on packing 82 greater than the maximum pressure within valve chamber 32 therebv to provide an inner σompressive force against packing 82 at all times.

For exerting a downward or inward loading on stem 36, a thrust ring 88 is mounted within intermediate bore portion 78 of plate 72 and fits against shoulder 52. Thrust ring 88 mav be formed of a suitable plastic material, such as polytetrafluoroethvlene, which will melt or sublimate at a temperature of about 70 °F. A nut 90 is threaded onto stem 36 over plate 72 for maintaining a predetermined relationship between thrust ring 88 and shoulder 52. " Since stem 36 is rotated relative to thrust ring 88, a relative light loading of thrust ring 88 is normally provided. A stop plate 92 has a generally rectangular opening 94 thereon which receives stem 36 and rotates with stem 36 with plate 58 of stem 36. A suitable washer 98 and spacer fit over handle 38 and a securing bolt 99 is threaded within an internallv threaded opening in the extending end of stem 36 for securing handle 38 thereon. Stop late 92 engages bolts 74 at the fully open and fullv closed positions of ball valve member 3 .

Follower 84 exerts a continuouslv and generallv uniform loading against packing 8? even in the event of wear on packing 82 as a result of the force exerted bv Belleville springer 86. Thrust ring 88 is positioned outwardlv of packing 2 and thus controls the position of stem 36 'independent!v of the force applied to packing 82 by Belleville spring 86. Further, thrust ring 88 limits the outward movement σf stem 36 upon high fluid pressures in valve chamber 32 and prevents contact of collar 70 with flange 68. However, when thrust ring 88 is consumed by high temperatures, such as mav be generated by a fire or the like, stem 36 mav be moved upwardlv by high pressure within valve chamber 32 with stem collar o contacting flange 68.

Cap screws 74 hold plate 72 tightly against bodv portion 1° and nut 90 is lightlv tightened for providing the desired frictional contact between shoulder 52 and thrust ring 88 upon rotation of ball valve member 34 between open and closed positions. Thus, the σompressive loading of thrust ring 88 can be increased independentlv of- and without compressing packing 82. Also, thrust ring 88 can easilv be inserted or replaced without removal of packing 82 and is not exposed to ladings within valve chamber 32 which might be corrosive.

Recesses 100 adjacent valve chamber 32 are provided in the valve body about inlet flow passage 28 and outlet flow passage 30. An annular upstream metal seat 102 is mounted in recess 100 about inlet flow passage 28 and an annular downstream metal seat 104 is mounted in recess 100 about outlet flow passage 30. Recesses 100 and seats 102, 104 are generally identical and for the purpose of illustration, onlv the downstream seat 104 is described in detail as shown in Figures 4 and 5.

Referring now particularly to Figures 4 and 5, recess 110 is defined bv an outer peripheral surface 106 which extends in a concentric relation to the longitudinal axis of the associated flow passage and a radial planar surface 108 forms a shoulder extending perpendicularly to surface 106. Metal seat 104 of a one-piece metal construction fits within recess 100 adiacent surfaces 106, 108 and comprises a bodv

portiσn 110 of a generallv uniform thickness T between generally parallel planar surfaces 112 and 113 which extend in a generallv radial direction.

Rear planar surface 112 provides a sealing surface against shoulder 108 which at low fluid pressure seals ^• generallv at the corner of recess 100 as shown in Figure 4, but at high fluid pressure seals along substantiallv the entire face of shoulder 108 as "shown in Figure 5. Body portion 110 acts in a manner similar to a Belleville spring and has a lip 114 at its inner circumference which is rounded at 116 for engaging spherical surface 40 of ball valve member 34. Lip 114 is spaced a distance D from the opposed shoulder 108 during normal operation in the open position of valve member 34 and during low fluid pressure operation in the closed position of ball valve member 34. A high pressure seat or bearing portion 118 of metal seat 104 is connected to body portion 110 and has an arcuate bearing or sealing surface 120 adapted to engage adjacent spherical surface 40 of ball valve member 34 under high fluid pressure conditions. Seat portion 118 has an outer circumferential surface 122 in opposed relation to outer periphery 106 and arcuate sealing surface 120 is of a contour generally the same as the adjacent spherical surface 40 of ball valve member 34. At low pressure conditions, ball valve member 34 is spaced a distance Dl from bearing surface 120 in axial direction parallel to the longitudinal axis of flow passages 28 and 30 as shown in Figure 4. Distance Dl under all conditions of operation is less than distance D to act as a stop for ball valve member 34 to minimize wear or damage to lip 114 in forcing lip 114 against shoulder 108. For example, for a ball valve of four inches internal diameter Dl may be .005 inch and D mav be .008 inch. In anv event, D would be at least .001 inch greater than Dl.

An outer annular groove 126 in seat 34 defines a connecting portion 128 of seat 34 extending between bearing portion 104 and body portion 110 in a direction generallv parallel to the longitudinal axis of the flow passages 28 and 30. Connecting portion 128 is flexible and preferablv has a generally uniform thickness Tl between around 25% and

65% of the thickness T of bodv portion 110 with an optimum thickness of around 45% of thickness T. Thus, under high pressure conditions as shown in Figure 5, connecting portion 128 flexes but vet has sufficient rigiditv to exert a strong force against bodv portion 110 for urging rear sealing surface 112 into tight sealing relation against shoulder 108.

As shown in Figure 4 for a low pressure condition, such as 50 psi for example, rounded end 116 is in substantiallv line contact relation with spherical surface 40 of ball valve member 34 with lip 114 spaced a distance D from adiacent recess shoulder 108, and bearing surface 120 is spaced a distance Dl from the adjacent spherical surface 40 of ball valve member 34. Body portion 110 is in metal-to-metal sealing relation with shoulder 108 adjacent the corner of recess 100 formed at the juncture of shoulder 108 with outer circumferential surface 106.

As shown in Figure 5 for a high pressure condition, such as 1000 psi, for example, floating ball valve member 34 in closed position moves downstream against lip 114 to urge lip 114 rearwardlv with ball valve member 34 contacting bearing surface 120 before lip 114 is pressed tightlv against shoulder 108. Further, ball valve member 34 through bearing portion 104 and connecting portion 128 urges the rear face or surface 112 of bodv portion 110 into tight metal-to-metal sealing relation with shoulder 108 with connecting portion 128 being slightly flexed. The higher the fluid pressure acting against ball valve member 34, the higher the sealing and seating forces exerted against and bv metal seal 104 against shoulder 108. Metal seal 104 mav be formed of various types of corrosion resistant metallic materials, such as a titanium, for example, which has a modulus of elasticity of around 15 million.

Thus, metal seat 104 while of a substantial strength is relatively flexible in a radial direction between lip 114 and seat portion 118 and will seal adequately even with substantial manufacturing tolerances in shoulder 108 and outer peripheral surface 106 of recess 100. Upon the exertion of a high fluid pressure against ball valve member

34, bearing surface 120 is contacted bv ball valve member 34 before lip 114 engages shoulder 108 to restrain the force exerted against low pressure lip 114 bv ball valve member 34. Connecting portion 128 transmits the force to body portion 110 for providing a tight sealing force which ^• increases in relation to an increase in fluid pressure. Metal seat 104 is oarticularlv adapted for fitting within a recess defined bv a pair of bodv surfaces at right angles to each other. A seoondarv stem seal is provided bv collar ^0 against flange 68 when high temperature consumes or deteriorates thrust bearing or ring 88 as internal pressure acting against stem 36 forces collar 70 against flange 68 to provide metal to metal engagement. while a preferred embodiment of the present invention has been illustrated in detail, it is apparent that modifications and adaptations of the preferred embodiment will occur to those skilled in the art. However, it is to be expressly understood that such modifications and adaptations are within the spirit and scope of the present invention as set forth in the following claims.