• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    "valve having a stem seal assembly, valve stem gasket assembly and seal ring? This invention relates generally to valve stem seals and in particular to a drained redundant stem seal system The valve of the present invention comprises: a valve body (13) defining a flow passage (15) and a body cavity (21) perpendicular to the flow passage, the valve body (13) defining additionally a stem opening (77) extending from an exterior of the body to the body cavity (21); a valve member movable between an open position and a closed position, the valve member blocking the flow passage in the closed position and allows flow through the flow passage in the open position; a valve stem (29) having a valve stem axis (25) coupled to the valve member, the valve stem (29) being valve (29) extends from the body cavity (21) to an exterior of the valve body through the valve stem opening (77) to move the valve member from the closed position to the open position; a first spring energized sealing ring (35a) positioned within the valve stem opening (77) to seal the valve stem (29) to the valve body; a second sealing ring (35b) positioned within the valve stem opening (77) to seal the valve stem (29) to the valve body; and a load ring assembly (99) mounted stationary and defining a valve body portion between the first seal ring (35a) and the second seal ring (35b) which insulates the first seal ring (35a) ) and the second sealing ring (35b) so that a force applied to the first sealing ring (35a) in a direction away from the second sealing ring (35b) is transferred to the load ring assembly (99). ).
    公开号:BR102012031584B1
    申请号:R102012031584-0
    申请日:2012-12-11
    公开日:2021-09-21
    发明作者:Rick C. Hunter
    申请人:Vetco Gray, Inc；
    IPC主号:
    专利说明:

    FIELD OF THE INVENTION
    [001] This invention relates in general to valve stem seals and, in particular, to a redundant valve-drained stem seal system. BACKGROUND OF THE INVENTION
    [002] A gate valve has a body with a central chamber that is intercepted by a flow passage. A drawer moves within the chamber between open and closed positions. The drawer has a hole through it that lines up with the flow passage while in the open position. The drawer can be of a split type, comprising two halves, or it can comprise a single slice. A rod extends in engagement with the drawer to move the drawer between open and closed positions. The chamber has a central portion, which is intercepted by flow passages, and a rod portion that extends from the central portion.
    [003] In one type, the rod extends in rotary engagement with a sleeve or threaded nut secured to the drawer. Rotating the rod causes the drawer to move linearly. In another type, the rod does not rotate. A threaded nut sleeve mounted on the valve cover engages the stem and, when rotated, causes the stem to move linearly. The sleeve and stem threads can slide against each other or they can employ balls between the grooves to reduce friction.
    [004] Gate valves can be operated manually, such as a wheel mounted on the stem or nut sleeve. It is also known to use a remote operated vehicle (ROV) to engage and turn a rod or nut sleeve. Hydraulically powered actuators are also used in which a piston moves the rod linearly without rotation. Electric actuators are also known to employ an electric motor and a gear train to turn a rod or nut sleeve to cause the drawer to move.
    [005] Typically, a seal in the stem portion of the chamber engages the stem to seal pressure within the chamber. The pressure exerted on the stem seal can be too great, causing the stem seal to fail. When the stem seal fails this will allow fluid or gas to flow out of the valve around the stem. Some prior art embodiments provide a second seal that will seal the valve stem to the valve body in the event that the primary seal fails. This provides redundancy within the valve stem seals which increases the reliability of the seals.
    [006] When a second seal is used, in the event that the first seal leaks, a volume of fluid will be maintained between the failed first seal and the second seal. Depending on the size of the spacing between the first seal and the second seal, the volume can be quite small. The small volume size allows the fluid pressure within the volume to quickly reach internal system pressure. This is not a rare condition as many of the environments in which valves are placed are subjected to extreme pressure loads for many years, significantly increasing the likelihood that the primary seal will leak or fail. When the valve is opened, pressure can then quickly drain through the leaking seal. This can cause additional damage to the primary seal so that what was a small leak becomes a major primary seal defect. Major primary seal defect can eliminate any benefit that the leaking primary seal provided, increasing the likelihood of subsequent secondary seal defect. Thus, there is a need for a stem seal with high reliability brought about by redundant seals, while allowing the seals to flow in leakage events through the primary seal. DESCRIPTION OF THE INVENTION
    [007] These and other problems are generally solved or circumvented and technical advantages are generally achieved by preferred embodiments of the present invention which provide a redundant valve-flowed stem sealing system and a method of using the same.
    [008] According to an embodiment of the present invention, a valve having a stem seal assembly is disclosed. The valve includes a valve body that defines a flow passage and a body cavity perpendicular to the flow passage. The valve body defines a stem opening that extends from an exterior of the body to the body cavity. The valve includes a valve member movable between an open position and a closed position, the valve member having an orifice therethrough which registers with the flow passage when the valve member is in the open position. The valve also includes a valve stem having a valve stem axis coupled to the valve member, the valve stem extending from the body cavity to an exterior of the valve body through the valve stem opening to move the valve member from the closed position to the open position. A gasket assembly is positioned within the valve stem opening to seal the valve stem to the valve body. The gasket assembly includes a sealing ring having a v-shaped profile defining first and second legs extending from an apex of the v-shape radially outwardly, the first and second legs for sealing the opposing annular surfaces. . The gasket assembly includes a back ring having a v-shaped channel so that an apex of the seal ring can be inserted into the channel, the back ring having greater rigidity to radial movement than the first and second legs for limit the radial deformation of the first and second legs.
    [009] According to another embodiment of the present invention, a slide valve stem gasket assembly for sealing a slide valve stem to a slide valve body having a body cavity is disclosed. The packing assembly includes a packing ring located within the stem opening such that an outer diameter of the packing ring is with the inner diameter of the stem opening and an inner diameter of the packing ring is with the outer diameter of the stem of valve. The packing ring defines a first annular recess in the outside diameter of the packing ring and a second annular recess in the inside diameter of the packing ring. The assembly also includes a sealing retainer ring positioned coaxial with the packing ring and secured to the valve body such that the sealing retainer ring secures the packing ring to the valve body. The seal retainer ring defines a third annular recess in the outer diameter of the seal retainer ring coaxial with and axially above the first annular recess. The gasket ring defines a fourth annular recess proximate the sealing retainer ring, the fourth annular recess coaxial with and axially above the second annular recess. A seal is positioned in each annular recess so that each seal prevents the passage of fluid in a first direction and drains fluid in a second direction opposite the first direction.
    [010] According to yet another embodiment of the present invention, a sealing ring for a gate valve is disclosed. The sealing ring includes an insulated annular sealing support having a first end and a second end. The sealing ring also includes a sealing ring having a v-shaped profile positioned on the insulated sealing bracket so that the second end of the insulated sealing bracket inserts into the v-shaped profile. The sealing ring defines first and second legs that extend from an apex of the v-shape radially outwardly, the first and second legs sealing to opposing annular surfaces. An energizing spring having a v-shaped profile is interposed between the insulated sealing bracket and the sealing ring, the energizing spring exerting an expanding force on the legs of the sealing ring so that the sealing ring will remain in sealing contact with the opposing annular surfaces. The energizing spring can be biased in response to fluid pressure in the seal ring opposite the energizing spring to allow fluid to flow through the seal ring. The seal ring includes a rear ring having a v-shaped channel so that an apex of the seal ring can be inserted into the channel, the rear ring having greater rigidity to radial movement than the first and second legs of the seal ring. sealing ring to limit radial deformation of the first and second legs of the sealing ring. The first end of the insulated seal bracket has a substantially flat portion positioned on a supporting shoulder of the gasket assembly and the second end of the insulated seal bracket is in operative engagement with the v-shaped profile. The gasket is made of a polymer and the back ring is made of a polymer that has a higher hardness than the polymer in the gasket. The posterior ring channel extends only partially to the distal ends of each leg of the gasket. A tail ring width is less than the distance between the seal ring legs and the tail ring does not seal engagement with the stem. The back ring channel extends from the apex of the gasket along only part of the gasket.
    [011] An advantage of a preferred embodiment is that it provides a true redundant seal while still allowing pressure relief flow when needed. Thus, any leakage through the primary seal does not cause damage to or additional defects of the primary seal when fluid flows through the primary seal when the valve is open. Furthermore, the seals operate independently to reduce wear on the seal assembly and extend the life of the seal assembly. BRIEF DESCRIPTION OF THE DRAWINGS
    [012] In order that the manner in which the features, advantages and objectives of the invention as well as others that will become apparent are achieved and can be understood in more detail, the more particular description of the invention briefly summarized above may be taken by reference to the realizations thereof that are illustrated in the attached drawings that form part of this descriptive report. It should be noted, however, that the drawings illustrate only one preferred embodiment of the invention and are therefore not to be considered as limiting its scope as the invention may admit to other equally effective embodiments.
    [013] Figure 1 is a partial sectional view of a gate valve according to an embodiment of the present invention.
    [014] Figure 2 is a detailed view of a portion of the slide valve stem as indicated in Figure 1 according to an embodiment of the present invention.
    [015] Figure 3 is a detailed view of a slide valve stem as indicated in Figure 2 according to an embodiment of the present invention.
    [016] Figure 4 is a top view of a rear ring of the slide valve stem seal of Figure 3. DESCRIPTION OF ACHIEVEMENTS OF THE INVENTION
    [017] The present invention will now be described more fully hereinafter with reference to the accompanying drawings which illustrate the embodiments of the invention. This invention may, however, be embodied in many different forms and is not to be construed as limited to the illustrated embodiments defined in the present invention. Rather, these embodiments are provided so that this disclosure will be meticulous and complete and will fully convey the scope of the invention to those skilled in the art. Like numbers refer to like elements throughout the document and the first notation, if used, indicates like elements in alternative embodiments.
    [018] In the following discussion, a number of specific details are defined to provide a thorough understanding of the present invention. However, it will be obvious to those skilled in the art that the present invention can be practiced without such specific details. Additionally, for the most part, details regarding valve construction, uses and the like have been omitted as such details are not considered necessary to obtain a full understanding of the present invention and are considered to be within the skill of technicians in the Subject.
    [019] Referring to Figure 1, the gate valve 11 has a body 13 and a flow passage 15 extending transversely through the body 13. The valve 11 has a gate 17 with an orifice 19 therethrough. Drawer 17 can be designed in one piece or two pieces. Drawer 17 can be divided into two slices; each slice of drawer 17 must either be open or closed at the same time. Gate 17 is shown in the closed position in Figure 1. Valve 11 shown in FIGURE 1 is a rising-stem-type valve; however, this invention can be used similarly in non-rising stem type valves. When slide 17 is in the open position, orifice 19 of slide 17 registers with flow passage 15 of body 13 therethrough allowing flow through valve 11. When slide 17 is closed as shown, orifice 19 does not registers further with flow passage 15, blocking fluid flow through passage 15 and valve 11. Flow passage 15 intercepts a central cavity or chamber 21 located in body 13. A counter-hole is formed in flow passage 15 at each intersection with chamber 21. A seat ring 27 locates in each counterbore to seal the flow passage 15 to the drawer 17 while the drawer 17 is in the closed position. The slide valve 11 also includes a stem 29 coupled to the slide 17. The stem 29 has a shaft 25 that passes through a center of the shaft 29. The shaft 29 is linearly movable without rotation along the shaft 25 to act drawer 17 between open and closed positions. In the illustrated embodiment, an induction assembly 31 couples to body 13 around rod 29 to induce rod 29 and drawer 17 into the closed position. As illustrated, valve 11 is hydraulically actuated. A remotely operated vehicle can interface with induction assembly 31 to move rod 29 and drawer 17 from the closed position shown to an open position where orifice 19 registers with flow passage 15. A gasket assembly 33 provides the seal for stem 29 where stem 29 passes through body 13. One skilled in the art will understand that gate valve 11 is an exemplary valve. The disclosed embodiments contemplate and include any valve that has a stem that passes through a valve body to operate a valve member located within the body.
    [020] Referring to Figure 2, the packing assembly 33 is shown in more detail. Gasket assembly 33 includes at least one seal 35, four of which are shown in Figure 2: a first seal 35A; a second seal 35B; a third seal 35C; and a fourth seal 35D. As shown in Figure 3, each seal 35 includes an insulated bracket 37, an energizing spring 39, a seal ring 41, and a back ring 43. The insulated seal bracket 37 comprises an annular protrusion or ring having a first end 45 and a second end 47. The first end 45 of the insulated seal bracket 37 has a substantially flat portion 49 so that the insulated seal bracket 37 can be positioned on a cylindrical bearing shoulder within the gasket assembly 33. The second end 47 of the insulated seal holder 37 is opposite the first end 45 and comprises a protrusion in contact with the energizing spring 39 to properly position the seal ring 41 against the rear ring 43 and limit unwanted axial compression of the seal ring 41. The insulated seal bracket 37 will provide support for the seal 35, preventing excessive compression of the seal 35 by reacting to directed forces from the second end 47 to the first end 45. The insulated seal holder 37 will be formed of a material having sufficient resistance to compression such that the insulated seal holder 37 will not collapse during operational use of the seal 35.
    [021] The sealing ring 41 comprises a v-shaped, inverted V-shaped or v-shaped profile such that a V-shaped apex 51 and the second end 47 of the insulated sealing bracket 37 are facing in the same direction. The sealing ring 41 also includes a first leg 53 and a second leg 55. The first leg 53 and the second leg 55 extend toward the first end 45 of the insulated sealing bracket 37. Additionally, a width between the distal ends 57 , 59, the first leg 53 and the second leg 55, respectively, is less than the width between the first and second legs 53, 55 of the sealing ring 41 at apex 51. Thus, the sealing ring 41 is wider near the first end 45 of the insulated seal bracket 37 than at apex 51. In the example shown, the outer surfaces of legs 53, 55 slant at a first angle a from apex 51 to a joint 52. Legs 53, 55 slant at a second angle p from junction 52 to distal ends 57, 59. Junction 52 is spaced closer to apex 51 than to distal ends 57, 59. Angle β is less than angle a relative to a geometric axis 54 traversing the legs 53, 55 and passing through the vertex 51. When energized, the distal ends 57, 59 can contact at least one of the stem 29 (Figure 2) and the body 13. The seal ring 41 has an interior surface 42 facing the insulated sealing bracket 37 and a surface outer 44 facing rear ring 43. Sealing ring 41 may be formed of a fluorocarbon material such as Teflon. One skilled in the art will understand that other materials which have similar properties to the fluorocarbon material disclosed in the present invention are contemplated and included in the disclosed embodiments.
    [022] The energizing spring 39 is an annular spring interposed between the sealing ring 41 and the insulated sealing bracket 37. The energizing spring 39 has a V-shaped cross-section profile similar to that of the sealing ring 41 so that a surface of the energizing spring 39 can contact the inner surface 42 of the sealing ring 41. An apex 61 of the energizing spring 39 will face in the same direction as the second end 47 of the insulated sealing bracket 37 and apex 51 of the sealing ring 41. The energizing spring 39 includes a first leg 63 and a second leg 65 which run parallel to, and generally in contact with, the first leg 53 and the second leg 55, respectively. The energizing spring 39 has a constant spring such that the energizing spring 39 will resist compression of the first leg 63 and second leg 65 towards the insulated sealing support 37 during normal operating conditions. Preferably, when the seal 35 is placed within the gasket assembly 33, the seal ring 41 and the energizing spring 39 will undergo a slight displacement towards each other of the first legs 53, 63 and second legs 55, 65 of the sealing ring 41 and energizing spring 39, respectively. This displacement causes the energizing spring 39 to exert a force against the compression of the energizing spring 39 and thus the compression of the sealing ring 41, towards the isolated sealing support 37. As a result, when placed within the gasket assembly 33, energizing spring 39 will cause the first and second legs 53, 55 of the sealing ring 41 to seal to at least one of the rod 29 and the body 13. In the illustrated embodiment, the spring energizing 39 is formed of a cobalt-chromium-nickel alloy such as ELGILOY®. One skilled in the art will understand that other materials having similar properties to the cobalt-chromium-nickel alloy disclosed in the present invention are contemplated and included in the disclosed embodiments.
    [023] The back ring 43 may be an annular ring positioned adjacent to the gasket 41 affixed to the energizing ring 39 and the insulated gasket bracket 37. The back ring 43 has a generally square-shaped cross-sectional profile. Preferably, the back ring 43 defines a channel 67 adjacent to the sealing ring 41. The channel 67 may have a V-shaped profile corresponding to the profile of the outer surface 44 formed by the sealing ring 41 so that the channel 67 can be with it. to apex 51 and to a portion of the outer surface 44 of the seal ring 41. The channel 67 may extend at least in part along the outer surface 44 of the first and second legs 53, 55 of the seal ring 41. In the embodiment shown , the back ring 43 extends along the legs 53, 55 less than half the length of the legs 53, 55 from the ends 57, 59 to the apex 51. The tips of the back ring 43 are near the junction 52. The ring tail 43 may have a width less than the width at the distal ends 57, 59 of the first and second legs 53, 55, respectively, of the sealing ring 41. Thus, the tail ring 43 preferably does not seal either the stem 29 or body 13. The back ring 43 pod and also have a substantially flat surface 69 opposite the surface 49 of the first end 45 of the insulated seal holder 37. The surface 69 may be positioned proximate to an oppositely facing shoulder 56 within the gasket assembly 33 so that the surface 69 may rest at shoulder 56 during operational use of seal 35. In the illustrated embodiment, back ring 43 may be formed of a polyether ether ketone (PEEK) material of sufficient strength to resist flow or deformation during operational uses that may compress the ring back 43 between seal ring 41 and shoulder 56 of gasket assembly 33. Preferably, back ring 43 has a hardness greater than the hardness of seal ring 41. One skilled in the art will understand that other materials have similar properties to Thermoplastic PEEK disclosed in the present invention are contemplated and included in the disclosed embodiments. In one embodiment, the back ring 43 attaches to the gasket 41. In another embodiment, the back ring 43 does not attach to the gasket 41.
    [024] The back ring 43 also includes a plurality of protrusions 60 formed on one or both of the inner diameter surface and the outer diameter surface of the back ring 43. For example, the second seal 35B of Figure 2 includes protrusions 60 formed on the back ring. Outer diameter of back ring 43 near gasket ring 71 as shown in Figure 3. At other sealing locations 35, protrusions 60 may be formed on the inner diameter of back ring 43. Protrusions 60 may be formed of the same material as posterior ring 43 and integral with posterior ring 43. Each protrusion 60 has a generally trapezoidal cross-sectional profile and extends a fractional portion of the circumference of posterior ring 43 as shown in Figure 4. Each protrusion 60 forms a channel 62 with a protrusion adjacent 60. Fluid under a higher pressure near surface 69 of back ring 43 flows through channels 62 to flow to an area. and the lower pressure one near the inner surface 42 of the seal ring 41. Thus, the protrusions 60 extend the life of the seal 35 by preventing catastrophic failure of the seal 35 due to pressure build-up in the non-sealing direction.
    [025] In one operation, seal 35 will perform both sealing and drain functions. As shown in Figure 3, the seal 35 provides a sealing function in response to gas or fluid pressure on the inner surface 42 of the seal ring 41. A gas or fluid pressure attempts to move from the inner surface 42 to the outer surface 44 in the Figure 3 a seal initially energized by energizing spring 39 will prevent the passage of fluid or gas through distal ends 57, 59 of seal ring 41. Increasing the gas or fluid pressure will exert a force on energizing spring 39 and inner surface 42 of the seal ring 41, pushing the distal ends 57, 59 and the first and second legs 53, 55 of the seal ring 41 into closer sealing contact with the surfaces to which the seal ring 41 is sealed. Thus, as the pressure increases on the inner surface 42, the sealing force of the sealing ring 41 will increase.
    [026] As fluid pressure increases on the inner surface 42 of the seal ring 41, pushing the distal ends 57, 59 into closer sealing contact with adjacent surfaces, the back ring 43 will exert a reactive force on the outer surface 44 through channel 67. The portions of the legs 53, 55 of the junction 52 to the distal ends 57, 59 are not directly restricted from flexing outwardly by the posterior 43. The increased fluid pressure applied to the inner surface 42 can cause the first and second legs 53, 55 collapse against adjacent surfaces or, in extreme cases, force portions of first and second legs 53, 55 to extrude between sides of back ring 43 and adjacent surfaces of gasket assembly 33 and at least one of the stem 29 and the body 13. To counteract this, the channel 67 will exert a reactive force on the compression of the seal ring 41 against the back ring 43 caused by the pressure of fluid. ment on the inner surface 42. The corresponding profile of the channel 67 and the outer surface 44 will allow the channel 67 to resist permanent deformation of the seal ring 41. Preventing or limiting permanent deformation of the seal ring 41 in situations where the pressure is high is exerted on the inner surface 42, the back ring 43 aids in extending the operational life of the seal ring 41 and thus the seal 35.
    [027] As shown in Figure 3, the seal 35 provides a flow function for the fluid or gas pressure on the outer surface 44 of the seal 41. In the case where the fluid or gas leaks around the seal ring 41 during the In prolonged use of valve 11, fluid or gas may become trapped in an adjacent outer surface of volume 44. Fluid may be trapped in a volume between second seal 35B and fourth seal 35D. Alternatively, fluid can be trapped in a volume between the second seal 35B and the load ring assembly 99. Continued operation of the valve 11 can rapidly raise the pressure from the trapped volume of fluid on the outer surface 44 to that of the surface pressure. interior 42 of the seal ring 41. When the slide 17 moves to the open position, allowing fluid to flow through the flow passage 15 of the valve 11, a pressure differential arises between the exterior surface 44 and the interior surface 42 of the sealing ring 41, such that a higher high pressure exists on the side of the outer surface 44. The narrower width of the back ring 43 relative to the width of the sealing ring 41 and channels 62 formed by the protrusions 60 will allow trapped fluid flow through the back ring 43. The protrusions 60 maintain a separation between the inside diameter of the gasket ring 71 in the annular recess 87 and back ring 43, providing a flow path for the volute. me trapped in the fluid that allows the fluid to flow under appropriate situational conditions. The fluid pressure can then exert a force on the outer surface 44 of the seal ring 41 overcoming the spring force of the energizing spring 39. The higher pressure on the outer surface 44 can compress the first and second legs 53, 55 of the sealing ring 41 to insulated sealing bracket 37, removing the distal ends 57, 59 from sealing contact with adjacent surfaces. The trapped fluid or gas can then flow through the sealing ring 41 to the low pressure side of the inner surface 42.
    [028] Once sufficient pressure has drained through the sealing ring 41, the spring force of the energizing spring 39 will overcome the force exerted on the outer surface 44 by the fluid or gas pressure and will move the distal ends 57, 59 of the first and second legs 53, 55,respectively, back in sealing contact with adjacent surfaces. The insulated seal bracket 37 positions the seal ring 41 a sufficient distance from the bearing shoulder in contact with the flat portion 49 to allow such displacement of the seal ring 41. Additionally, the insulated seal bracket 41 prevents axial movement of the gasket 41 during this pressure draining operation. Thus, the seal 35 provides a seal to high pressure forces exerted against the inner surface 42 of the seal ring 41 and a flow to high pressure forces exerted against the outer surface 44 of the seal ring 41. Following the flow, the ring The energizing valve 39 can return the sealing ring 41 to the energized position, preventing flow from the inner surface 42 to the outer surface 44 when the valve 11 is closed.
    [029] As shown in Figure 2, the packing assembly 33 includes four seals 35 in this example. The packing assembly 33 also includes a metal packing ring 71 and a metal packing retainer ring 73. The packing ring 71 rests on an upwardly facing annular shoulder 75 of the body 13 formed within a stem opening 77 which allows passage of stem 29 into cavity 21. Gasket ring 71 includes an annular alignment surface 79 on an inner diameter of gasket ring 71. Alignment surface 79 is tapered and extends from a downwardly facing shoulder 81 of the packing ring 71 to opening 77. The downwardly facing shoulder 81 is adapted to seat on the annular shoulder 75 of the body 13 so that the packing ring 71 is coaxial with the axis 25. The packing ring 71 includes a first annular recess 83 formed in an outer diameter of the packing ring near the annular shoulder 81. The first annular recess 83 extends from the outer diameter of the inner packing ring 71 to the outwardly facing cylindrical surface 84 and from the facing shoulder down 81 to the downwardly facing recess shoulder 85. The first annular recess 83 will be sized and shaped such that the first seal 35A can be placed within the first annular recess 83. The first seal 35A substantially fills the first annular recess 83 and is positioned so that the first end 49 (Figure 3) of the first seal 35A abuts the upwardly facing shoulder 75 of the body 13 (Figure 2). The surface 69 of the back ring 43 of the first seal 35A will be close to, but optionally may not contact the downwardly facing recess shoulder 85. Preferably, the distal end 59 of the seal ring 41 of second leg 55 of the first seal 35A will contact and seal the outwardly facing shoulder 84 of the gasket ring 71 within the first annular recess 83. Similarly, the distal end 57 of the first leg 53 of the seal ring 41 of the first seal 35A will contact and seal to a surface of the body 13. Thus, the first seal 35A will seal against the movement of fluid from cavity 21 to an exterior of body 13 and will drain fluid from an exterior of body 13 to cavity 21.
    [030] The gasket ring 71 also defines a second annular recess 87 in an inner diameter of the gasket ring 71. The second annular recess 87 extends from the inner diameter surface to seat on a radially inwardly facing shoulder 89 and from from an upwardly facing shoulder 91 toward the cavity 21 to seat on an upwardly facing recess shoulder 93. The gasket ring 71 also includes an annular portion 95 extending from an upper end of the gasket ring 71 proximal to a center of the width of the packing ring 71 so that the packing ring 71 defines the upwardly facing shoulder 91 on an inside diameter side of the annular portion 95 and an upward facing shoulder 97 on an outside diameter side of the annular portion 95 A load ring assembly 99 will be positioned on the outwardly facing shoulder 91 and will extend over a portion of the length of the annular protrusion 95. The load ring assembly 99 may comprise any suitable assembly adapted to transfer load from second seal 35B to gasket ring 71. In the illustrated embodiment, load ring assembly 99 does not transfer a load applied to second seal 35B to fourth seal 35D such that second seal 35B and fourth seal 35D operate independently of each other. In an exemplary embodiment, the load ring assembly 99 comprises a rod assembly similar to "Segmented Seal Ring and Support for Same" as disclosed in Pending Patent Application No. 13/281,526, filed October 26, 2011 and is incorporated by way of reference in its entirety in the present invention. One skilled in the art will recognize that other suitable annular stem assemblies can be used provided the stem assembly allows for independent loading of the second gasket 35B and fourth gasket 35D.
    [031] The second seal 35B will substantially fill the second annular recess 87 and will be positioned so that the first end 49 (Figure 3) of the second seal 35B abuts the upward facing shoulder 93 of the gasket ring 71 (Figure 2). The surface 69 of the back ring 43 of the second seal 35B will be proximate to, but may not contact, a downwardly facing surface 101 of the load ring assembly 99. Preferably, the distal end 59 of the second leg 55 of the second seal ring 41 seal 35B will contact and seal an OD surface of stem 29. Similarly, the distal end 57 of the first leg 53 of the seal ring 41 of the second seal 35B will contact and seal the inwardly facing shoulder 89 of the second annular recess 87 of the gasket ring 71. Thus, the second seal 35B will seal against the movement of fluid from cavity 21 to an exterior of body 13 along rod 29 and will drain fluid into cavity 21 along rod 29 from an exterior of the body. body 13.
    [032] The sealing retainer ring 73 includes an annular protrusion 103 extending from a lower portion of the sealing retainer ring 73 towards the cavity 21. The annular protrusion 103 has a width such that the annular protrusion 103 will substantially fill a gap between the annular protrusion 95 of the gasket ring 71 and an inner diameter surface of the opening 77. As shown, the outer diameter of the annular protrusion 103 is flush with the outer diameter of the gasket ring 71. The annular protrusion 103 will define a third recess annular protrusion 105 extending from the outer diameter of annular protrusion 103 toward annular protrusion 95 to seat in an outwardly facing shoulder 107. The third annular recess 105 will extend from one end of annular protrusion 103 away from cavity 21 to seat in one shoulder facing down 109.
    [033] The third annular recess 105 will be sized and shaped such that a third seal 35C can be placed within the third annular recess 105. The third seal 35C will substantially fill the third annular recess 105 and will be positioned so that the first end 49 (Figure 3) of third seal 35C will adjoin downwardly facing shoulder 109 of third annular recess 105 (Figure 2). The surface 69 of the back ring 43 of the third seal 35C will be proximate, but may not contact the upturned shoulder 91 of the gasket ring 71. Preferably, the distal end 57 of the first leg 53 of the seal ring 41 of the third seal 35C will contacting and sealing the outwardly facing shoulder 107 within the third annular recess 105. Similarly, the distal end 59 of the second leg 55 of the seal ring 41 of the third seal 35C will contact and seal a surface of the body 13. Thus, third seal 35C will seal against fluid movement from an exterior of body 13 to cavity 21 and will drain fluid from cavity 21 to an exterior of body 13.
    [034] The seal retainer 73 defines a downwardly facing shoulder 111 that extends from a base of the annular protrusion 103 to an inner diameter of the seal retainer ring 73 near the stem 29. The annular protrusion 95 of the gasket ring 71 has a width extending a portion of the width between the annular protrusion 103 of the sealing retaining ring 73 and the inner diameter of the sealing retaining ring 73 such that a fourth annular recess 113 exists between the annular protrusion 95, downwardly facing shoulder 111 of the retaining ring seal 73 and an upper surface 115 of the load ring assembly 99. The fourth annular recess 113 extends from an area proximate the stem 29 inwardly to the inwardly facing surface 117 of the annular protrusion 95.
    The fourth annular recess 113 will be sized and shaped such that a fourth seal 35D can be placed within the fourth annular recess 113. The fourth seal 35D will substantially fill the fourth annular recess 113 and be positioned so that the first end 49 (Figure 3) of fourth seal 35D will abut top surface 115 of load ring assembly 99 (Figure 2). The surface 69 of the back ring 43 of the fourth seal 35D will be proximate, but may not contact the downwardly facing shoulder 111 of the seal retaining ring 73. Preferably, the distal end 57 of the first leg 53 of the seal ring 41 of the fourth seal 35D will contact and seal the inwardly facing surface 117 of the annular protrusion 95 of the gasket ring 71 within the fourth annular recess 113. Similarly, the distal end 59 of the second leg 55 of the seal ring 41 of the fourth seal 35D will contact and seal a rod surface 29. Thus, fourth seal 35D will seal against the movement of fluid from cavity 21 to an exterior of body 13 and will drain fluid into cavity 21.
    [036] As illustrated in Figure 2, the second seal 35B and the fourth seal 35D are positioned so that the seals seal the stem 29 to prevent fluid flow out of the cavity 21 along the stem 29 while allowing the fluid to which can leak through the second seal 35B flows back into cavity 21. This provides a redundant seal system that is more effective than prior art seal methods. Similarly, the combined second and fourth seals 35B, 35D provide fluid flow that prevents damage to the seals where fluid pressure within cavity 21 is suddenly released. Similarly, first seal 35A and third seal 35C are positioned to prevent fluid flow into cavity 21 along body 13. Unlike seals 35B and 35D, seals 35A and 35C do not provide redundant protection. Instead, the first and third seals 35A, 35C, respectively, provide the opposite direction seal. This potentially reduces the amount of fluid that can pass between an exterior of the body 13 and the cavity 21. Additionally, the first and third seals 35A, 35C, respectively, provide the opposite direction flow that protects both data seals in the event of a sudden pressure change in the sealed area. One skilled in the art will understand that the seal and flow directions of each seal can be switched by inverting the position of each seal as needed.
    [037] Consequently, the disclosed embodiments provide several advantages over the prior art. For example, the disclosed embodiments provide a redundant seal system that provides two independent and checkable seals along the valve stem. This significantly improves the effectiveness and reliability over prior art stem seals. Additionally, the disclosed embodiments provide a flow mechanism to allow the release of fluid that has leaked through the seals to flow in response to rapid changes in fluid pressure within the valve cavity. This prevents damage to the first seal that can be caused by known leakage problems in all valve seal mechanisms. This in turn extends the life of the seal.
    [038] It is understood that the present invention can take many forms and embodiments. Consequently, several variations can be made without departing from the spirit or scope of the invention. Having thus described the present invention by reference to some of its preferred embodiments, it is noted that the disclosed embodiments are illustrative rather than limiting in nature and that a wide range of variations, modifications, alterations and substitutions is contemplated in the above description and , in some instances, some features of the present invention may be employed without a corresponding use of the other features. Many such variations and modifications may be considered obvious and desirable by those skilled in the art based on a review of the above description of preferred embodiments. Accordingly, it is appropriate that the appended claims be construed broadly and in a manner consistent with the scope of the invention.
    权利要求:
    Claims (17)
    [0001]
    1. VALVE HAVING A STEM SEAL ASSEMBLY, characterized by comprising: a valve body (13) defining a flow passage (15) and a body cavity (21) perpendicular to the flow passage; the valve body (13) further defining a stem opening (77) extending from an exterior of the body to the body cavity (21); a valve member movable between an open position and a closed position, the valve member blocking the flow passage in the closed position and permitting flow through the flow passage in the open position; a valve stem (29) having a valve stem (29) axis (25) coupled to the valve member, the valve stem (29) extending from the body cavity (21) to an exterior of the valve body through the valve stem opening (77) to move the valve member from the closed position to the open position; a first spring energized sealing ring (35A) positioned within the valve stem opening (77) for sealing the valve stem (29) to the valve body, the first sealing ring (35A) comprising: - a profile in V-shape defining first and second legs (53.55) extending from an apex of the V-shaped profile radially outward, the first and second legs (53.55) sealing the stem and body. to opposing annular surfaces; and - a rear ring (43) having a v-shaped channel that receives the apex of the v-shaped profile, the rear ring (43) having greater rigidity for radial movement than the first and second legs ( 53.55) to limit the radial deformation of the first and second legs (53.55); and - an insulated annular seal holder (37) having a first end (45) and a second end (47) wherein the first end (45) is positioned on a bearing shoulder of the gasket assembly and the second end (47) being inserted into an inner radius defined by the apex of the v-shaped profile to support the v-shaped profile positioned in the insulated ring seal holder (37); a second sealing ring (35B) positioned within the valve stem opening (77) to seal the valve stem (29) to the valve body; and a load ring assembly (99) stationarily mounted and defining a portion of the valve body between the first gasket (35A) and the second gasket (35B) that insulates the first gasket (35A) ) and the second seal ring (35B) such that a force applied to the first seal ring (35A) in a direction toward the second seal ring (35B) transfers to the load ring assembly (99) .
    [0002]
    VALVE according to claim 1, characterized in that the first sealing ring (41) further comprises: an energizing spring (39) having a V-shaped profile interposed between the insulated sealing support (37) and the v-shaped profile, whereby the energizing spring (39) exerts an expanding force on the legs (53.55) of the v-shaped profile so that the v-shaped profile will remain in sealing contact with the surfaces opposite annulars; and wherein the energizing spring (39) is biasable in response to a fluid pressure in the v-shaped profile opposite the energizing spring (39) to allow fluid to flow through the v-shaped profile.
    [0003]
    3. VALVE, according to claim 1, characterized in that the v-shaped profile is formed by a polymer and the posterior ring (43) is formed by a polymer that has a greater rigidity than the polymer of the v-shaped profile.
    [0004]
    4. VALVE, according to claim 1, characterized in that the posterior ring channel extends only partially to the distal ends (57,59) of each leg of the v-shaped profile.
    [0005]
    5. VALVE according to claim 1, characterized in that a width of the rear ring (43) is less than a distance between the outside of the distal ends (57.59) of the sealing ring legs (53.55) (41); and an inner span is located between the rear ring (43) and the stem (29) and an outer span is located between the rear ring (43) and the body (13).
    [0006]
    6. VALVE according to claim 1, characterized in that the rear ring channel (43) extends from the apex of the v-shaped profile along only part of the v-shaped profile.
    [0007]
    VALVE according to claim 1, characterized in that: the v-shaped profile has two outer angled portions meeting at a joint (52); and the angled portion of the apex (51) to the junction (52) has a greater angle relative to a geometric axis (54) passing through the apex (51) than the angled portion of the junction (52) to the distal ends of each. leg (53.55) of gasket (41).
    [0008]
    The VALVE of claim 1, further comprising a plurality of circumferentially spaced protrusions (60) on the rear ring (43) which define a plurality of fluid channels (62) which allow fluid to flow through. of the surface of the v-shaped profile.
    [0009]
    VALVE according to claim 1, characterized in that the second seal comprises a spring-energized seal.
    [0010]
    10. VALVE STEM GASKET ASSEMBLY, for sealing a valve stem (29) to a valve body (13) characterized by comprising a body cavity (21), the gasket assembly comprising: a first ring of spring-energized seal (35A) positioned within a valve stem opening (77) that extends axially through the body to seal the valve stem (29) to the valve body (13) and the first seal ring (35A) comprising: - a v-shaped profile defining first and second legs (53.55) extending from an apex of the v-shaped profile radially outwards, the first and second legs (53.55) seal stem and body to opposing annular surfaces; and - a rear ring (43) having a v-shaped channel that receives the apex of the v-shaped profile, the rear ring (43) having greater rigidity for radial movement than the first and second legs ( 53.55) to limit the radial deformation of the first and second legs (53.55); and; - an insulated ring seal bracket (37) having a first end (45) and a second end (47) wherein the first end (45) is positioned on a supporting shoulder of the gasket assembly and the second end ( 47) being inserted into an inner radius defined by the apex of the v-shaped profile to support the v-shaped profile positioned in the insulated ring seal holder (37); a second sealing ring (35B) positioned within the valve stem opening (77) to seal the valve stem (29) to the valve body (13); and a load ring assembly (99) mounted to, and forming a part of, the body (13) having a first end in engagement with the first sealing ring (35A) and a second end in engagement with the second ring. seal (35B), such that an axial force applied to the first seal ring (35A) transfers to the load ring assembly (99), an axial force in an opposite direction to the second seal ring (35B) ) transfers to the load ring assembly (99).
    [0011]
    11. GASKET ASSEMBLY according to claim 10, characterized in that the first seal comprises: an energizing spring (39) having a V-shaped profile interposed between the insulated sealing bracket (37) and the sealing ring, the energizing spring (39) exerting an expanding force on the legs of the seal ring (53.55) so that the seal ring will remain in sealing contact with the opposing annular surfaces; wherein the energizing spring (39) can be biased in response to a fluid pressure in the seal ring opposite the energizing spring (39) to allow fluid to flow through the seal ring (41); and a back ring (43) having a v-shaped channel that receives an apex (51) of the sealing ring (41), the back ring (43) having a greater rigidity to radial movement than the first and second. legs (53.55) of the seal ring (41) to limit radial deformation of the first and second legs (53.55) of the seal ring (41).
    [0012]
    The gasket assembly of claim 11, further comprising a plurality of circumferentially spaced protrusions (60) on the rear ring (43) defining a plurality of fluid channels (62) that allow fluid flows through the sealing surface of the gasket (41).
    [0013]
    13. GASKET ASSEMBLY according to claim 11, characterized in that the first sealing ring (41) additionally comprises a protrusion (60) formed on an outer surface of the rear ring (43) opposite an end of the sealing ring (41 ) which seals to the valve stem (29) and the valve body (13), the protrusion (60) forming one or more fluid channels (62) so that fluid can flow through the sealing surface of the first sealing ring (41).
    [0014]
    14. GASKET ASSEMBLY according to claim 11, characterized in that: the sealing ring (41) is formed by a polymer; and the back ring (43) is formed of a polymer that has a greater hardness than the polymer of the sealing ring (41).
    [0015]
    A GASKET ASSEMBLY according to claim 11, characterized in that the second sealing ring comprises a spring-energized seal (39).
    [0016]
    16. SEALING RING, for a valve stem (29) characterized by comprising: an insulated ring seal holder (37) having a first end (45) and a second end (47); a sealing ring (41) having a v-shaped profile positioned on the insulated sealing bracket (37) so that the second end (47) of the insulated sealing bracket (37) inserts into the v-shaped profile. ; wherein the sealing ring (41) defines first and second legs (53.55) extending from an apex (51) of the V-shaped profile radially outwardly, the first and second legs ( 53,55) seal to opposing annular surfaces of the valve stem (29) and a valve body (13); an energizing spring (39) having a v-shaped profile interposed between the insulated sealing bracket (37) and the sealing ring (41), the energizing spring (39) exerting an expanding force on the legs. the sealing ring (53.55) so that the sealing ring (41) will remain in sealing contact with the opposing annular surfaces; wherein the energizing spring (39) can be biased in response to a fluid pressure in the seal ring (41) opposite the energizing spring (39) to allow fluid to flow through the seal ring (41); a rear ring (43) having a v-shaped channel (67) that receives an apex (51) of the sealing ring, the rear ring (43) having greater rigidity to radial movement than the first and second legs. (53.55) of the seal ring (41) to limit radial deformation of the first and second legs (53.55) of the seal ring (41); wherein the first end (45) of the insulated seal bracket (37) has a substantially flat portion (49) positioned on a bearing shoulder of the gasket assembly and the second end (47) of the insulated seal bracket (37) is in operative engagement with the v-shaped profile; wherein the sealing ring (41) is formed of a polymer and the back ring (43) is formed of a polymer that has a greater hardness than the polymer of the sealing ring (41); wherein the channel (67) of the back ring (60) extends only partially to the distal ends of each leg (53,55) of the seal ring (41); wherein a width of the back ring (43) is less than a distance between the outer sides of the distal ends (57,59) of the legs (53,55) of the sealing ring (41); wherein an inner span is located between the rear ring (43) and the stem (29) and an outer span is located between the rear ring (43) and the valve body (13); wherein the channel (67) of the back ring (43) extends from the apex (51) of the gasket (41) along only part of the gasket (41); and a plurality of circumferentially spaced protrusions (60) formed on an outer surface of the back ring (43) which define a plurality of fluid channels (62) so that fluid can flow through the sealing surface of the sealing ring ( 41).
    [0017]
    The gasket of claim 16, characterized in that: the gasket (41) has two angled outer portions meeting at a joint (52); and the angled portion of the apex (51) to the junction (52) has a greater angle relative to a geometric axis (54) passing through the apex (51) than the angled portion of the junction (52) to the distal ends of each. leg (53.55) of gasket (41).
    类似技术:
    公开号 | 公开日 | 专利标题
    BR102012031584B1|2021-09-21|VALVE THAT HAS A STEM SEAL ASSEMBLY, VALVE STEM GASKET ASSEMBLY AND SEAL RING
    BR102012007777B1|2021-03-16|gate valve seat, gate valve and method for sealing on a gate valve
    US4741509A|1988-05-03|Gate valve with improved secondary body to bushing seals
    US9850770B2|2017-12-26|Intershaft seal with asymmetric sealing ring
    US8690534B1|2014-04-08|Backup seals in rotary pumps
    DE102015225166A1|2016-06-16|Arc-bound ring seal and an arcuately bonded ring seal containing ring sealing system
    US10677360B2|2020-06-09|Gate valve
    US20070140877A1|2007-06-21|Shutdown seal for reactor coolant pump
    JP2007292068A|2007-11-08|Variable clearance positive pressure packing ring with leaf spring and support device
    GB2153972A|1985-08-29|Expanding gate valve
    BR102012005322B1|2021-08-24|GATE VALVE ASSEMBLY AND VALVE SEAT
    BRPI0922071B1|2019-07-02|FLOW CONTROL DEVICE.
    BRPI0911274B1|2019-12-03|internally pressurized seal assembly
    BR112013028963B1|2021-03-16|valve useful as a production valve in an underwater production tree or connected to an underwater production tree
    EP0675304B1|2001-05-23|Seals
    BR112021008392A2|2021-09-14|VALVE WITH DIFFERENTIAL PRESSURE SEAT
    US9541219B2|2017-01-10|Valve packing shield for use in hydrocarbon operations
    AU2015328620B2|2019-09-19|Non-parallel multi-bore sealing device
    KR20190006961A|2019-01-21|Butterfly valve disk unit
    WO2016171857A1|2016-10-27|Valve vented redundant stem seal system
    CN109804189B|2021-06-04|Valve with a valve body
    US3625480A|1971-12-07|Temperature compensated preloaded seal
    BR112015015799B1|2021-12-07|DRAWER VALVE
    US10428959B2|2019-10-01|Assembly for compressing a ball valve seat
    WO2014078619A2|2014-05-22|Thermally-sensitive triggering mechanism for selective mechanical energization of annular seal element
    同族专利:
    公开号 | 公开日
    NO342786B1|2018-08-06|
    SG191529A1|2013-07-31|
    US20130161553A1|2013-06-27|
    GB201222192D0|2013-01-23|
    AU2012261740A1|2013-07-11|
    BR102012031584A2|2016-10-11|
    NO20121444A1|2013-06-24|
    US20150226338A1|2015-08-13|
    GB2497850A|2013-06-26|
    US9989157B2|2018-06-05|
    US9010725B2|2015-04-21|
    GB2497850B|2014-10-29|
    CN103174873A|2013-06-26|
    MY166826A|2018-07-23|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US765430A|1903-05-16|1904-07-19|Charles E Huxley|Gate-valve.|
    US3060964A|1958-11-10|1962-10-30|Texas Pipe Line Company|Valve having vented housing|
    US3421547A|1965-11-30|1969-01-14|Alkon Products Corp|Check valve mechanism|
    US3765690A|1971-01-21|1973-10-16|Ato Inc|Composite seal|
    US3921991A|1974-01-17|1975-11-25|Parker Hannifin Corp|Combination fluid seal and rod wiper|
    US3958592A|1974-02-06|1976-05-25|Willis Oil Tool Co.|Safety shut-off valve|
    US3990679A|1975-03-20|1976-11-09|Gray Tool Company|Stem sealing for high pressure valve or the like|
    US3993092A|1975-09-17|1976-11-23|New Concepts, Inc.|Gate valve with replaceable liner|
    US4340204A|1976-02-06|1982-07-20|Smith International, Inc.|High pressure gate valve with preloaded, stacked, solid lubricated stem seals|
    US4363465A|1976-06-16|1982-12-14|Smith International, Inc.|Extreme temperature, high pressure balanced, rising stem gate valve with super preloaded, stacked, solid lubricated, metal-to-metal seal|
    US4281819A|1978-03-23|1981-08-04|Linder Morris B|Balanced stem gate valve|
    US4230299A|1978-07-03|1980-10-28|Petroleum Designers, Inc.|Pressure balanced gate valve having selective actuator systems|
    US4274432A|1980-01-21|1981-06-23|Otis Engineering Corporation|Valve|
    US4364544A|1981-05-18|1982-12-21|Daniel Industries, Inc.|Valve seat with sediment guard|
    GB2103310B|1981-07-31|1985-07-24|Smith International|Seal|
    US4451047A|1981-07-31|1984-05-29|Smith International, Inc.|Seal|
    US4531711A|1982-06-30|1985-07-30|Cameron Iron Works, Inc.|Valve and stem seal therefor|
    US4568062A|1983-03-07|1986-02-04|Fmc Corporation|Fire-resistant gate valve|
    US4541449A|1983-04-28|1985-09-17|Cameron Iron Works, Inc.|Gate valve|
    US4570659A|1983-11-01|1986-02-18|Gray Tool Company|Fire resistant valve|
    US5624101A|1983-11-14|1997-04-29|Beson; John|Dual seal valve|
    US4592558A|1984-10-17|1986-06-03|Hydril Company|Spring ring and hat ring seal|
    US4706970A|1984-11-14|1987-11-17|Polydyne Industries, Inc.|Flexible ring seal with insert in circumferentially extending channel|
    US4576385A|1984-12-12|1986-03-18|Fmc Corporation|Fluid packing assembly with alternating diverse seal ring elements|
    US4577873A|1985-03-29|1986-03-25|Baumann Hans D|Dual valve stem packing arrangement|
    US4658847A|1985-07-09|1987-04-21|The Fluorocarbon Company|Bimetallic C-ring seal|
    US5306021A|1986-02-25|1994-04-26|Morvant John D|V-shaped seal with anti-extrusion section|
    US4886241A|1987-09-16|1989-12-12|Fisher Controls International, Inc.|Valve stem packing containment for high pressure, high temperature|
    DE3873072T2|1988-03-23|1992-12-03|Cooper Ind Inc|VALVE SEAL.|
    US4878651A|1988-03-24|1989-11-07|Worldwide Oilfield Machine, Inc.|Valve seat assembly|
    US4893650A|1988-09-12|1990-01-16|Bill Chisholm|One way high pressure flow control fittings|
    GB8903585D0|1989-02-16|1989-04-05|Kent Introl Ltd|Improvements relating to seals|
    US5238252A|1990-01-18|1993-08-24|Eisenwerk Heinrich Schilling Gmbh & Co.|Shut-off fittings with a sealing device|
    US5230498A|1990-10-09|1993-07-27|Fisher Controls International, Inc.|Live load packing system|
    US5094270A|1991-03-14|1992-03-10|Dril-Quip Inc.|Double gated valve|
    EP0525261A1|1991-07-31|1993-02-03|Cooper Industries, Inc.|Stem seal|
    US5246236A|1992-01-21|1993-09-21|Halliburton Company|Seal for long-time exposures in oil and gas well tools|
    US5201872A|1992-01-27|1993-04-13|Superior Oilfield Products, Inc.|Gate valve improvement|
    US5192051A|1992-07-30|1993-03-09|Abb Vetco Gray Inc.|Unidirectional seat seal for gate valve|
    US5375812A|1993-12-06|1994-12-27|Abb Vetco Gray Inc.|Dynamic metal-to-metal seal|
    US5730419A|1994-07-12|1998-03-24|Fmc Corporation|Dual backseat valve assembly|
    US6290235B1|1997-07-02|2001-09-18|Parker-Hannifin Corporation|Sealing system for a reciprocating shaft|
    US6082707A|1998-10-23|2000-07-04|Gulf Technologies International, L.C.|Valve seat and method|
    US6386548B1|1998-10-27|2002-05-14|A. W. Chesterton Company|Dual seal assembly|
    US6260822B1|2000-01-04|2001-07-17|Worldwide Oilfield Machine, Inc|Seat assembly for a gate valve|
    US6345805B1|2000-01-04|2002-02-12|Vijay R. Chatufale|Rotary valve with seat assembly|
    WO2001073254A2|2000-03-24|2001-10-04|Fmc Corporation|Coupling means for controls bridge through a tubing head|
    DE10139499C1|2001-08-10|2003-03-13|Lucas Automotive Gmbh|Composite component, in particular valve, and method for producing the same|
    US6659419B2|2001-12-26|2003-12-09|Hp&T Products, Inc.|Hydraulic double acting valve actuator|
    US6869079B2|2002-02-15|2005-03-22|Fmc Technologies, Inc.|Stackable metallic seal and method of using same|
    US6840270B2|2002-10-09|2005-01-11|Visteon Global Technologies, Inc.|Low deviation pressure relief valve for fuel pumps|
    EP1433988B1|2002-12-24|2005-12-14|Techspace Aero S.A.|Regulation valve|
    US6966537B2|2003-03-11|2005-11-22|Worldwide Oilfield Machine, Inc.|Valve with seat assembly|
    US7118114B2|2003-05-15|2006-10-10|Woodward Governor Company|Dynamic sealing arrangement for movable shaft|
    US7004452B2|2003-09-25|2006-02-28|Hp&T Products, Inc.|Valve seal assemblies and methods|
    CA2586442C|2004-11-05|2010-05-25|Petrolvalves Usa|Metal valve stem seal and sealing system|
    US7309058B2|2004-12-03|2007-12-18|Vetco Gray Inc.|Flexible backseat seal for gate valve|
    JP2007071329A|2005-09-08|2007-03-22|Nok Corp|Back-up ring|
    NO328728B1|2006-11-20|2010-05-03|Aker Subsea As|Lock valve for oil and gas production systems|
    GB0623326D0|2006-11-22|2007-01-03|British Engines Ltd|Metal stem seal|
    US8215646B2|2008-08-28|2012-07-10|Castleman Larry J|Seal assembly|
    US7946556B1|2010-08-16|2011-05-24|Sistag Ag Absperrtechnik|Resilient seat seal for a valve|
    US20120080634A1|2010-09-30|2012-04-05|Vetco Gray Inc.| valve bore sealing method and apparatus|
    US8672295B2|2010-10-08|2014-03-18|National Oilwell Varco, L.P.|Gate valve|
    CN102094987A|2010-12-21|2011-06-15|上海神开石油化工装备股份有限公司|Ultrahigh pressure flat plate gate valve|
    EP2681409B1|2011-03-04|2018-10-24|Parker-Hannificn Corporation|Metal chevron axial seal|
    NO334295B1|2011-05-09|2014-01-27|Aker Subsea As|Valve usable as a production valve|
    US8752634B2|2011-10-26|2014-06-17|Vetco Gray Inc.|Segmented seal ring and support of same|
    US9010725B2|2011-12-21|2015-04-21|Vetco Gray Inc.|Valve vented redundant stem seal system|
    US9897215B2|2012-12-31|2018-02-20|Vetco Gray Inc.|Multi-valve seat seal assembly for a gate valve|DE202011110961U1|2011-08-15|2017-11-02|Elringklinger Ag|Seal for sealing a sealing gap|
    WO2016171857A1|2015-04-20|2016-10-27|Vetco Gray Inc.|Valve vented redundant stem seal system|
    US9010725B2|2011-12-21|2015-04-21|Vetco Gray Inc.|Valve vented redundant stem seal system|
    US9897215B2|2012-12-31|2018-02-20|Vetco Gray Inc.|Multi-valve seat seal assembly for a gate valve|
    US10801622B2|2013-04-18|2020-10-13|Bal Seal Engineering, Llc|Interlocking face seal assemblies and related methods|
    JP6032139B2|2013-06-13|2016-11-24|トヨタ自動車株式会社|Seal body and gas seal mechanism|
    US9347585B2|2013-11-26|2016-05-24|Ge Oil & Gas Pressure Control Lp|Dual seal fire safe stem packing orientation|
    US10036485B2|2013-11-26|2018-07-31|Ge Oil & Gas Pressure Control Lp|Dual seal fire safe stem packing orientation|
    DE102014002727A1|2014-03-03|2015-09-03|Carl Freudenberg Kg|rod seal|
    US20150267819A1|2014-03-18|2015-09-24|Vetco Gray Inc.|Seal Element Having Contoured V-Spring|
    US9869350B2|2014-11-18|2018-01-16|Bürkert Contromatic Corp.|Positioning device|
    US9863551B2|2014-12-22|2018-01-09|Ge Oil & Gas Pressure Control Lp|Dynamic stem packing|
    US9885420B2|2015-05-07|2018-02-06|Sri Energy, Inc.|Gate valve|
    CN105626869A|2016-02-29|2016-06-01|苏州纽威阀门股份有限公司|Sealing structure and gate valve with sealing structure|
    US10724307B2|2016-11-14|2020-07-28|Cameron International Corporation|Annular packer system and method|
    US11105451B2|2017-07-07|2021-08-31|Eaton Intelligent Power Limited|Heat transfer interruption for improved fire resistance/proof performance|
    WO2019108745A1|2017-11-30|2019-06-06|Saint-Gobain Performance Plastics Corporation|Seal, assembly, and methods of using the same|
    CA3121851A1|2019-01-11|2020-07-16|A.W. Chesterton Company|Multiple component seal assembly|
    US11174958B2|2019-01-24|2021-11-16|Jet Oilfield Services, LLC|Gate valve and method of repairing same|
    CN113544357A|2019-03-20|2021-10-22|美国圣戈班性能塑料公司|Sealing element|
    法律状态:
    2016-10-11| B03A| Publication of a patent application or of a certificate of addition of invention [chapter 3.1 patent gazette]|
    2018-12-04| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2019-09-10| B15K| Others concerning applications: alteration of classification|Free format text: AS CLASSIFICACOES ANTERIORES ERAM: F16J 15/32 , F16K 3/02 , F16K 39/04 , F16K 41/08 Ipc: F16K 3/02 (1968.09), F16K 39/04 (1968.09), F16K 41 |
    2019-10-29| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2021-07-06| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2021-09-21| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 11/12/2012, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    US13/333,024|2011-12-21|
    US13/333,024|US9010725B2|2011-12-21|2011-12-21|Valve vented redundant stem seal system|
    [返回顶部]