Butterfly valve sealing element

Abstract

The valve assembly may include a valve body and a sealing ring. A sealing ring may be disposed within the sealing cavity of the valve body. The seal ring may include a base portion extending in an axial direction within the seal cavity, a leg portion extending from the base portion, and a foot portion extending from the leg portion. When the valve disc of the valve assembly is in the closed position, a primary sealing portion can be formed between the foot portion and the valve disc, and a secondary sealing portion can be formed between the base portion and the first wall of the sealing cavity. The seal ring may accommodate drift of the valve disc at least in part via elastic bending and may provide valve disc tracking via lateral movement within the seal cavity.

Description

Background Technology

[0001] Valve assemblies can employ various sealing systems. For example, in a butterfly valve, the sealing system can be configured to assist the valve disc in suppressing flow through the valve when it is in the closed position. Typically, a sealing assembly that improves the integrity of the seal within the valve and manages valve disc drift and valve disc tracking is desired. Summary of the Invention

[0002] Some examples of this disclosure provide a valve assembly. The valve assembly may include a valve body, a valve passage, a valve disc, a sealing cavity, and a sealing ring. The valve passage extends axially through the valve body. The valve disc may be arranged to selectively inhibit flow through the valve passage in the valve body, and the valve disc may be movable between a valve open position and a valve closed position. The sealing cavity may be formed, or at least partially formed, in the valve body. The sealing ring may include: a base extending axially within the sealing cavity; a leg extending transversely to the axial direction from the base; and a foot extending from the leg. When the valve disc is in the valve closed position, a primary seal may be formed between the foot and the valve disc, and a secondary seal may be formed between the base and a first wall of the sealing cavity.

[0003] Some examples of this disclosure provide a sealing system for use in the sealing ring cavity of a butterfly valve. The sealing system may include a sealing ring having a sealing ring body. The sealing ring body may include: a base extending axially within the sealing ring cavity; a leg extending laterally from the base toward the valve disc of the butterfly valve and cantilevered in cross-section relative to the base; and a foot extending from the leg and configured to engage the valve disc when the butterfly valve is in the closed position. The sealing ring is movable laterally within the sealing ring cavity to accommodate valve disc movement perpendicular to the axial direction.

[0004] Some examples of this disclosure provide a method for sealing a butterfly valve. The method may include rotating the valve disc of the butterfly valve toward a closed position and engaging the valve disc with a foot of a sealing ring disposed within a sealing cavity of the butterfly valve. The sealing ring may include: a base extending axially within the sealing cavity; a leg extending from the base; and a foot extending from the leg. An upstream pressure may be applied to cause the valve disc to drift downstream, allowing the foot to resiliently deflect and form a primary seal between the foot and the valve disc. The base of the sealing ring may withstand torsion and engage with a first wall of the sealing cavity to form a secondary seal between the base and the first wall of the sealing cavity. Attached Figure Description

[0005] Figure 1 This is an isometric view of a butterfly valve in the closed position.

[0006] Figure 2This is an isometric view of a butterfly valve in the open position.

[0007] Figure 3 This is a cross-sectional view of a butterfly valve in the closed position.

[0008] Figure 4 This is a cross-sectional view of a butterfly valve in the open position.

[0009] Figure 5 This is a cross-sectional view of the butterfly valve along its drive shaft.

[0010] Figure 6 It is an isometric view of a sealing ring for a butterfly valve, based on an example of the disclosed technology.

[0011] Figure 7 It is installed in the sealing cavity of the butterfly valve. Figure 6 A partial view of the cross-section of the sealing ring.

[0012] Figure 8 yes Figure 7 A partial view of the cross-section of the sealing ring, including example arrows indicating the direction of valve disc drift and tracking.

[0013] Figure 9 yes Figure 7 A partial view of the cross-section of the sealing ring, including example arrows indicating the rotation points of the sealing ring.

[0014] Figure 10 The valve disc of the butterfly valve is in the closed position and under relatively low pressure. Figure 7 An exemplary finite element analysis of the sealing ring.

[0015] Figure 11 The valve disc of a butterfly valve in the closed position and under relatively high pressure and Figure 7 An exemplary finite element analysis of the sealing ring.

[0016] Figure 12 This is a partial cross-sectional view of an embodiment of a sealing ring including a first contact structure and a second contact structure, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0017] Figure 13 It is the valve disc of the butterfly valve under pressure and Figure 12 A partial view of the cross-section of the sealing ring.

[0018] Figure 14 This is a partial cross-sectional view of another embodiment of a sealing ring, including a first contact structure and a second contact structure, according to an example of the disclosed technology, wherein the sealing ring is disposed within the sealing cavity of a butterfly valve.

[0019] Figure 15This is a partial cross-sectional view of another embodiment of a sealing ring, including a first contact structure and a second contact structure, according to an example of the disclosed technology, wherein the sealing ring is disposed within the sealing cavity of a butterfly valve.

[0020] Figure 16 This is a partial cross-sectional view of another embodiment of a sealing ring, including a first contact structure and a second contact structure, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0021] Figure 17 It is the valve disc of the butterfly valve under pressure and Figure 16 A partial view of the cross-section of the sealing ring.

[0022] Figure 18 This is a partial cross-sectional view of another embodiment of a sealing ring, including a first contact structure and a second contact structure, according to an example of the disclosed technology, wherein the sealing ring is disposed within the sealing cavity of a butterfly valve.

[0023] Figure 19 It is the valve disc of the butterfly valve under pressure and Figure 18 A partial view of the cross-section of the sealing ring.

[0024] Figure 20 This is a partial cross-sectional view of another embodiment of a sealing ring, including a first contact structure and a second contact structure, according to an example of the disclosed technology, wherein the sealing ring is disposed within the sealing cavity of a butterfly valve.

[0025] Figure 21 This is an exemplary finite element analysis of the valve disc and sealing ring of a butterfly valve in the closed position and under relatively high pressure.

[0026] Figure 22 This is another exemplary finite element analysis of the valve disc and sealing ring of a butterfly valve in the closed position and under relatively high pressure.

[0027] Figure 23 This is another exemplary finite element analysis of the valve disc and sealing ring of a butterfly valve in the closed position and under relatively high pressure.

[0028] Figure 24 This is a partial cross-sectional view of an embodiment of a sealing ring including a compression structure, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0029] Figure 25 yes Figure 24 A partial cross-sectional view of the sealing ring, showing the pressure balance channel of the sealing ring.

[0030] Figure 26This is a partial cross-sectional view of another embodiment of a sealing ring including a compression structure, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0031] Figure 27 This is a partial cross-sectional view of another embodiment of a sealing ring including a compression structure, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0032] Figure 28 This is a partial cross-sectional view of another embodiment of a sealing ring including a compression structure, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0033] Figure 29 This is a partial cross-sectional view of another embodiment of a sealing ring including a compression structure, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0034] Figure 30 This is a partial cross-sectional view of another embodiment of a sealing ring including a compression structure, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0035] Figure 31 This is a partial cross-sectional view of another embodiment of a sealing ring including a compression structure, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0036] Figure 32 This is a partial cross-sectional view of another embodiment of a sealing ring including a compression structure, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0037] Figure 33 This is a partial cross-sectional view of another embodiment of a sealing ring including a compression structure, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0038] Figure 34 This is a partial cross-sectional view of another embodiment of a sealing ring including a compression structure, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0039] Figure 35 This is a partial cross-sectional view of another embodiment of a sealing ring including a compression structure, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0040] Figure 36 This is a partial cross-sectional view of another embodiment of a sealing ring including a compression structure, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0041] Figure 37 This is an exemplary finite element analysis of the valve disc and sealing ring of a butterfly valve in the closed position and under relatively low pressure.

[0042] Figure 38 The valve disc of a butterfly valve in the closed position and under relatively high pressure and Figure 37 An exemplary finite element analysis of the sealing ring.

[0043] Figure 39 This is an exemplary finite element analysis of the valve disc and sealing ring of a butterfly valve in the closed position and under relatively low pressure.

[0044] Figure 40 The valve disc of a butterfly valve in the closed position and under relatively high pressure and Figure 39 An exemplary finite element analysis of the sealing ring.

[0045] Figure 41 This is a partial cross-sectional view of an embodiment of a sealing ring including a secondary sealing member, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0046] Figure 42 This is a partial cross-sectional view of another embodiment of a sealing ring including a secondary sealing member, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0047] Figure 43 This is a partial cross-sectional view of another embodiment of a sealing ring including a secondary sealing member, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0048] Figure 44 This is a partial cross-sectional view of another embodiment of a sealing ring including a secondary sealing member, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0049] Figure 45 This is a partial cross-sectional view of another embodiment of a sealing ring including a secondary sealing member, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0050] Figure 46 This is a partial cross-sectional view of another embodiment of a sealing ring including a secondary sealing member, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0051] Figure 47 This is a partial cross-sectional view of another embodiment of a sealing ring including a secondary sealing member, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0052] Figure 48This is a partial cross-sectional view of another embodiment of a sealing ring including a secondary sealing member, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0053] Figure 49 This is a partial cross-sectional view of another embodiment of a sealing ring including a secondary sealing member, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0054] Figure 50 This is a partial cross-sectional view of another embodiment of a sealing ring including a secondary sealing member, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0055] Figure 51 This is a partial cross-sectional view of another embodiment of a sealing ring including a secondary sealing member, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0056] Figure 52 This is a partial cross-sectional view of another embodiment of a sealing ring including a secondary sealing member, according to an example of the disclosed technology, wherein the sealing ring is disposed in the sealing cavity of a butterfly valve.

[0057] Figure 53 This is a partial cross-sectional view of an embodiment of a secondary sealing ring according to an example of the disclosed technology, the sealing ring being disposed in the sealing cavity of a butterfly valve.

[0058] Figure 54 yes Figure 53 A partial cross-sectional view of the sealing ring, showing the pressure balance channel of the sealing ring.

[0059] Figure 55 This is a partial cross-sectional view of another embodiment of a secondary sealing ring according to an example of the disclosed technology, the sealing ring being disposed in the sealing cavity of a butterfly valve.

[0060] Figure 56 This is a partial cross-sectional view of another embodiment of a secondary sealing ring according to an embodiment of the disclosed technology, the sealing ring being disposed in the sealing cavity of a butterfly valve.

[0061] Figure 57 The valve disc of the butterfly valve is in the closed position and under relatively low pressure. Figure 56 An exemplary finite element analysis of the sealing ring.

[0062] Figure 58 The valve disc of the butterfly valve is in the closed position and under relatively low pressure. Figure 56 An exemplary finite element analysis of the sealing ring. Detailed Implementation

[0063] The concepts disclosed in this discussion are described and illustrated with reference to exemplary arrangements. However, the application of these concepts is not limited to the construction details and component arrangements in the exemplary examples and can be practiced or implemented in a variety of other ways. The terminology in this document is for descriptive purposes only and should not be considered limiting. Words such as “including,” “comprising,” and “having,” and variations thereof, as used herein, are intended to cover the items listed thereafter, their equivalents, and others.

[0064] The sealing ring systems, valve assemblies, and methods disclosed herein can be implemented in a variety of different forms. Therefore, although several specific examples are discussed herein to illustrate the principles of the technology disclosed, the technology disclosed is not intended to be limited to the examples shown.

[0065] As briefly described above, valves can utilize various sealing elements and sealing systems to selectively prevent (or substantially reduce) flow through the valve. For example, control valves (such as butterfly valves, ball valves, or other types of rotary valves) include seals, such as sealing rings. These valves typically include control elements (e.g., valve discs, balls, segmented balls, etc.) that can be rotated via a drive shaft to control the flow of fluid through pipes or other containers at different temperatures and pressures. Such control valves can be installed in pipelines to control various fluids or flowing media, including gases, liquids, slurries, etc. Various industries, including oil and gas production, transportation and refining, power generation, pulp and paper, metals and mining, chemicals, and the food and beverage industry, employ these control valves.

[0066] When under pressure, the control element of a control valve (e.g., a valve disc or ball) can drift or float downstream. That is, when the valve is in the closed position relative to the pressurized flow medium flowing from upstream to downstream, the pressure from the flow medium can push the control element downstream, causing drift. Although typically limited by the rod or other structure supporting the control element, valve disc floating or drifting can still occur to varying degrees, depending on factors such as the stiffness of the shaft or control element, valve size and other conventional configurations, fluid pressure, and clearances within the transmission system. Valve disc (or control element) drift is unavoidable and, especially in cases of significant drift, can lead to sealing strain or leakage in existing sealing designs.

[0067] Some conventional valves may include seals designed to withstand valve disc drift. However, seals often struggle to simultaneously withstand low drift at low pressures and high drift at high pressures, especially when both high and low pressures exist throughout the valve's lifespan. In particular, for conventional seals, recovering from a high-pressure event to a low-pressure environment while maintaining seal integrity and continuous shut-off performance can be the most challenging scenario.

[0068] Some conventional valve seals can be made from one or more polymers, including, for example, polytetrafluoroethylene (PTFE) and ethylene-tetrafluoroethylene copolymer (ETFE), which typically exhibit good abrasion resistance and resistance to pressure drop fluctuations. Such polymer seals are often referred to as "soft" seals. The compliance of the polymer allows for pressure drop memory (e.g., fluctuating high and low pressures) while generally maintaining shut-off and leakage requirements. Provided the handling conditions are favorable, such polymer seals are useful under low leakage and low torque conditions. However, depending on the type of flowing medium and operating temperature, polymer seals can experience wear, degradation, or even failure.

[0069] For higher temperature conditions that may not be suitable for polymer seals, valve sealing rings can be made of metal. However, metal sealing rings typically wear relatively quickly using conventional methods, thus requiring coating or hardening treatments and more frequent replacement. Furthermore, because metals do not have the same degree of compliance as polymers, conventional metal seals may not effectively maintain their closing performance under pressure fluctuations.

[0070] Typically, it is desirable to have a seal that can withstand cycling (e.g., cycling between high and low pressure loads, or cyclic rotation of a control element between open and closed positions), temperature, and other operating conditions that metal seals can withstand, while functioning like a soft (e.g., polymer) seal to provide the same precision and limited leakage as a typical soft seal. Some conventional metal seal designs attempt to match the leakage of soft seals. However, the load required to bring a metal seal into contact with a control element is much greater than that required for a soft seal. The higher load required to close a soft seal translates to a greater disconnecting torque (i.e., the torque required to disengage a closed valve from its seat). In contrast, when maintaining the same disconnecting torque value between conventional soft seals and conventional metal seals, the leakage of metal seals is much greater than that of soft seals, and therefore some leakage requirements may not be met.

[0071] Conventional metal seals are typically categorized into several types based on their deformation mechanisms. Generally, elastic deformation is desirable to cope with pressure variations in a single system. One type of conventional metal seal is the expansion seal. These seals typically rely on radial expansion (e.g., caused by circumferential stress) to elastically expand and recover within their limits. Furthermore, in response to valve disc drift, these seals typically deform radially (e.g., radial expansion). Another type of conventional metal seal is the bending or flexing seal. These seals typically rely on the legs of the seal bending and flexing as the valve disc drifts. These seals are typically clamped in place and can be pressurized. For both categories, it is generally desirable to keep the seal within its elastic deformation zone regardless of the amount of valve disc drift occurring in a given valve assembly.

[0072] These conventional seals can have various limitations. For example, expansion seals may withstand high seat loads and may yield along the diameter or crush along the pipe direction under high pressure. Flexural seals may also yield under high pressure or have stiffness that results in excessive disconnecting torque and is not as expected. Furthermore, these conventional seals are typically clamped in place, which can lead to misalignment between the seal and the valve disc, resulting in leakage over the valve's service life. Therefore, these conventional designs often struggle to achieve consistent performance.

[0073] As mentioned above, conventional valve seals perform poorly under high valve disc drift, and therefore the valve seat may easily yield when exposed to high pressure. When these seals are exposed to high pressure, yielding may occur in the radial or downstream direction. When yielding occurs and the pressure in the system decreases, the sealing performance deteriorates due to the plastic deformation of the seal. In other words, after exposure to high pressure, the seal will not return to its original leakage performance (e.g., under low pressure).

[0074] Especially for butterfly valves, providing a valve seal that effectively manages disc drift can be challenging. As mentioned above, disc drift refers to the downstream movement of the valve disc when closed and under load (i.e., pressure). This drift is caused by the bending of the valve trim clearance and elastic shaft under load. In a non-limiting example, the downstream disc drift of a six-inch valve can reach several thousandths of an inch (e.g., 0.040 inches), which can result in downstream and radial interferences far exceeding what is expected in conventional seal designs. For example, metal-to-metal seals may rely on only several thousandths of an inch of disc-seal interference regardless of the disc drift state. Thus, for example, the disc drift distance can be, for example, eight to forty times the amount of interference designed for the seal. Conventional metal seals cannot cope with this disc drift and may correspondingly yield under high pressure conditions. Alternatively, if the seals are designed to resist yielding, they are often too stiff and require very high operating torques, which may exceed the limits of the valve trim. Similarly, using materials with higher yield strength in conventional designs can also result in high-moment conditions if yielding does not occur. Therefore, conventional methods may be limited to relatively narrow pressure conditions, and yielding at higher pressures—with a corresponding decrease in sealing performance—is largely unavoidable.

[0075] The aspects of this disclosure can address these and other deficiencies of conventional sealing systems used in control valves. For example, the sealing ring according to this disclosure can provide an advantageous combination of materials and geometries that can effectively accommodate high valve disc drift with minimal plastic deformation, limit leakage to meet required standards, and provide valve disc tracking management to prevent or reduce centerline misalignment, as well as other advantages described below.

[0076] Typically, the sealing rings disclosed herein provide sealing elasticity by using elastically deformable legs. In some embodiments, sealing elasticity can be provided by a combination of bending (in cross-section) and torsion of the cantilevered legs to elastically withstand valve disc drift while maintaining adequate sealing contact with the associated components. By optimizing geometric parameters (e.g., leg thickness, outer diameter, post / base thickness, post / base height, etc.) and material properties (e.g., yield strength), the seal can exhibit elasticity under pressure and valve disc drift. Therefore, embodiments of the seals disclosed herein can withstand a variety of pressure fluctuations (e.g., compared to conventional seals) while maintaining sealing load upon returning to a low-pressure state.

[0077] Additionally, the sealing rings disclosed herein can provide improved valve disc tracking management. For example, the seals disclosed herein can track the valve disc of a butterfly valve in a direction parallel to the radial or lateral direction, thereby allowing the seal to reach and engage the valve disc regardless of its location. Unlike many conventional seals, seals according to some embodiments of this disclosure are not clamped within the sealing cavity to prevent movement (e.g., radial or torsional movement), thus allowing free movement (e.g., radial translation) within the sealing cavity to accommodate valve disc positions under various pressures. Furthermore, not clamping the sealing ring to prevent its movement within the valve's sealing cavity makes the resilient behavior of the sealing ring more predictable. In some embodiments, as further detailed below, the sealing ring can engage with the downstream wall of the sealing cavity during operation but not with the upstream wall, thereby leaving a nominal clearance between the upstream wall of the sealing cavity and the seal. This nominal clearance allows the seal to torsionally rotate under load (e.g., providing a third-stage seal at the upstream wall) and translate within the sealing cavity to reach the valve disc.

[0078] According to the elements disclosed herein, the geometry of the sealing ring can be adjusted to exhibit elasticity under specified pressure conditions. Therefore, in environments where high-cost, high-yield materials are typically required, low-cost, low-yield materials can be used. The overall geometry disclosed herein provides customizable and repeatable leakage requirements.

[0079] Furthermore, embodiments of this disclosure can provide advantageous torque assistance. For example, in use, when pressure is applied to the axial side of the valve disc, a sealing ring according to embodiments of this disclosure can contact the valve disc and form a seal to form a primary seal. The sealing ring can also contact the sidewalls of the sealing ring cavity (e.g., at the retainer forming the sealing ring cavity) to form a secondary seal. In this respect, there is a diameter difference between the primary and secondary seals. Due to the difference in seal diameter, a pressure difference (i.e., differential pressure) occurs on a portion of the sealing ring (e.g., the leg of the sealing ring). Such a differential pressure can cause the net force acting on the leg to be in the same direction as the valve disc drift, and the pressure contributes to the secondary seal. The behavior of the sealing ring under pressure (e.g., bending of the sealing ring leg) can correspondingly reduce the net load between the sealing ring and the valve disc, thereby allowing a lower disconnecting torque (e.g., compared to conventional seals, such as expansion seals), and contributing to the formation of a particularly robust secondary seal. For example, this low-torque behavior allows for a higher upper limit of pressure capacity compared to sealing rings that rely solely on radial expansion to resist valve disc drift.

[0080] Typically, the manufacturability of the sealing rings according to embodiments of this disclosure also makes them superior to conventional sealing rings. For example, the geometry of the sealing rings disclosed herein can be easily machined using standard inserts and tool holders (e.g., turning on a lathe). In contrast, some conventional sealing rings combine complex cross-sections with multiple angles and thin cross-sectional geometries, making the sealing rings prone to breakage and requiring specialized tools. Relatedly, the cross-sectional geometry of the sealing rings disclosed herein also advantageously manipulates valve disc drift and compressive strength by bending and providing torsional stiffness (e.g., as described above). Overall, the nominal geometry of the seals disclosed herein can be much thicker than that of conventional seals (e.g., expander-type seals). Due to the relatively stiff cross-section, this geometry provides improved stability in manufacturing and machining applications requiring low shape errors and smooth surface finishes.

[0081] Now refer to the attached diagram, Figure 1 and Figure 2 An exemplary butterfly valve 100 is shown. The butterfly valve 100 includes a valve body 102 and a valve passage 104 extending axially through the valve body 102. The butterfly valve 100 also includes a valve disc 106, which is actuable via a drive shaft 108. Figure 1 Specifically shown is a butterfly valve 100 in the closed position, in which the valve disc 106 blocks the valve passage 104 to prevent fluid flow through the valve passage. Figure 2 A butterfly valve 100 is shown in the open position, in which the valve disc 106 allows fluid to pass through the valve passage 104.

[0082] Figure 3 and Figure 4 Cross-sections of valve 100 in the closed and open positions are shown. Figure 3 and Figure 4 The cross-sectional view shows the sealing ring cavity 112. The boundary of the sealing ring cavity 112 is at least partially formed by the valve body 102 and the seal retainer 114. Further as... Figure 3 and Figure 4 As shown, an exemplary sealing ring 120 is disposed in a sealing ring cavity 112. Figure 3 and Figure 4 The sealing ring 120 shown is merely an example and, as will be described below, other sealing rings including sealing rings with different geometries may be used in the butterfly valve 100 or other valve assemblies.

[0083] Figure 5 Another cross-sectional view of valve 100 is shown. Figure 5The cross-sectional view shows other components of valve 100. These other components include a sealing gasket 124, a bearing 126, an expansion pin 128, a gasket shaft 130, a gasket spring 132, a gasket, and an end cap 136. Figure 6 It shows in Figure 3 and Figure 4 Visible sealing ring 120. Sealing ring 120 includes sealing ring body 140. Reference Figures 7 to 11 The features and advantages of the sealing ring 120 are discussed below. Figures 7 to 11 Each shows a cross-section of the sealing ring 120.

[0084] like Figure 7 As shown, the body 140 of the sealing ring 120 includes a base (e.g., a post) 142, a leg 144, and a foot 146. The base 142 extends axially within the sealing ring cavity 112 between a first wall 150 and a second wall 152 of the sealing ring cavity 112. In the illustrated example, the first wall 150 of the sealing ring cavity 112 is formed by a seal retainer 114, and the second wall 152 of the sealing ring cavity 112 is formed by a valve body 102. Furthermore, in the illustrated embodiment, the first wall 150 of the sealing ring cavity 112 is oriented at a downstream side 156 of the sealing ring 120, and the second wall 152 of the sealing ring cavity 112 is oriented at an upstream side 158 of the sealing ring 120. Upstream and downstream refer to the intended flow direction of fluid through the passage 104 of the valve 100. The flow direction is also aligned with the axial direction 162 of the valve 100. However, in other embodiments, the flow direction may be different.

[0085] Continue to refer to Figure 7 Leg 144 extends from base 142 toward valve disc 106 in a lateral direction 164. In the illustrated view, the lateral direction refers to a specific radial direction, wherein, in the illustrated cross-sectional orientation, generally, the radial direction is perpendicular to the axial direction 162 and the lateral direction is also perpendicular to the axial direction 162. In the illustrated embodiment, in cross-section, leg 144 is cantilevered relative to base 142. Furthermore, leg 144 extends from base 142 along the height of base 142 (i.e., along the axial direction 162) at a position closer to the upstream side 158 of sealing ring 120. That is, leg 144 is positioned closer to the second wall 152 of sealing ring cavity 112, particularly when the force acting on valve disc 106 that would cause valve disc to drift in the downstream direction is small or nonexistent. Sealing ring body 140 also includes foot 146. The foot 146 extends from the leg 144 and is configured to seal against the valve disc 106 when the valve disc 106 is in the valve closed position.

[0086] exist Figure 7In the illustration, valve disc 106 is shown in the valve closed position, in which there is little or no valve disc drift. That is, due to the upstream fluid pressure acting on valve disc 106, valve disc 106 moves a very short distance or not at all in the downstream direction. When valve disc 106 is in the illustrated valve closed position (or in the valve closed position and experiencing valve disc drift), sealing ring 120 forms a primary seal with valve disc 106 and a secondary seal with sealing ring cavity 112. More specifically, in the illustrated embodiment, the foot 146 of sealing ring 120 forms a primary seal 168 with valve disc 106, and the downstream side 156 of the base 142 of sealing ring 120 forms a secondary seal 170 with seal retainer 114 at the first wall 150 of sealing ring cavity 112 (wherein the primary seal 168 and the secondary seal 170 are sealing areas between corresponding components).

[0087] Typically, each component of the sealing ring body 140 can define both its height and thickness. For example, the base 142 can define a base height along an axial direction 162, said base height extending between the first wall 150 and the second wall 152 of the sealing ring cavity. The base 142 can also define a base thickness along a lateral direction 164. Figure 7 In the illustrated embodiment, the base height is greater than the base thickness. However, in other embodiments, such as those with a shorter sealing ring cavity 112 (i.e., along the axial direction 162), the base thickness may be greater than the base height (see, for example, Figure 18 and Figure 19 ).

[0088] The base 142 may also define a downstream portion 174 and an upstream portion 176, the upstream portion being segmented approximately by the location where the leg 144 extends from the base. In the illustrated embodiment, the downstream portion 174 and the upstream portion 176 of the base 142 both have the same or similar base thickness but different heights (corresponding to the leg 144 positioned closer to the second wall 152 of the sealing ring cavity 112). However, in other embodiments, the downstream portion 174 and the upstream portion 176 of the base 142 may have different thicknesses (see, for example, Figure 16 and Figure 17 ).

[0089] Still referencing Figure 7The sealing ring body 140 is sized such that the foot 146 extends at least partially to the outside of the sealing ring cavity 112 and into the valve passage 104 to engage the valve disc 106 when the valve disc 106 is in the valve closed position. The foot 144 generally divides the sealing ring cavity 112 into a downstream volume 180 and an upstream volume 182. Furthermore, the base 142 generally forms an outward volume 184 between the base 142 and the third wall 188 of the sealing ring cavity 112. As shown, the third wall 188 may extend between and substantially perpendicular to the first and second walls of the sealing ring cavity 112 and may be formed by the valve body 102 and the seal retainer 114. Also... Figure 7 As shown, a gap 192 exists along the axial direction between the base 142 and the second wall 152 of the sealing ring cavity 112. (Refer to...) Figure 8 In further detail, clearance 192 can provide certain pressure equalization and other benefits related to valve performance and assembly, including improving the ability of the sealing ring body 140 to track the movement of the disc 106.

[0090] Now for reference Figure 8 This shows again Figure 7 A sectional view. For example... Figure 8 As highlighted, gap 192 allows for pressure equalization between the upstream volume 182 and the outer volume 184 of the sealing ring cavity 112. As shown, when valve disc 106 is in the valve closed position (or valve open position), the upstream pressure of valve passage 104 can be the same as or similar to the pressure of each of the upstream volume 182 and the outer volume 184, such as... Figure 8 As shown in P1. When the valve disc 106 is in the valve closed position and fluid pressure acts on the upstream side of the valve disc 106, the primary seal 168 and the secondary seal 170 prevent fluid from flowing from the upstream side of the valve disc 106 to the downstream side of the valve disc 106, thereby creating a pressure difference within the valve passage 104 and between the upstream volume 182 and the downstream volume 180 of the sealing ring cavity 112, as shown in P1. Figure 8 P1 and P2 are shown in the diagram.

[0091] Continue to refer to Figure 8 Another advantage of this valve system is that the presence of clearance 192 allows the sealing ring 120 to move laterally 164 to accommodate valve disc tracking, and it exhibits less resistance compared to conventional devices. Typically, valve disc tracking refers to the lateral movement of the valve disc 106, such as... Figure 8As indicated by lateral arrow 164 on the valve disc. During assembly or use, the valve disc 106 may move laterally, potentially resulting in loss or weakening of contact with a conventional sealing ring. Advantageously, when the valve disc 106 is off-center, the sealing ring 120 is also allowed to move in the lateral direction 164 to engage the valve disc 106 (e.g., maintain sealing contact with the valve disc). In the illustrated embodiment, gap 192 can facilitate lateral movement of the sealing ring 120, specifically because the sealing ring 120 is not correspondingly immovably clamped within the sealing ring cavity 112 as a conventional valve seal.

[0092] In addition, it can be along Figure 8 The valve disc drift occurring in the axial direction 162 indicated by the middle arrow is accommodated by the sealing ring 120 via the elastic bending of the leg 144 and the torsion of the cross section of the base 142. Figure 9 A schematic representation of the sealing ring 120 is shown. Specifically, Figure 9 The first and second bending moments of the sealing ring 120 around rotation points M1 and M2 are shown. In use, when the sealing ring 120 actively provides a seal between the upstream and downstream sides of the valve passage 104 via the primary seal portion 168 and the secondary seal portion 170, multiple forces are applied to the sealing ring body 140. The force applied to the foot 146 at the primary seal portion 168 and the force applied to the base 142 at the secondary seal portion 170 form a bending moment of the foot 144 at the first rotation point M1 and a torque of the base 142 at the second rotation point M2. In this respect, for example, the second rotation point M2 may correspond to the sealing contact point of the base 142 (e.g., for a secondary seal portion with a retainer ring, as discussed further above and below).

[0093] It should be understood that, Figure 9 The bending and torsion points shown are merely examples, and bending and torsion can occur at different locations on the sealing ring body 140, depending on the geometry of the specific sealing ring, valve configuration, or handling conditions. However, it is worth noting that the overall favorable elastic deformation of the sealing ring body 140 is the result of a combination of carefully designed geometry and material composition, a result that can be optimized through various parameters, including operating conditions (e.g., temperature, pressure, fluid type, etc.) and valve specifications (e.g., size, rated flow rate, material composition, etc.).

[0094] Figure 10 and Figure 11 Exemplary finite element analyses of the sealing ring 120 are shown when low and high pressures are applied to the valve disc 106, respectively. Figure 10As shown, the stress acting on the sealing ring body 140 is minimized, and the gap 192 can be maintained, allowing the sealing ring body 140 to move easily laterally to follow the valve disc 106, and enabling pressure balance to be achieved via the gap 192 (e.g., as per [reference to...]). Figure 8 (as stated above). Conversely, Figure 11 The diagram illustrates stress concentration near the foot 146 and leg 144 when the valve disc 106 bends the leg 144 and tilts the base 142 to generate a greater force at the secondary seal 170. As shown, the bending of the foot 146 or leg 144 of the sealing ring 120 is generally elastic and therefore the geometry will correspondingly return to its original shape once the pressure on the valve disc 106 decreases. Also... Figure 10 and Figure 11 As shown, due to the high pressure load caused by the torsion on the body 140, the size of the gap 192 between the base 142 at the upstream side 158 and the second wall 152 of the sealing ring cavity 112 may decrease, although the gap 192 may remain unchanged under certain high pressure conditions (e.g., as shown in the figure).

[0095] generally, Figures 1 to 5 The valve assembly of butterfly valve 100 is shown, and Figures 6 to 11 An exemplary configuration of the sealing ring 120 is shown, which can be used in the valve assembly of the butterfly valve 100. As described above, the sealing ring 120 configuration shown in these figures is presented by way of example, and other configurations of the sealing ring are also possible, as described below. Relatedly, Figures 1 to 5 The specific butterfly valve 100 shown is merely an example, and the sealing ring 120 can be used with other variations of the valve assembly. Furthermore, some of the figures below show portions of the valve, which will be referred to as butterfly valve 100, and its corresponding components. However, it should be understood that... Figures 7 to 58 The valve shown can be other valve components and is referred to as butterfly valve 100 for example only.

[0096] Similarly, the following text will refer to Figures 12 to 58 Other geometries of the sealing ring are described, and where applicable, the same reference numerals as those for sealing ring 120 are used. Therefore, unless otherwise stated, the discussion of similarly numbered parts above also applies below, and vice versa. Correspondingly, although the same reference numerals are used to denote the example sealing ring 120 described herein, it should be understood that variations of other geometries can provide embodiments of various sealing rings with different characteristics, while still possessing the same or similar physical characteristics or functions as the other sealing rings discussed herein. The features of the sealing ring 120 described below, unless otherwise stated... Figures 6 to 11Parts of the sealing ring 120 shown, or those not discussed therein, will be discussed separately and given appropriate reference numerals as appropriate. It should also be understood that relevant features, geometries, and components of any exemplary sealing ring 120 described in this disclosure may be combined, integrated, or substituted with any other features, geometries, and components of other sealing rings 120 described and shown in this disclosure (e.g., replacing a particular body, arm, foot, or contact surface geometry of one ring 120 in another ring 120).

[0097] Figures 12 to 23 An additional embodiment of the sealing ring 120 is shown. For example, Figures 12 to 23 The sealing ring 120 includes a first contact structure 210 located at the secondary sealing portion 170 and a second contact structure 212 located at the third-level contact point 214. As described above, the secondary sealing portion 170 is formed between the base 142 of the sealing ring 120 and a first (downstream) wall 150 (e.g., a seal retainer 114) of the sealing ring cavity 112 located at the downstream portion 174 of the base 142. Correspondingly, the third-level contact point 214 may form a third-level seal between the base 142 of the sealing ring 120 and a second (upstream) wall 152 (e.g., a valve body 102) of the sealing ring cavity 112 located at the upstream portion 176 of the base 142.

[0098] also, Figures 12 to 23 Each of the first contact structure 210 and the second contact structure 212 shown is offset in the lateral direction. In particular, the first contact structure 210 is closer to the valve disc 106 than the second contact structure 212, and the second contact structure 212 is closer to the third wall 188 of the sealing ring cavity 112 than the first contact structure 210.

[0099] Now for reference Figure 12 An exemplary embodiment of a sealing ring 120 located in the sealing ring cavity 112 of valve 100 is shown. As summarized above, Figure 12 The sealing ring 120 includes a first contact structure 210 and a second contact structure 212. Along the indicated orientation, a gap 192 is formed between the second contact structure 212 and the second wall 152 of the sealing ring cavity 112. This gap is present when the valve disc 106 is in the valve open position and when the valve disc 106 is in the valve closed position and the fluid force acting on the valve disc 106 is relatively small (e.g., none). Figure 12 A gap 192 exists. Conversely, when the force applied to the valve disc 106 is sufficiently large (e.g., through outward and downstream torsional rotation of the sealing ring 120, such as...), Figure 13 As shown), gap 192 can be closed (e.g., eliminated).

[0100] refer to Figure 13 When the force F acting on the valve disc 106D When larger (and) Figure 12 In contrast, the corresponding first force F1 can be applied to the foot 146 of the sealing ring 120 to form a primary seal 168, thereby causing a second force F2 to be applied to the first contact structure 210 to form a secondary seal 170. Furthermore, when force F... D When sufficiently large, the sealing ring body 140 can rotate (e.g., downstream and outward as shown), allowing a third force F3 to be applied to the second contact structure 212 at the third-stage contact point 214 (e.g., having a corresponding third-stage seal). Specifically, in the illustrated example, the contact diameter of the secondary seal 170 is larger than that of the primary seal 168, causing a torque to be generated in the sealing ring 120 through the contact between the valve disc 106 and the foot 146, while the base 142 correspondingly undergoes torsional rotation and establishes (or reinforces) the third-stage seal (e.g., at contact point 214 as shown). Typically, F2 and F3 thus increase with valve disc drift, and the sealing performance of the secondary and third-stage seals also improves accordingly with the increase in valve disc drift. Furthermore, even if valve disc drift is eliminated (or reduced), the seal 168 can still elastically recover to an appropriate sealing configuration for lower pressures (e.g., as shown). Figure 12 (As shown).

[0101] In other words, during use, the fluid pressure acting on the valve disc 106 can cause pressure along F... D Valve disc drift in direction. When valve disc 106 drifts, the engagement of valve disc 106 with cantilever leg 144 causes leg 144 to deflect, resulting in rotation of the cross-section of sealing ring 120 (e.g., by torsion applied via leg 144). Therefore, when the elastic rotation of sealing ring 120 closes gap 192, mechanical leverage can increase the load on secondary seal 170 and the load on third-stage seal at point 214. Furthermore, the contact at secondary seal 170 and third-stage contact point 214 via first contact structure 210 and second contact structure 212 can provide anti-rotation features for sealing ring 120 to resist excessive rotation.

[0102] Return to reference Figure 12 When the sealing ring 120 is first installed in the valve assembly, the gap 192 exists and allows the sealing ring 120 and valve disc 106 to track (e.g., translate) in the lateral direction. This tracking capability is the same as described above, thus advantageously allowing... Figure 12The sealing ring 120 moves laterally within the sealing ring cavity 112 to contact the valve disc. In contrast, some conventional sealing rings are clamped or otherwise fixed within the sealing ring cavity and cannot move laterally. This can lead to unwanted valve disc misalignment when the valve disc moves laterally. However, as described above, the rotation of the sealing ring 120 caused by the load on the valve disc 106 causes the gap 192 to close (e.g., via torsion on the sealing ring 120), such that under certain operating conditions, a third-stage seal (i.e., replacing the gap 192) can be formed on the upstream side of the sealing ring cavity.

[0103] refer to Figure 12 and Figure 13 The first contact structure 210 and the second contact structure include generally rounded (e.g., rounded corners) surfaces that contact the respective walls 150, 152 of the sealing ring cavity 112. The rounded surfaces advantageously prevent the sealing ring 120 from engaging or wedging within the sealing ring cavity 112. Specifically, the rounded surfaces become three-dimensional annular sections and allow the sealing ring 120 to rotate (e.g., oscillate) about the contact points of the anti-engaging contact structures 210, 212. Thus, for example, the rounded surfaces can allow the seal to rotate relative to a second torque while in a clamped state (see, for example, ...). Figure 9 The rotation point M2 in the seal is used to reduce strain on the legs of the seal. Furthermore, the rounded surface allows for more precise control of the contact position between the sealing ring and the corresponding cavity wall (e.g., controlling the offset between contact points on relative cavity walls 150, 152). This, in turn, allows for better control of the upstream wall at the seal contact point (e.g., ...). Figure 13 The wall 152 shown is before the second moment (e.g., Figure 9 The amount of rotation of the rotation point M2 in the middle.

[0104] Generally, various combinations of selectively rounded surfaces, legs of optional length and thickness, or selective lateral placement of the base and contact points allow for tailoring metal seals to specific applications to minimize the likelihood of valve disc drift increasing and causing permanent deformation. However, other contact structures and geometries are also feasible. For example, if gap 192 does exist, contact structures 210, 212 can typically be left unrounded (e.g., with rounded corners) and therefore can have relatively sharp or rectangular features.

[0105] In other configurations, other spacing and geometries are also possible, including adjustments to specific seals as described above. In this regard, Figure 14 and Figure 15 An example configuration is shown, which includes a greater lateral distance between the contact points of the first contact structure 210 and the second contact structure 212. See in particular... Figure 15It employs a relatively square or sharp contact structure 212, although other configurations can also position the contact points along the rounded surface (as described above).

[0106] Typically, as mentioned above, Figures 12 to 23 Each of the sealing rings 120 includes a first contact structure 210 and a second contact structure 212, the first and second contact structures being laterally offset and each configured to engage a corresponding wall 150, 152 of the sealing ring cavity 112. Furthermore, Figures 12 to 23 Each of the sealing rings 120 is configured to form a gap 192 between the upstream portion 176 of the base 142 and the second wall 152 of the sealing ring cavity 112 when the seal is not under load. (The remaining text is omitted.) Figures 14 to 20 Other details are omitted to avoid repetition; however, it should be understood that similar features, mechanical structures and advantages described above can be applied to these embodiments of the sealing ring 120.

[0107] Figures 21 to 23 Finite element analysis of an additional embodiment of the sealing ring 120 is shown. As illustrated in these figures, when the valve disc 106 acts at the foot 146 of the sealing ring 120, a seal is formed between the foot 146 and the valve disc 106, and between the first contact structure 210. The first contact structure 210 and the second contact structure 212 act as pivot points for the base 142 and engage with the walls 150, 152 of the sealing ring cavity 112 to restrict torsion in the sealing ring 120. As shown, bending along the leg 144 results in stress concentration. These stress concentrations can vary based on a given geometry of the sealing ring 120, but ultimately provide resilient bending without yielding.

[0108] Figures 24 to 40 An additional embodiment of the sealing ring 120 is shown. For example, Figures 24 to 40 The sealing ring 120 includes a compression structure 230 located at the base 142 of the sealing ring body 140, which functions similarly to a spring. Typically, the compression structure 230 can provide a load or one or more compression features to reinforce the retainer of the secondary seal 170, which is particularly beneficial under low-pressure sealing conditions. The compression structure 230 can provide an initial mechanical load at the secondary seal 170, which in turn provides an initial seat load at the valve disc 106, thus facilitating sealing at relatively low pressures (i.e., low fluid pressure on the valve disc 106). Furthermore, as described above, the offset between the diameter of the primary seal 168 and the diameter of the secondary seal 170 provides a pressure-assisted region that increases the pressure on the secondary seal 170.

[0109] Typically, the compression load provided by the compression structure 230 is high enough to facilitate a low-pressure seal, but low enough to ensure that the sealing ring 120 can track the valve disc 106 in the lateral direction. That is, even if the centerlines of the sealing ring 120 and the valve disc 106 are misaligned, the sealing ring 120 can still move laterally (i.e., perpendicular to the pipe axis) within the sealing ring cavity 112. Therefore, Figures 24 to 40 The embodiment of the sealing ring 120 shown provides similar advantageous valve disc tracking as described above with reference to the previous figures.

[0110] also, Figures 24 to 40 The exemplary sealing ring 120 shown may include one or more pressure balancing channels 232 (see, for example, Figure 24 and Figure 25 The pressure balancing channel 232 can be configured as one or more sectors, which can allow for pressure from upstream and pressure in the upstream volume 182 (e.g., Figure 8 The P1) in the compression structure 230 migrates to the outward volume 184. Typically, the pressure balancing channel 232 can prevent pressure from being trapped behind the sealing ring 120 and can help with pressure-assisted sealing.

[0111] Some embodiments of the compression structure 230 of the sealing ring 120 may include one or more compression legs. A compression leg typically refers to a cross-sectional feature that is axisymmetric. For example, Figures 24 to 29 The compression structure 230 includes a single compression leg feature. This single leg compression (e.g., bending) feature creates interference between the sealing ring 120, the seal retainer 114, and the valve body 102 within the sealing ring cavity 112. The single compression leg feature of the compression structure 230 may be formed at the outer diameter of the base 142 (see [reference]). Figures 24 to 28 and Figures 30 to 35 It can also be formed or provided at the inner diameter of the base 142 (see...). Figure 29 and Figure 36 ).

[0112] In some embodiments, the sealing system according to this disclosure may include a sealing ring 120 and a sealing ring body 140, the sealing ring and the sealing ring body being integrally formed. In other embodiments, the sealing system may include additional components not integrally formed with the sealing ring body 140 (see...). Figure 36 ).

[0113] refer to Figure 24 and Figure 25 The compression structure 230 can be a cut in the outer diameter of the base 142 (e.g., a machined notch or other recess). For example, Figure 24 and Figure 25 The compression structure 230 in the middle is a notch of approximately 35° (e.g., similar to a lathe blade). For example... Figure 24 and Figure 25 The V-shaped profile of the compression structure shown facilitates elastic bending and provides a spring constant and secondary seat load for the seal retainer 114. This compression structure 230 can be produced using various machining methods, such as insert fitting, grooving tools, or contouring. Figures 12 to 23 similar, Figures 24 to 40 Some of the sealing rings 120 may include a first contact structure 210 and a second contact structure 212 offset in the axial direction. This can provide the same as described above. Figures 12 to 23 Similar advantages discussed.

[0114] Figures 26 to 29 The compression structure 230, which is a single compression leg feature, is also shown. Figures 26 to 28 Overall, a single compression leg feature is shown formed by a groove or slot extending perpendicular to the outer diameter of the sealing ring 120 (i.e., in the lateral direction relative to the figures), and Figure 29 Includes a groove or slot extending perpendicular to the inner diameter of the base 142.

[0115] Figures 30 to 35 An embodiment of a compression structure 230 configured as a dual-leg compression feature is shown. The dual-leg compression feature integrally forms a C-shaped cross-section, which provides a double-acting load within the sealing ring cavity 112. The seal retainer 114 side of the compression structure 230 may incorporate a local toroidal feature such that when the primary seal 168 engages with the valve disc 106 (e.g., during valve disc drift), seal torsion allows the secondary seal 170 to swing and remain in contact with the seal retainer 114. Figures 30 to 35 As shown, the dual-leg compression feature can have various geometries, and each geometry typically allows compression of both legs to occur at the same diameter, resulting in retainer compression rather than artificial seal wobbling. Generally, elastic bending should occur in the compression structure 230 on the leg closest to the valve body 102 within the sealing ring cavity 112; however, the other leg (i.e., the leg closest to the seal retainer 114) can also bend to elastically provide load (e.g., due to the thinner configuration of the upstream leg, such as...). Figures 27 to 29 (As shown in the overall diagram).

[0116] Typically, when the contact diameter between the sealing ring 120 and the sealing retainer 114 (i.e., at the secondary seal 170) differs from the contact diameter between the sealing ring 120 and the valve body 102 (i.e., at the tertiary contact point 214), a cross-sectional moment is generated when the sealing retainer 114 is compressed by the pipe flange force (e.g., fully seated). This elastic cross-sectional torsion of the sealing ring 120 is generated during installation and can assist or mitigate the initial primary seat load depending on design requirements and usage expectations.

[0117] refer to Figure 36 The compression structure 230 of the ring may optionally be in the form of a secondary spring. The secondary spring may be separable from the sealing ring body 140. The secondary spring may be one or more of a variety of springs or other elastomers well known in the art. In some embodiments, the secondary spring may be combined with one or more compression structures 230 of the sealing ring 120. Figure 36 In the embodiment shown, a compression structure 230 configured as a secondary spring is disposed between the base 142 and the valve body 102 in the sealing ring cavity 112, so as to load the sealing ring 120 against the sealing retainer 114.

[0118] Figures 37 to 40 Finite element analysis of an embodiment of the sealing ring 120 is shown. Figure 37 and Figure 38 Exemplary analyses performed under high and low pressure applied to valve disc 106 are shown respectively. Figure 37 As shown, under low pressure drop, the stress acting on the sealing ring body 140 is minimal. In contrast, Figure 38 This illustrates that under high pressure drop, stress concentrates along different areas of the sealing ring body 140, including at leg 144. The bending that occurs at leg 144 is elastic, and the geometry returns to its original shape once the pressure on valve disc 106 decreases. Figure 39 and Figure 40 They respectively showed the same as Figure 37 and Figure 38 Similar stress concentration situations.

[0119] Figures 41 to 52 An additional embodiment of the sealing ring 120 is shown. For example, Figures 41 to 52 The sealing ring 120 includes a sealing member 240, which is not integrally formed with the sealing ring body 140 (e.g., it is placed within the body of the base 142 of the sealing ring 120 as an insert). Generally, the geometry of the sealing ring 120 is similar to... Figures 6 to 11 The sealing ring 120 shown has a similar geometry and has the same or similar advantages as described above. Figures 41 to 52 The sealing ring 120 shown is Figures 6 to 11 One difference between the shown sealing rings 120 is that a seal 240 is incorporated at the secondary sealing portion 170. For example... Figures 41 to 52 As shown, the sealing member 240 can be disposed between the base 142 of the sealing ring 120 and the seal retainer 114 within the sealing ring cavity 112. Typically, the sealing member 240 can provide an auxiliary seal at the secondary sealing portion 170.

[0120] Figures 41 to 43 A sealing member 240 is shown, which may include a graphite gasket secondary seal; however, other gasket materials are also possible. Figure 41 In this configuration, sealing member 240 is a single sealing member. This single sealing member may include a graphite gasket with a full graphite cross-section. Sealing member 240 can be fixed and loaded via valve disc drift. Figure 42 In this embodiment, the sealing member 240 includes at least two sub-sealing members. The at least two sub-sealing members of the sealing member 240 may be separated by an intermediate material (such as a metal foil). This intermediate material can increase the maneuverability of the sealing member 240, especially when using graphite sub-sealing members. Figure 43 As shown, the sealing member 240 includes a sub-seal radial laminate. The sub-seal radial laminate may include, for example, a graphite radial laminate having radial metal rings.

[0121] Figures 44 to 47 A sealing member 240, which may include a polymer gasket secondary seal, is shown. Figure 44 In this context, the sealing member 240 is a single sealing member having a generally rectangular cross-section, which forms a flat surface that contacts the seal retainer 114. Figure 45 In this context, sealing member 240 is a single sealing member having a rounded contact portion that contacts the seal retainer 114. Compared to a non-rounded contact portion, the rounded contact portion can provide higher initial contact stress during valve disc drift. Figure 46 In this context, sealing member 240 is a single sealing member with beaded contact ridges. Similar to rounded or curved contacts, beaded contact ridges can provide higher initial contact stress compared to flat contacts. Figure 47 The sealing member 240 is shown as a single sealing member having multiple beaded contact ridges and thus multiple sealing position selections.

[0122] Figures 48 to 50 A sealing member 240, which may include a spring member, is shown. The spring member may include a sheath (e.g., a polymer sheath) that at least partially surrounds the inner spring. The inner spring can provide a low mechanical pressure load, and the sheath can provide an auxiliary seal at the secondary seal 170. Therefore, Figures 48 to 50 The sealing component 240 can provide a spring-loaded pressure-assisted seal. The geometry of the sleeve and inner spring can vary depending on various factors, including valve and seal parameters or requirements. Therefore, Figures 48 to 50 Several exemplary embodiments of a sealing member 240 configured as a spring member are shown.

[0123] Figure 51 and Figure 52 A sealing member 240 is shown, which may include an elastomeric O-ring. The elastomeric O-ring may have various cross-sectional geometries, including annular (see...). Figure 51 ) or square (see Figure 52As described above, the sealing member 240 can provide an auxiliary seal at the secondary seal portion 170 between the sealing ring 120 and the seal retainer 114 within the sealing ring cavity.

[0124] Figures 53 to 58 An additional embodiment of the sealing ring 120 is shown. For example, Figures 53 to 58 The sealing ring 120 may include a U-shaped or D-shaped cross-section. Similar to the sealing ring 120 described above, Figures 53 to 58 The sealing ring 120 may include a sealing ring body 140 having: a base 142 that contacts the walls 150, 152 of the sealing ring cavity 112; legs 144 that extend laterally from the base 142; and feet 146 that extend from the legs 144 and are configured to engage the valve disc 106 of the valve 100. Also similar to the sealing ring 120 described above, it may allow... Figures 53 to 58 The sealing ring 120 moves laterally to accommodate valve disc tracking.

[0125] Figures 53 to 58 The sealing ring 120 can be initially mechanically compressed in the axial direction within the sealing ring cavity 112. This retained interference can provide an initial load at the secondary seal 170. However, this initial compressive load on the sealing ring 120 still allows lateral movement of the sealing ring 120 because the sealing ring 120 is not permanently fixed or designed to remain laterally stationary within the sealing ring cavity 112 as some conventional sealing rings do.

[0126] generally, Figures 53 to 58 The sealing ring 120 is similar to the sealing ring 120 described above in that it provides elastic behavior (e.g., as a response to valve disc drift) and undergoes cross-sectional torsion under load. It is worth noting that... Figure 53 and Figure 54 The sealing ring 120 includes an upper base 142 that rotates laterally outward under valve disc pressure, while Figure 55 and Figure 56 The sealing ring 120 includes an upper base 142 that rotates inward toward the valve disc side, and... Figure 53 and Figure 54 In comparison, its range of flexibility has increased.

[0127] Figures 53 to 58 The sealing ring 120 may also include one or more pressure balancing channels 232, with reference to Figure 24 and Figure 25 Similar to the pressure balancing channel 232 described above. The pressure balancing channel 232 can allow upstream pressure to migrate through a compression structure (e.g., sealing ring 120) to prevent pressure from becoming trapped behind the pressure ring (e.g., at the outward volume 184).

[0128] Figure 57 and Figure 58 It shows Figure 53 and Figure 54 Finite element analysis of sealing ring 120. Figure 57 This shows stress concentration within the sealing ring 120 under relatively low pressure. Figure 58 The stress concentration within the sealing ring 120 under relatively high pressure is shown. Overall, any bending that occurs in the foot 146, leg 144, or base 142 is elastic, and the geometry will return to its original shape once the pressure on the valve disc 106 is reduced.

[0129] As described above, the accompanying drawings in this disclosure are merely illustrative, and the features described herein or elsewhere can be used to create favorable bending and torsion within the valve, similar to those of the sealing ring. Therefore, embodiments of the technology disclosed herein can provide improvements to sealing control valves over conventional systems and methods. The foregoing description of the disclosed embodiments is intended to enable those skilled in the art to make or use the technology disclosed herein. Various modifications to these embodiments will readily be understood by those skilled in the art, and the general principles defined herein can be applied to other embodiments without departing from the spirit or scope of the technology disclosed herein. Therefore, the technology disclosed herein is not intended to be limited to the embodiments shown herein, but should be given the widest scope consistent with the principles and novel features disclosed herein.

[0130] Unless otherwise specified or limited, the terms “about” and “approximately” used herein with respect to reference values ​​mean a deviation of ±15% or less relative to the reference value, including the endpoints of the range. Similarly, the term “substantially” used herein with respect to reference values ​​means a deviation of ±5% or less relative to the reference value, including the endpoints of the range.

[0131] Similarly, in this document, the terminology used for clamping systems, unless otherwise specified or restricted, is as follows: “axial” refers to the main flow direction through the valve seat, and “radial” refers to the direction perpendicular to the main flow direction.

[0132] As used herein, unless otherwise limited or defined, “or” signifies a non-exclusive list of components or operations that may appear in any combination, rather than an exclusive list of components that can only appear as alternatives to each other. For example, a list of “A, B, or C” represents the following options: A; B; C; A and B; A and C; B and C; and A, B, and C. Correspondingly, the term “or” as used herein is intended to indicate an exclusive choice only when preceded by an exclusive term (e.g., “any,” “one of,” “only one,” or “exactly one of”). For example, a list of “one of A, B, or C” represents the following options: A, but excluding B and C; B, but excluding A and C; and C, but excluding A and B. A list beginning with “one or more” (and its variations) and separated by “or” represents an option of one or more of any or all of the listed components. For example, the phrases “one or more of A, B, or C” and “at least one of A, B, or C” represent the following options: one or more A’s; one or more B’s; one or more C’s; one or more A’s and one or more B’s; one or more B’s and one or more C’s; one or more A’s and one or more C’s; and one or more A’s, one or more B’s, and one or more C’s. Similarly, a list beginning with “multiple” (and its variations) and containing “or” separating the listed elements represents an option where there may be multiple instances of any or all of the listed elements. For example, the phrases “multiple A’s, B’s, or C” and “two or more A’s, B’s, or C’s” represent the following options: A and B’s; B and C’s; A and C’s; and A, B’s, and C’s.

[0133] As also described herein, unless otherwise limited or defined, "integral" and its derivatives (e.g., "monolithically") describe an element manufactured as a single piece, without the need for fasteners, adhesives, or the like to hold the individual parts together. For example, an element that is stamped, cast, or otherwise molded from a single sheet of metal or other continuous single-piece material into a single part without the use of rivets, screws, other fasteners, or adhesives to hold the individually formed parts together is an integral (monolithically molded) element. Conversely, an element formed from multiple parts that were initially formed separately and then fastened together is not an integral (or monolithically molded) element.

[0134] In some embodiments, the apparatus or system disclosed herein may be utilized, manufactured, installed, etc., using methods embodying aspects of the disclosed technology. Correspondingly, any description herein of a particular feature, capability, or intended use of an apparatus or system is generally intended to include disclosures of: methods for using such apparatus for its intended use, methods for otherwise realizing such capabilities, methods for manufacturing related components of such apparatus or system (or the entire apparatus or system), and methods for installing disclosed (or otherwise known) components to support such purposes or capabilities. Similarly, unless otherwise stated or limited, any discussion herein of any method of manufacture or use of a particular apparatus or system (including installation of the apparatus or system) is intended to inherently include disclosures of features utilized and capabilities realized by such apparatus or systems as examples of the disclosed technology.

[0135] As also described herein, unless otherwise defined or limited, directional terms are used to facilitate discussion with reference to a particular drawing or example, or to indicate spatial relationships relative to a particular other component or context, and are not intended to indicate absolute directions. For example, references to downward, forward, or other directions, or upward, backward, or other positions (or features) may be used to discuss aspects of a particular example or drawing, but do not necessarily require similar orientations or geometries in all installations or configurations.

[0136] As also stated herein, unless otherwise limited or defined, “configured as” means that a component, system, or module is specifically suited for the relevant function. Therefore, for example, ZZ configured as YY is specifically suited for YY, not merely something that can generally be done.

[0137] Although the technology of this disclosure has been described with reference to preferred examples, those skilled in the art will recognize that modifications in form and detail may be made to the disclosed examples without departing from the spirit and scope of the concepts described herein.

Claims

1. A valve assembly, the valve assembly comprising: Valve body; A valve passage that extends axially through the valve body; A valve disc, arranged to selectively suppress flow through the valve passage of the valve body, the valve disc being movable between a valve open position and a valve closed position; A sealing cavity, which is at least partially formed in the valve body; as well as A sealing ring, the sealing ring comprising: The base extends within the sealing cavity along the axial direction to provide an upstream contact structure and a downstream contact structure relative to the flow through the valve passage along the axial direction; A leg that extends transversely from the base in the axial direction from a position axially located between the upstream contact structure and the downstream contact structure; and The foot, which at least partially extends laterally from the distal end of the leg along the axial direction, When the valve disc is in the valve closed position and is subjected to a first pressure load from the upstream direction, a primary seal is formed between the foot of the sealing ring and the valve disc, and a secondary seal is formed between the downstream contact structure of the base of the sealing ring and the downstream wall of the sealing cavity.

2. The valve assembly according to claim 1, characterized in that, The boundary of the sealed cavity is formed by the valve body and the seal retainer, and The secondary sealing portion is formed between the downstream contact structure of the seal retainer and the base of the sealing ring.

3. The valve assembly according to claim 1, characterized in that, When the valve disc is in the valve closed position and is subjected to a load from the upstream direction greater than the first pressure, the valve disc drifts in response to the following: The legs are configured to deflect relative to the base, including rotating about a first point of rotation, and The base is configured to be subjected to a torsional load via the legs to rotate about a second rotation point spaced apart from the first rotation point.

4. The valve assembly according to claim 3, characterized in that, Under the first pressure, a gap is formed in the axial direction between the upstream contact structure at the base of the sealing ring and the upstream wall of the sealing cavity.

5. The valve assembly according to claim 4, characterized in that, Under the second pressure, the rotation of the base causes the upstream contact structure to contact the upstream wall of the sealing cavity to form a third-level seal. and The secondary sealing portion is radially offset from the third sealing portion.

6. The valve assembly according to claim 1, characterized in that, The sealing ring further includes a compression structure that is biased into contact with the upstream wall of the sealing cavity to push the downstream contact structure toward the downstream wall.

7. The valve assembly according to claim 6, characterized in that, The compression structure is a spring disposed between the upstream side of the base of the sealing ring and the upstream wall of the sealing cavity.

8. The valve assembly according to claim 6, characterized in that, The compression structure is formed by a notch in the base and includes the upstream contact structure.

9. The valve assembly according to claim 6, characterized in that, The sealing ring also includes a pressure balancing channel, such that a sub-volume of the sealing cavity formed on the radially outer side of the sealing ring is in fluid communication with the upstream side of the sealing ring.

10. The valve assembly according to claim 1, characterized in that, The base of the sealing ring includes a base body and a sealing member received in the base body, the sealing member providing a downstream contact surface to form the secondary seal with the downstream wall of the sealing cavity.

11. A sealing system for a butterfly valve, the butterfly valve comprising a valve disc and a sealing ring cavity, the sealing system comprising: A sealing ring having a sealing ring body, the sealing ring body comprising: A base that extends axially between an upstream end and a downstream end and is configured to be received within the sealing ring cavity; A leg, extending radially inward from the base to extend from within the sealing ring cavity toward the valve disc of the butterfly valve, the leg being cantilevered relative to the base in a cross-section extending along the axial and radial directions of the sealing ring; and A foot, extending downstream from the leg and opposite the base, engages with the valve disc of the butterfly valve when the valve disc is in the closed position to provide a primary seal. The downstream end of the base is configured to provide a secondary seal at the downstream wall of the sealing ring cavity; and The leg is flexibly supported relative to the base to allow the base to rotate when subjected to an axial load on the upstream side of the leg, thereby providing a third-level seal between the upstream end of the base and the upstream wall of the sealing ring cavity.

12. The sealing system according to claim 11, characterized in that, The sealing ring body is a single, integrally molded metal body.

13. The sealing system according to claim 11, characterized in that, The downstream end of the base includes a downstream contact structure configured to provide the secondary seal. and The upstream end of the base includes an upstream contact structure configured to provide the third-stage seal in response to a torsional load generated on the base by the axial load of the leg.

14. The sealing system according to claim 13, characterized in that, The upstream contact structure is oriented such that the third-level seal is provided at a position radially offset from the secondary seal.

15. The sealing system according to claim 11, characterized in that, The sealing ring body includes a channel that fluidly connects the upstream side of the sealing ring body to the outer radial side of the sealing ring body.

16. The sealing system according to claim 11, characterized in that, The base includes a sealing recess that receives a secondary sealing insert to provide the secondary seal.

17. A method for sealing a butterfly valve, the method comprising: Rotate the valve disc of the butterfly valve toward the closed position so that the valve disc engages with the foot of the sealing ring, the sealing ring having: a base that extends axially within the sealing cavity of the butterfly valve; And the legs, which extend from the base; The foot extends from the leg relative to the base in a downstream direction relative to the flow through the valve disc; A first upstream pressure is applied to the valve disc relative to the flow direction through the butterfly valve, such that: The foot deflects in the downstream direction to form a primary seal between the foot and the valve disc; and The base is loaded by the deflection of the leg to engage with the downstream wall of the sealing cavity, thereby forming a secondary seal between the base and the sealing cavity.

18. The method according to claim 17, characterized in that, The sealing ring is movable in a radial direction to accommodate misalignment of the valve disc, the radial direction being perpendicular to the flow direction through the butterfly valve.

19. The method of claim 17, further comprising: A second upstream pressure greater than the first upstream pressure is applied to the valve disc to cause the valve disc to drift in the downstream direction; The characteristic feature is that the valve disc drift causes the base to rotate to engage with the upstream wall of the sealing cavity, thereby forming a third-level seal between the base and the sealing cavity.

20. The method according to claim 19, characterized in that, During the application of the first upstream pressure, a gap is formed between the base of the sealing ring and the second wall of the sealing cavity at the upstream side of the sealing ring; and The base rotates to close the gap to form the third-level sealing portion.

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