VALVE

Abstract: A diaphragm-type valve uses a multiple annular metal diaphragm (36) welded about its inner periphery to a valve operating stem (34). The diaphragm is sealingly clamped about its outer periphery to the valve body and is also clamped about its inner periphery at a location spaced outwardly of the weld to prevent the weld from being subjected to flexure stresses during valve actuation. The outer periphery of the diaphragm (36′) may be welded to the valve body (10′) outwardly of the outer clamp. The actuating assembly (20) is arranged to produce non-rotary, reciprocatory movement of the operating stem (34) through a bonnet mounted rotary actuator (116). A stem tip seal (16) comprises a metallic seal ring (152) backed by a PTFE ring (158) and surrounded by a harder plastics ring (160) held captive by a sleeve (166).

Description: VALVE. The present invention relates to stem tip seals for valves. US-A- 29 36154 discloses a stem tip seal for a shut-off valve comprising a valve member mounted for movement axially towards and away from an associated annular valve seat; a substantially cylindrical sleeve carried by said valve member and axially movable independently thereof; a substantially cylindrical rigid body situated within said sleeve to define an axially open annular chamber between said sleeve and said rigid body, the sleeve being axially movable independently of said rigid body and the rigid body having an outer diameter greater than the inner diameter of said seat, and a resilient seal ring located in said annular chamber and having an end face adapted to engage said seat as said valve member moves axially towards said seat. A stem tip seal according to the invention is characterised in that the valve member has a cylindrical end portion extending axially towards said seat, the diameter (d) of said end portion being less than the inner diameter of said seat; and the rigid body comprises a rigid ring slidably received on said cylindrical end portion; and in that a compressible ring is located about said end portion and between said rigid ring and said valve member for allowing said rigid ring to move axially inwardly relative to said resilient seal ring and said sleeve and for permitting compressive forces between said seal ring and said seat to increase after said rigid ring engages said seat during such inward movement. The compressible ring located between the rigid ring and the valve member allows the rigid ring to move axially relative to the seal ring and the sleeve and to allow the rigid ring to maintain contact with the seat while compressive forces between the seal ring and the seat increase. In accordance with a still further object, the sleeve has an end face configured to engage the seat with line contact as the valve member moves towards the seat. Further, the rigid ring is also preferably configured to engage the seat with line contact in the area closely adjacent the resilient seal ring. The invention is applicable to diaphragm-type valves. A diaphragm-type valve is one in which the valve chamber in the valve body is sealed off by means of a flexible diaphragm which flexes to permit a valve operator to displace a valve closure member. Such a valve is to be distinguished from a diaphragm valve which is a valve whose closure member is in the form of a flexible diaphragm. Diaphragm-type valves having a metal diaphragm are often used in systems handling toxic and dangerous fluids. The valves are preferred in such environments because the diaphragm can provide total hermetic sealing between the valve chamber or cavity and the valve operating mechanism. In accordance with a preferred aspect of the invention, there is provided a diaphragm-type valve which includes a valve body having an opening that extends inwardly from the exterior of the body to define a generally cylindrical valve chamber. The valve operating stem is positioned to extend axially into the valve chamber for engagement with a valve element and thereby form a seal assembly. The valve chamber is sealed by an annular flexible metal diaphragm whose outer periphery is clampingly joined to the body and whose inner periphery is welded to the seal assembly circumferentially thereof. The diaphragm assembly includes a plurality of relatively thin, annular metal elements positioned in aligned, juxtaposed relationship. First clamp means are provided for sealingly clamping the outer peripheral portion of the annular metal elements to the body circumferentially of the valve chamber. Second clamp means are provided for clamping an inner peripheral portion of the diaphragm to the seal assembly circumferentially thereof. The second clamp means are arranged to engage and clamp the annular elements at a point radially outwardly of the weld to prevent forces produced during flexure of the diaphragm from acting on the weld. Actuating means are provided for selectively moving the stem axially of the valve chamber without applying torsional loads to the diaphragm. The actuating means include a bonnet member through which the stem extends with co-operating surfaces between the bonnet member and the stem for permitting free axial movement of the stem while preventing axial rotation. A drive member is rotatably carried by the bonnet member and has threads in engagement with corresponding threads formed on the stem. A bonnet nut surrounds the bonnet member and the drive member and is threaded into the body to clanp the bonnet member and the diaphragm into sealed engagement with the body. Carried by the nut are means for continually biasing the drive member axially outwardly. In addition, a handle member is positioned over the bonnet member and is releasably joined to the drive member. In accordance with another aspect of the invention, both the stem and the nut extend axially outwardly of the bonnet member and the stem extends through an opening in the handle member so that the outer free end of the stem provides a visual indication of the position of the valve element. Accordingly, one object is the provision of a stem tip seal assembly which is particularly suited for use in diaphragm-type valves and other shut-off valves. Another object of the invention is the provision of a diaphragm-type valve wherein the diaphragm is welded and clamped to the operating stem or to the valve member in a manner which allows the weld to provide full hermetic sealing of the valve chamber while preventing flexure forces from acting against the weld. A further object is the provision of a diaphragm-type valve in which the operating mechanism permits free axial movement of the stem without transmitting any torsional loads through the stem to the diaphragm or the stem tip assembly. The invention is further described, by way of example, with reference to the accompanying drawings, wherein: Fig .1 is a sectional view of a diaphragm-type valve in accordance with the present invention; Fig .2 is an enlarged cross-sectional view of the valve chamber and stem tip assembly of the valve of Fig.1; Fig .3 is a greatly enlarged cross-sectional view showing the sealing portion of the stem tip assembly in closed position in engagement with the valve seat; Fig.4 is a cross-sectional view taken on line 4-4 of Fig.1; Fig.5 is an enlarged view of the circled portion of Fig.2; Fig.6 is an enlarged cross-sectional view of the circled portion of Fig.1; and Fig.7 is an enlarged cross-sectional view like Fig.6 but showing a modified arrangement for sealing the outer periphery of the diaphragm to the valve body. Referring to Fig.1, a valve in accordance with the present invention comprises a main body 10 having a generally cylindrical internal valve chamber 12 which is sealed at its outer end by a diaphragm assembly 14. Positioned within the valve chamber 12 and arranged to control flow therethrough is a stem tip seal assembly 16. The valve is moved between its open and closed positions by an operating assembly 18 including a handle member 20. In the embodiment under consideration, the main body 10 is formed of a suitable metal, such as stainless steel, and is provided with an inlet passage 20 and an outlet passage 22. Inlet passage 20 terminates in an upwardly open port 24 which is axially aligned with the generally cylindrical valve chamber 12. As illustrated, the valve chamber 12 is preferably formed with a stepped bore which includes a first cylindrical section 26 and an outer, somewhat larger diameter section 28. The inner end of the valve chamber 12 terminates in a conically shaped, inclined bottom wall 30 which defines an annular valve seat area about port 24. Mounted to extend axially into the valve chamber 12 is an operating stem member 34 which has the stem tip seal member 16 carried on its inner end in a manner subsequently to be described. The valve chamber 12 is sealed by the previously mentioned diaphragm assembly 14. In the embodiment under consideration, the diaphragm assembly 14 comprises a multiple layer metal diaphragm 36 which is formed generally as described in GB-A-2137738. Broadly, the diaphragm 36 is, as shown in Fig.5, formed as a plural layered diaphragm comprised of three separate annular metal disc elements 38,40 and 42. As shown, the disc elements 38, 40 and 42 are preferably of equal thickness and each disc element preferably is formed from Austenitic 316 stainless steel which has been heat treated to a hardness of not less than about 38 on the Rockwell C Scale. Referring again to Fig.2, the diaphragm 36 has its outer peripheral portion 44 received on a shoulder 46 formed at the juncture between cylindrical bores 26, 28. The diaphragm 36 is sealingly clamped to shoulder 46 by bonnet member 50 in a manner subsequently to be described. Referring particularly to Fig.6, the relationship between the shoulder 46 and the clamping face 52 of bonnet member 50 is shown in some detail. The particular clamping arrangement utilized is shown and described in more detail in the previously mentioned GB-A-2137738. In general, however, shoulder 46 and bonnet clamping surface 52 are provided with spaced-apart opposite flat and parallel circumferential surface areas 54 and 60, respectively, which provide primary clamping surfaces to clamp and grip the diaphragm inwardly from its outer periphery. A second pair of flat and parallel clamping surfaces 62 and 64 is also provided to clamp the diaphragm at a position axially and radially spaced from the primary clamping surfaces 54 and 60. The primary and secondary surfaces are separated by relatively sharp corners 66 and 68 across which the diaphragm 36 is bent axially. The corners 66 and 68 provide excellent sealing against the opposite faces of diaphragm 36. Preferably, the machining tolerances for the surface of the shoulder 46 and the associated clamping face 52 are selected such that the spacing between surfaces 54 and 60 will always assure maximum clamping action at this area as opposed to the clamping action between surfaces 62 and 64. This ensures that the primary diaphragm sealing occurs at surface 54 and disc element 56 to better accommodate valve purging. The outer periphery of the diaphragm 36 is further bent and clamped by secondary corners 72 and chamfered corner 70. These corners are effectively axially spaced from one another a distance less than the actual spacing between corners 66 and 68. Thus, the outer peripheral portion of diaphragm 36 is deformed to a greater degree than the deformation that takes place between corners 66 and 68. As fully described in the previously mentioned GB-A-2137738, this relationship provides an extremely effective peripheral seal for the diaphragm. Referring again to Figs. 2 and 5, the diaphragm 36 has a central opening 74 which is closely received about a vertically extending collar portion 76 formed on the main body 78 of the stem tip assembly 16. To seal between the stem tip body 78 and the inner periphery 74 of diaphragm 36, a continuous full penetration weld, as shown at 80, is provided completely about the inner periphery of the diaphragm to positively join and seal it to the body 78. In addition, the weld joins all layers of the diaphragm to also prevent any possible leak paths between the layers. Preferably, and in accordance with an aspect of the invention, means are also provided to mechanically clamp the diaphragm 36 to the body 78 at a location radially outwardly of the weld 80. In the embodiment shown, the stem tip body 78 is threadedly connected at 84 to the lower reduced diameter end portion 86 of stem 34. The clamping of the inner periphery of the diaphragm is accomplished by co-operation between an annular clamp ring 82 located beneath the larger diameter portion 88 of stem 34 and the upper surface of the diaphragm 36. As shown, the annular ring 82 has an inner open diameter 90 which is substantially larger than the inner diameter 74 of the diaphragm 36. This assures that, when the stem tip body 78 is threadedly tightened on the stem 34, clamping between the under surface of ring 82 and the upper surface of stem tip body 78 takes place at a location significantly outwardly of the weld 80. Preferably distance "D" is predetermined to be sufficiently outwardly of weld 80 to prevent any bending forces generated during reciprocation of the valve and flexure of the diaphragm 36 from being transmitted to the weld 80. This distance may, of course, vary depending upon the size and/or thickness of the diaphragm. Preferably, the upper surface 92 of stem tip body 78 is smoothly contoured away from the diaphragm as shown. Similarly, the under surface of the clamp ring 82 is also smoothly contoured away from the upper surface of diaphragm 36. This arrangement allows the clamping forces applied by clamp ring 82 to be concentrated in the area 94 and allows the diaphragm 36 to undergo the required deflection without being subjected to sharp bends or the like. The overall arrangement and operation of the operating assembly 18 can best be understood by reference to Fig. 1. The bonnet member 50 is provided with an outwardly extending flange-like portion 100 which is sized so that its outer periphery 102 is closely and slidably received in the bore section 28. A generally axially extending sleeve portion 104 extends upwardly from flange portion 100. Bonnet member 50 is clampingly retained in the enlarged bore 28 by a bonnet nut 106 which is threadedly received in bore 28 by co-operating threads 108. The upper end of the bonnet nut 106 is provided with suitable wrench flats 110 to permit the nut to be tightened and released from the bore 28. In addition, tightening the bonnet nut 110 causes the bonnet member 50 to be moved to the diaphragm clamping position previously discussed. The stem 34 extends axially through the bonnet member 50 and the bonnet nut 106 as shown. Preferably, the stem 34 is prevented from rotating relative to the bonnet nut by co-operating surfaces on the stem and the bonnet. Specifically, according to the subject embodiment, the stem 34 (as best shown in Fig. 4) includes a radially extending section 112 which has a generally hexagonal configuration. The bonnet member 50 is provided with a central opening 114 which is broached or otherwise machined to provide longitudinally extending grooves 115 arranged to closely but slidably engage the corners of the hexagonal configuration of portion 112. The grooves 115 thus permit free axial sliding of the stem 34 while preventing any rotational movement. Selective axial movement of the stem 34 is provided by an actuator 116 which has a generally cylindrical configuration with an outwardly extending flange 118. The lower end 120 of the actuator 116 is closely received and guided in a bore 122 formed in the sleeve portion 104 of bonnet member 50. The flange portion 118 is sized so as to be closely and rotatably received in the axially extending bore 124 of the bonnet nut 106. The length of the actuator 116 is such that an upper end portion 126 extends outwardly of the bonnet nut 110. Threads 128 are formed between the exterior of the stem 34 and the interior of the actuator 116. Preferably, the threads 128 are left-hand threads so that clockwise rotation of the actuator 116 produces inward or closing movement of stem 34. In the embodiment shown, the actuator 116 is continually biased in an outward direction by a spring wavy washer 130 positioned between the top of bonnet sleeve 104 and the under surface of flange 118. In addition, a bearing washer 132, formed from bronze or the like, is positioned between the top of flange 118 and the under surface of a radially inwardly extending flange 136 of bonnet nut 106. This arrangement firmly captures and holds the actuator 116 against axial movement while permitting it to have free driving rotation for adjustment of stem 34. Selective rotation of the actuator 116 is provided by handle member 20 which is joined to the outer end 126 of actuator 116. Many different types of handles could be provided; however, according to the subject embodiment, the handle 20 comprises a main handle body 138 which is moulded about a metal insert 140. Insert 140 has a centre bore 142 which is sized so as to be closely received on the outer end of actuator 116. A socket head setscrew 144 or the like is carried in the insert member 140 for connecting the handle 20 to the actuator 116. A suitable opening 146 is moulded or otherwise formed in the handle body 138 to provide access to the setscrew 144. Preferably, the stem 34 has an outer free end 148 which is of a length such that as the valve is moved to an open position the free end 148 of stem 34 extends outwardly of the handle body 138 to provide a visual indication that the valve is in an open position. The stem end 148 is sized such that, when the valve is in the closed position shown in Fig. 1 the top end of the stem is substantially flush with the top surface of handle 20. The structure and arrangement of the stem tip seal assembly 16 is shown in Figs. 2 and 3. The lower end of the stem tip main body 78 is provided with a circumferentially extending recess 150 which opens axially and radially of the body 78. The inner diameter d of recess 150 is slightly less than the diameter of port 24. Carried on the lower end of body 78 and slidably received on the inner wall of recess 150 is a metal seal ring 152. Ring 152 has a generally flat lower face 154 which terminates in an outer, relatively sharp corner 156. The corner 156 is arranged to engage the inclined bottom wall 30 of valve chamber 26 circumferentially about the port 24 as the valve moves towards a closed position shown in Fig. 3. Corner 156 thus provides a metal-to-metal generally line contact seal about port 24. Positioned axially inwardly of the ring 152 and captured between the rear of the ring and the axially facing surface 157 of recess 150 is a resilient ring or a washer member 158. In the embodiment under consideration, the ring 158 is formed from virgin polytetrafluoroethylene and is sized so as to substantially completely fill the area or space between ring 152 and surface 157. Positioned radially outwardly of ring 152 and 158 is a seal ring 160 formed from a suitable resilient, abrasion-resistant seal material, such as chlorotrifluorethylene or a filled polytetrafluoroethylene. For reasons which will subsequently be described, ring 160 has a greater stiffness than previously mentioned ring 158. The ring 160 is configured to substantially fill the axially open space between the inner rings 152 and 158 and the outer diameter of the body 78. Ring 160 has a radially inwardly extending portion 162 which extends under a radially outwardly extending flange 164 formed on ring 152. Portion 162 or ring 160 thus acts to axially retain ring 152 in position on body 78. Preferably, and for reasons subsequently to be discussed, the lower or seal face 167 of seal ring 160 is generally coplanar with, or slightly below the corner 156 of ring 152 when the rings are in their assembled position on body 78. The rings 152 and 160 are retained in position by a circumferentially continuous metal sleeve 166 which is closely and slidably received on the outer surface of body 78. Sleeve 166 extends downwardly about the outer circumference of seal ring 160 and includes an inwardly extending continuous flange portion 168 which extends under the axially outer portion of ring 160. The sleeve 166 is slidably retained on the body 78 by radially inwardly extending flanges or tabs 170 (see Fig. 2) which are bent inwardly over a shoulder on body 78. Additionally, and for reasons subsequently to be discussed, the continuous flange portion 168 is preferably inclined at an angle beta which is slightly greater than the angle of inclination alpha of end wall 30 of chamber 12. With the stem tip assembly 12 arranged as shown, a closing movement of the valve results in contact being made between the seat area and the end face 167 of the resilient seal member 160. As further closing movement takes place, the seal ring 160 is compressed and the outer corner 156 of rigid ring 152 engages the seat area radially inwardly of the seal ring 160. With further closing movement, the compressive forces acting between the seal face 167 and the stiffer resilient seal ring 160 increase. The forces between corner 156 of ring 152 and the seat also increase but to a lesser extent because the less stiff and more resilient ring 158 can more readily undergo compression to allow some rearward movement of ring 152 relative to body 78 and ring 160. This allows ring 152 to maintain firm engagement with the seat area while allowing the sealing pressures between surface 167 and the seat to be increased. Additionally, the compressive forces acting within ring 160 maintain a downward force on the sleeve 166 because of the flange portion 168. With the final closing movement of the valve, the lower edge of sleeve 166 engages the seat area with line contact circumferentially of seal ring 160. The seal ring 160 is thus confined between the inner rigid ring 152 and the outer sleeve 166. In addition, the inner ring 152 and the outer sleeve 166 make metal-to-metal line contact with the seat and totally confine the resilient seal ring 160. Fig. 7 shows a modified form of mounting and sealing for the outer periphery of the diaphragm to the valve body 10. In the Fig. 7 embodiment, like reference numerals differentiated by a prime suffix (′) have been used to identify parts corresponding to those previously described with reference to Figs. 1 to 6. The description of such parts is to be taken as equally applicable to those of the Fig. 7 embodiment unless otherwise noted. In particular, in the Fig. 7 embodiment, the shoulder 46′ is made flat without the stepped configuration of Fig.6. The diaphragm 36′ rests on the flat shoulder 46′ and is continuously welded to the shoulder by a fully penetrating weld 170 located relatively closely to the outer periphery of the diaphragm. This weld firmly attaches and completely seals the individual disc elements to each other and to the body 10′. The diaphragm is also clamped to the shoulder 46′ by a clamp face 172 which extends outwardly from bonnet member 50′ to provide a circumferentially continuous, relatively narrow clamping band located radially inwardly of weld 170. Preferably the face 172 extends generally parallel to shoulder 46′. The relationship between the weld 170 and the clamp surface 172 is such that the flexure forces produced in diaphragm 36′ during valve operation cannot be transmitted to the weld.

Claims: A stem tip seal for a shut-off valve comprising a valve member (78) mounted for movement axially towards and away from an associated annular valve seat (30), a substantially cylindrical sleeve (166) carried by said valve member (78) and axially movable independently thereof; a substantially cylindrical rigid body (152) situated within said sleeve (166) to define an axially open annular chamber between said sleeve (166) and said rigid body (152), the sleeve (166) being axially movable independently of said rigid body (152) and the rigid body (152) having an outer diameter greater than the inner diameter of said seat (30); and a resilient seal ring (160) located in said annular chamber and having an end face (167) adapted to engage said seat (30) as said valve member moves axially towards said seat; characterised in that the valve member (78) has a cylindrical end portion extending axially towards said seat, the diameter (d) of said end portion being less than the inner diameter of said seat (30); and the rigid body (152) comprises a rigid ring slidably received on said cylindrical end portion; and in that a compressible ring (158) is located about said portion and between said rigid ring (152) and said valve member (78) for allowing said rigid ring (152) to move axially inwardly relative to said resilient seal ring (160) and said sleeve (166) and for permitting compressive forces between said seal ring and said seat to increase after said rigid ring engages said seat during such inward movement. A stem tip seal as claimed in claim 1, wherein said sleeve (166) has an end face configured to engage said seat with line contact as said valve member moves towards said seat. A stem tip seal as claimed in claim 1 or 2, wherein compressive forces applied to said resilient seal ring (160) produce axially outwardly directed forces on said sleeve (166). A stem tip seal as claimed in any of claims 1 to 3, wherein said rigid ring (152) is positioned to engage said seat (30) substantially simultaneosuly with said resilient seal ring (160) as said valve member (78) moves towards said seat. A stem tip seal as claimed in claim 4, wherein said rigid ring (152) is configured to engage said seat (30) with line contact in the area closely adjacent said resilient seal ring (160). A stem stip seal as claimed in claim 4 or 5, wherein said seat (30) is inclined at a first angle (α) relative to the path of movement of said valve member (78) and wherein said sleeve (166) has an end face inclined at a second angle (β) to be engageable with said seat (30) in line contact as said valve member (78) moves towards said seat. A diaphragm-type shut-off valve having a stem tip seal as claimed in any preceding claim, and comprising a valve body (10) defining a valve chamber (12) which extends inwardly from the exterior of said body; said valve member (78) forming part of a seal assembly which includes a valve operating stem (34) extending from the exterior of said body axially into said chamber (12); and a diaphragm assembly (14) attached to said body (10) and to said seal assembly (34,78) for sealing said valve chamber (12) while permitting said seal assembly (34,78) to have limited axial movement in said chamber, said diaphragm assembly (14) being positioned to extend transversely of said valve chamber (12) with said seal assembly (34,78) extending axially there through, said diaphragm assembly (14) including a plurality of relatively thin, annular metal elements (38,40,42) positioned in superposed juxtaposed relationship. A valve as claimed in claim 7, in which the metal elements (38,40,42) are joined to said stem (34) by a continuous weld (80) extending about their inner periphery to form a unitary diaphragm (36), and in which first clamp means (46,50) sealingly clamp an outer peripheral portion of said diaphragm (36) to said body (10) circumferentially of said valve chamber, and second clamp means (78,82) sealingly clamp an inner peripheral portion of said diaphragm (36) to said stem (34) circumferentially thereof, said second clamp means (78,82) engaging and clamping said diaphragm (36) radially outwardly of the weld (80) to prevent forces produced during flexure of said diaphragm (36) from acting on said weld (80). A valve as claimed in claim 8, wherein the outer peripheral portion of the diaphragm (36) is welded to said body by a continuous weld (170) located radially outwardly of said first clamp means (46',50'). A valve as claimed in claim 8 or 9 , wherein said second clamp means comprises a pair of clamp members (78,82) positioned on axially opposite sides of said diaphragm (36), each of said clamp members being carried by said stem (34) and having opposed surfaces (92) which face said diaphragm (36) and which curve axially away from said diaphragm. A valve as claimed in claim 8, 9 or 10, wherein said second clamp means (78,82) includes an axially extending collar (76) which is received in the centre of said annular metal elements (38,40,42). A valve as claimed in claim 11, in which a portion of the valve member (78) positioned in said valve chamber (12) constitutes a portion of said second clamp means. A valve as claimed in any of claims 7 to 12, which further comprises a bonnet member (50) through which said stem (34) extends, with co-operating surfaces (114,115) between said bonnet member and said stem for permitting axial movement of said stem while preventing axial rotation; a drive member (116) rotatably carried by said bonnet member (50) in surrounding relationship to said stem (34) and having threads (128) engaging said stem for producing axial movement of said stem with rotation of said drive member; a nut (106) surrounding said bonnet member (50) and said drive member (116), said nut being threaded into said body (10) and clamping said bonnet member (50) to said body; bearing means (132) in said nut (106) engaged with said drive member (116) for preventing axial outward movement of said drive member while permitting axial rotation; and handle means (20) positioned over said bonnet member (50) and joined to said drive member (116) with said stem (34) extending axially through said handle means (20). A valve as claimed in claim 13, wherein said bearing means include co-operating shoulders on said drive member (116) and said nut (106) with a bearing ring (132) positioned therebetween. A valve as claimed in claim 13 or 14, wherein said nut (106) is axially received in the outer end (28) of said opening (26) and wherein the outer periphery of said diaphragm (36) is clamped between said bonnet member (50) and said body (10). A valve as claimed in claim 15, wherein said bearing means include spring means (130) for biasing said drive member (116) axially outwardly of said nut (106). A valve as claimed in claim 16, wherein said spring means (130) are located between said bonnet member (50) and said drive member (116). A valve as claimed in claims 16 or 17, wherein said drive member (116) extends outwardly of said nut (106). A valve as claimed in claim 18, wherein said bonnet member (50) includes a cylindrical portion (104) which extends into said nut (106). A valve as claimed in claim 19, wherein said bearing means includes a radially extending shoulder (118) formed on said drive member (116) and a co-operating radially extending shoulder (136) formed on said nut (106).

Inventors: KOLENC, TERRENCE JAMES, SCHEFFEL, GARY WILLIAM
Applicants: NUPRO COMPANY
Application year: 1987
Main classification: F16K41
IPC codes: F16K7, F16K1, F16K41