pressure relief valve

Abstract

A valve for conveying a fluid is provided having a closed position and an open position and including a body (20), a valve seat (70) disposed in the body, a holder (50) disposed in the body, and a valve seat disk (60). The valve seat includes one or more inner surfaces (73) and an outer surface (71), and the one or more inner surfaces define an inner void (75). The valve seat disk is connected to the holder and is movable with the holder between a first position in which the valve seat disk sealingly engages the outer surface of the valve seat and a second position in which the valve seat disk is disengaged from the outer surface of the valve seat. The valve is in the closed position when the valve seat disk is in the first position and is in the open position when the valve seat disk is in the second position.

Description

TECHNICAL FIELD

[0001] The present disclosure relates generally to a pressure relief valve for discharging fluid from a pressurized vessel, such as a tank or a conduit, to ambient atmosphere. BACKGROUND

[0002] Pressure relief valves discharge or vent fluid, such as vapor / gaseous fluid, from a pressurized vessel to ambient atmosphere. Discharge is needed when the pressure of the fluid in the vessel exceeds a threshold. Discharge reduces the pressure of the fluid in the vessel below the threshold. For example, a tank can hold fluid such as compressed natural gas, liquefied natural gas, liquefied nitrogen, etc. The tank can be configured to withstand a maximum pressure. At some point, the fluid can warm up, thus increasing the pressure in the tank above the maximum pressure.

[0003] A pressure relief valve can be connected to and in fluid communication with the tank. The pressure relief valve discharges compressed gas from the tank to ambient atmosphere until the pressure of the compressed natural gas falls below the maximum pressure. Exemplary pressure relief valves are disclosed in U.S. Patent No. 9,939,072 to Wyatt and WO 2016 / 044398 to Wyatt, the entireties of which are hereby incorporated by reference. SUMMARY

[0004] Existing pressure relief valves often experience various challenges. For example, existing pressure relief valves can experience buildup of particulates, such as dust and dirt, on their valve seats, which can be caused by contaminated media and / or improper valve cleaning. This buildup of particulates compromises the quality of the seal between the valve seat and the valve component that is pressed against the valve seat. If the quality of the seal is severely compromised, fluid can leak through the pressure relief valve, thus creating air pollution and wasting fluid.

[0005] Existing pressure relief valves can experience collisions between their valve components and their outer valve bodies. These collisions create annoying rattling noises and can corrode the valve components and the outer valve bodies.

[0006] Existing pressure relief valves can also experience compromised or reduced quality of the seal at lower (e.g., cryogenic) temperatures. The outer surface of the valve component is pressed against the inner surface of the valve body to create the seal. At cryogenic temperatures, the valve component can experience greater shrinkage than the valve body, thus degrading the quality of the valve seal.

[0007] The present application discloses many embodiments of valves and many embodiments of components of valves. At least some of these embodiments address or at least partially address one or more of the above challenges.

[0008] One embodiment of a valve for delivering a fluid of the present disclosure has a closed position and an open position and includes a body, a valve seat disposed in the body, a retainer disposed in the body, and a valve seat disk. The valve seat includes one or more inner surfaces and an outer surface, and the one or more inner surfaces define an inner void. The valve seat disk is connected to the retainer and is movable with the retainer between a first position in which the valve seat disk sealingly engages the outer surface of the valve seat and a second position in which the valve seat disk disengages from the outer surface of the valve seat. The valve is in the closed position when the valve seat disk is in the first position and is in the open position when the valve seat disk is in the second position.

[0009] This application is defined by the appended claims. This description outlines aspects of example embodiments and is not to be used to limit the claims. Other implementations can be contemplated by those skilled in the art given the teachings of this technology as described herein, and such implementations are intended to fall within the scope of this application as given by the claims, as will be evident upon inspection of the following drawings and detailed description. BRIEF DESCRIPTION OF DRAWINGS

[0010] Figure 1A is a cross-sectional side view of one embodiment of a pressure relief valve of the present disclosure taken along line 1-1 of Figure 2 showing the pressure relief valve in a closed configuration.

[0011] Figure 1B is a cross-sectional side view of the pressure relief valve of Figure 1A showing the pressure relief valve in an open configuration.

[0012] Figure 2 is a cross-sectional top view of the pressure relief valve of Figure 1A taken along line 2-2 of Figure 1A .

[0013] Figure 3 is a cross-sectional side view of the body of the pressure relief valve of Figure 1A .

[0014] Figure 4 is a cross-sectional side view of the piston of the pressure relief valve of Figure 5 taken along line 4-4 of Figure 1A .

[0015] Figure 5 is an isometric view of the piston of Figure 4 .

[0016] Figure 6 is a partial cross-sectional side view of the piston of Figure 4 .

[0017] Figure 7 isFigure 4 A partial cross-sectional side view of the piston, in which the receiving... Figure 1A The seat of the pressure relief valve.

[0018] Figure 8 It is along Figure 9 The line cut from 8-8 Figure 1A A cross-sectional side view of the valve seat of the pressure relief valve.

[0019] Figure 9 yes Figure 8 Isometric view of the valve seat.

[0020] Figure 10 yes Figure 1A A partial cross-sectional side view of the pressure relief valve, showing along... Figure 2 The valve seat, part of the main body, and part of the seat plate are cut from line 1-1.

[0021] Figure 11 yes Figure 1A A cross-sectional side view of the seat of the pressure relief valve.

[0022] Figure 12A It is along Figure 13 The image shows a cross-sectional side view of another embodiment of the pressure relief valve of this disclosure, taken from lines 12A-12A, which shows the pressure relief valve in the closed configuration.

[0023] Figure 12B yes Figure 12A A cross-sectional side view of the pressure relief valve, showing the pressure relief valve in the open configuration.

[0024] Figure 13 It is along Figure 12A The line 13-13 was cut off Figure 12A A top view of the cross-section of the pressure relief valve.

[0025] Figure 14 yes Figure 12A An isometric view of the piston of the pressure relief valve.

[0026] Figure 15 It is along Figure 14 The line cut at 15-15 Figure 14 A side view of the cross-section of the piston.

[0027] Figure 16 yes Figure 12A Isometric view of the seat of the pressure relief valve.

[0028] Figure 17 It is along Figure 16 The line 17-17 was cut off Figure 16 A cross-sectional side view of the base plate.

[0029] Figure 18 yesFigure 12A isometric view of a retaining screw of the pressure relief valve of

[0030] Figure 19 is a cross-sectional side view of the retaining screw of the pressure relief valve of Figure 18 taken along line 19-19 of Figure 18 is a cross-sectional side view of the retaining screw of the pressure relief valve of

[0031] Figure 20 is a partial cross-sectional side view of the pressure relief valve of Figure 12A taken along line 12A-12A of Figure 13

[0032] Figure 21A is a cross-sectional side view of another embodiment of the pressure relief valve of the present disclosure, showing the pressure relief valve in a closed configuration.

[0033] Figure 21B is a cross-sectional side view of the pressure relief valve of Figure 21A taken along line 19-19 of DETAILED DESCRIPTION

[0034] The following description describes, illustrates, and exemplifies one or more embodiments of the present application according to the principles of the present application. The description is not meant to limit the present application to the embodiments described, but is intended to explain and teach the principles of the present application so that others can apply the principles to their own embodiments and / or practice the application.

[0035] The scope of the application is intended to cover all such embodiments as can come within the scope of the following claims, either literally or under the doctrine of equivalents. The specification describes illustrative embodiments of the present application, but does not limit the scope of the claims or the scope or spirit of the application. Features described in the specification that are not embodied in the claims or the specification are not intended to be limitations on the claims.

[0036] It should be noted that in the description and drawings, like or substantially similar elements can be labeled with the same reference numerals. However, these elements can sometimes be labeled with different numbers, for example, where such labeling facilitates a clearer description. In addition, the drawings set forth herein are not necessarily drawn to scale, and in some instances, the dimensions of certain features can have been exaggerated for the sake of more clearly depicting such features. Such labeling and drawing practices do not necessarily imply a substantial underlying purpose.

[0037] ​Relative terms such as top, bottom, vertical, right, left, etc. can be used to describe some features. These relative terms are used only to facilitate the description of the disclosed embodiments. These relative terms do not limit the disclosed embodiments. More specifically, it is contemplated that the valves depicted in the drawings will be oriented in different directions in practice and the relative orientation of the features will change accordingly.

[0038] As stated above, this specification is intended to be read as a whole and interpreted in accordance with the principles of the application as taught herein and understood by those skilled in the art.

[0039] Figures 1A to 11 An embodiment of a pressure relief valve of the present application is illustrated as a pressure relief valve 10. The pressure relief valve 10 includes a body 20, a set screw 30, a spring 40, a piston 50, a washer 59, a seat disk 60, and a valve seat 70.

[0040] As Figure 1A and 3 Best shown in FIGS. 1-3, the body 20 houses the set screw 30, the spring 40, the piston 50, the washer 59, the seat disk 60, and the valve seat 70. The body 20 has a longitudinal axis L B and includes a plurality of inner surfaces 21 that define a plurality of voids 22. The body 20 also includes a plurality of outer surfaces 23.

[0041] A first inner surface 21a of the body 20 is parallel to the longitudinal axis L B and defines a cylindrical inlet (or first) void 22a. A second inner surface 21b of the body 20 is inclined relative to the longitudinal axis L B and defines a frustoconical second void 22b. A third inner surface 21c of the body 20 is parallel to the longitudinal axis L B and defines a cylindrical third void 22c. A fourth inner surface 21d of the body 20 perpendicularly joins the third inner surface 21c with a fifth inner surface 21e of the body 20. The fifth inner surface 21e is parallel to the longitudinal axis L B . A sixth inner surface 21f of the body 20 is threaded but otherwise similar to the fifth inner surface 21e. The fourth, fifth, and sixth inner surfaces 21d, 21e, and 21f collectively define a cylindrical outlet (or fourth) void 22d.

[0042] A first outer surface 23a of the body 20 is threaded but otherwise parallel to the longitudinal axis L B . A second outer surface 23b of the body 20 perpendicularly joins the first outer surface 23a with a third outer surface 23c of the body 20. In the illustrated example, a radius defined between the first outer surface 23a and the second outer surface 23b provides a smooth transition between the first and second outer surfaces 23a and 23b. The third outer surface 23c is parallel to the longitudinal axis L B . A fourth outer surface 23d of the body 20 is inclined relative to the longitudinal axis LB angled (e.g., 45 degrees). The fifth outer surface 23e of the body 20 is parallel to the longitudinal axis L B . The sixth outer surface 23f of the body 20 is angled (e.g., 45 degrees) relative to the longitudinal axis L B angled (e.g., 45 degrees). The seventh outer surface 23g of the body 20 is parallel to the longitudinal axis L B .

[0043] The first outer surface 23a is configured to threadably engage corresponding threads of a container (not shown) to removably attach the body 20 (and thus the valve 10) to the container. The sixth inner surface 21f is configured to threadably engage corresponding threads of a set screw 30. During manufacturing, the set screw 30 is precisely adjusted to set or otherwise define a desired threshold pressure setting for opening and / or closing the valve 10. Once the threshold pressure is set, the set screw 30 is pinned or otherwise secured in place so as to prevent unauthorized adjustment of the threshold pressure setting of the valve 10.

[0044] As best shown in Figure 4 and 5 , the piston 50 (sometimes referred to as a “retainer”) includes a receiver 51a and a guide 51b. The receiver 51a includes a generally box-shaped exterior formed by four body guide surfaces 58a and four connecting surfaces 58b. Each connecting surface 58b extends between two different body guide surfaces 58a. The receiver 51a is configured to receive the seat disc 60, receive the pressurized fluid when the valve 10 is in the open configuration, and receive the spring 40. The guide 51b is generally annular. The piston 50 is preferably symmetric about a plane extending through opposing body guide surfaces 58a.

[0045] As shown in FIG. 1, the washer 59 is positioned above the receiver 51a (relative to the orientation shown in FIG. 1) and directly contacts the lower end of the spring 40. When the washer 59 is not present, the receiver 51a can directly contact the lower end of the spring 40. When the washer 59 is present, the receiver 51a can indirectly contact the lower end of the spring 40 via the washer 59.

[0046] In this embodiment, as best shown in Figure 5 , the body guide surfaces 58a have a radius of curvature equal to the radius of curvature of the cylindrical outer surface of the guide 51b. The body guide surfaces 58a are flush with the cylindrical outer surface of the guide 51b and are configured to guide the piston 50 in moving within the body 20. The guide 51b radially protrudes relative to the connecting surfaces 58b that extend between adjacent body guide surfaces 58a.

[0047] Piston 50 is sized and shaped to be received in void 22d formed in body 20. When piston 50 is received in body 20, body guide surface 58a of receiver 51a positions piston 50 within body 20 to define a small clearance between piston 50 and inner wall 21e of body 20. This clearance between piston 50 and inner wall 21e forms multiple partial cylindrical gaps 11a, 11b, 11c, and 11d between body guide surface 58a and fifth surface 21e of body 20. As shown in FIGS. 1 and 2, for example, gap 11a is formed between body guide surface 58a and first surface 21a of body 20. Gap 11b is formed between body guide surface 58a and second surface 21b of body 20. Gap 11c is formed between body guide surface 58a and third surface 21c of body 20. Gap 11d is formed between body guide surface 58a and fourth surface 21d of body 20. Figure 1A and 1B As shown in FIGS. 1 and 2, for example, cylindrical outer surface of guide 51b defines a small clearance between guide 51b and inner wall 21e of body 20.

[0048] The presence of gaps 11a through 11d between body 20 and piston 50 advantageously prevents foreign particles (e.g., dust) from accumulating on inner surface 21e of body 20 and thus hindering the longitudinal movement of piston 50. More specifically, the presence of gaps 11a through 11d causes particles that enter valve 10 via valve outlet 22d to fall downward through gaps 11a through 11d and past inner surface 21e until reaching fourth inner surface 21d of body 20. Additionally, gaps 11a through 11d advantageously allow debris from a pressurized container (e.g., a tank) to flow through valve 10 rather than accumulating within body 20.

[0049] Additionally, guide 51b and body guide surface 58a are configured to align piston 50 relative to body 20 by circumferentially guiding piston 50 adjacent to fifth inner surface 21e of body 20. By aligning piston 50 relative to body 20, guide 51b and body guide surface 58a align spring 40 relative to body 20 and seat disk 60 relative to valve seat 70. Moreover, this alignment and guidance between inner surface 21e of body 20, body guide surface 58a, and cylindrical outer surface of guide 51b prevents piston 50 from rattling and clanking inside body 20. According to some embodiments, piston 50 is configured to be circumferentially positioned relative to body 20 (via guide 51b and / or body guide surface 58a) along the entire longitudinal length of piston 50 to prevent any other portion of piston 50 from radially colliding with body 20.

[0050] In another embodiment, the body guide surface is not flush with the cylindrical outer surface of the guide. According to this embodiment, the maximum effective diameter of the receiver (i.e., between the opposing body guide surfaces or between the opposing connecting surfaces) is less than the maximum diameter of the guide, such that the guide protrudes radially outward relative to both the connecting surfaces and the body guide surfaces. In this embodiment, when the piston is received in the body, the cylindrical outer surface of the guide contacts the body, but the body guide surface does not contact the body.

[0051] Returning to the illustrated embodiment, asFigure 4 and 5 As best shown in Figure 4 and 5 As shown in Figure 6 and 7 As best shown in

[0052] Figure 6 is a schematic side plan view of one partial slice of the receiver 51a cut along a plane perpendicular to one of the connecting surfaces 58b. In Figure 6 The seat 60 is removed for clarity in Figure 6 As shown in Figure 7 The seat 60 is added to Figure 6 In Figure 7 It can be seen that the tips 55b are deformed and thus grip the outer surface of the seat 60. The seat 60 at least partially occupies or fully occupies the void defined by the undercuts 55c.

[0053] As best shown in Figure 4 and 5 The receiver 51a defines four cylindrical first openings 52, four rectangular second openings 53 and a cylindrical central opening 54. The column 51c, which includes portions of the body guide surface 58a and portions of the connecting surface 58b, extends between the second openings 53. Each inner surface has a radius of curvature equal to the radius of curvature of the central opening 54, such that the inner reference circumference of the receiver 51a is flush with the inner surface 51cc of the column 51c.

[0054] The central opening 54 is in fluid communication with both the first opening 52 and the second opening 53. When the valve 10 is in the open configuration, fluid is passed between the piston 50 and the body 20 and into the piston 50 via the first opening 52 and / or the second opening 53 (as described below). The second opening 53 has a larger surface area than the first opening 52 and therefore accommodates a larger volume of fluid flow in the absence of the spring 40. However, as shown in FIG1, the spring 40 at least partially obstructs the second opening 53. As the spring 40 is compressed (i.e., as the piston 50 moves upward relative to the body 20), the spring 40 obstructs the second opening 53 to a greater extent, thus reducing the fluid flow through the second opening 53. When the spring 40 is fully compressed, the first opening 52 can accommodate a larger volume of fluid flow than the second opening 53.

[0055] like Figure 8 and 9 As best shown in the diagram, valve seat 70 is partially spherical and about its longitudinal axis L VS Symmetrical, the vertical axis L VS It can be connected to the longitudinal axis L of the main body 20 B Collinear. Valve seat 70 includes an outer surface 71 (also referred to as a valve seat surface, or at least one valve seat surface), a first flange 72, a second opposing flange 74, and an inner surface 73. The inner surface 73 defines a cylindrical valve seat clearance 75. According to some embodiments, the outer surface 71 is bent such that the valve seat 70 is shaped like a partially sphere (e.g., a sphere in which two opposing ends are removed, such as...). Figure 8 (As shown in the image).

[0056] In some embodiments, the first and second flanges 72 and 74 have the same radius of curvature. The first and second flanges 72 and 74 may be identical, such that the valve seat 70 is positioned about the midpoint extending through the outer surface 71 and perpendicular to the longitudinal axis L. VS The plane is symmetric. For example... Figure 9 As best illustrated, the first flange 72 defines a first circumferential edge 72a having an outer surface 71 and a second circumferential edge 72b having an inner surface 73. Reference segment 72c is flush with the first flange 72, and the connection between the first circumferential edge 72a and the second circumferential edge 72b can be flat (e.g., linear) or curved. Figure 8 In the middle, reference segment 72c is an arc with a radius of curvature.

[0057] The outer surface 71 and / or the inner surface 73 is smooth or has an excellent surface finish (e.g., polished). The outer surface 71 and / or the inner surface 73 has a smoother or more excellent surface finish than the inner surface 21 (including the inner surfaces 21b and 21c) of the body 20. The difference in surface finish enables the rough inner surface of the body 20 to grip the smooth outer surface 71 of the valve seat 70. Furthermore, the smooth outer surface 71 of the valve seat 70 prevents particles (e.g., dirt) from accumulating on the outer surface 71 and compromising the seal quality between the seat disc 60 and the valve seat 70. Because the valve seat 70 can be machined separately from the body 20, a user can polish the outer surface 71 to include a desired surface finish before inserting the valve seat 70 into the body 20. Thus, this desired surface finish of the outer surface 71 can be configured to provide a desired amount of sealing between the valve seat 70 and the seat disc 60.

[0058] As best shown in FIGS. 1 and 10, the valve seat 70 is sized and shaped for an interference fit with the body 20. In the illustrated embodiment, the valve seat 70 contacts the body 20 along a first circumference 76a and a second circumference 76b. Thus, the valve seat 70 is dimensioned such that the diameter of the first circumference 76a is greater than the diameter of the void 22c of the body 20, and the diameter of the second circumference 76b is greater than the corresponding diameter of the portion of the void 22b of the body 20.

[0059] In the illustrated embodiment, the body 20 is preferably made of a first material (e.g., brass), and the valve seat 70 is preferably made of a different second material (e.g., stainless steel). The first material preferably has a greater coefficient of thermal expansion than the second material, such that when the valve 10 is subjected to cryogenic temperatures (e.g., 123 K or -150 C), the body 20 shrinks a greater extent than the valve seat 70. This differential shrinkage improves the interference fit between the body 20 and the valve seat 70, such that the compressive force exerted by the body 20 on the valve seat 70 at cryogenic temperatures is increased compared to at room temperature (e.g., 294 K or 21 C). Thus, the seal between the body 20 and the valve seat 70 along the first and second circumferences 76a and 76b is improved when the valve 10 is subjected to cryogenic temperatures. As with all features disclosed herein, brass and stainless steel are optional materials for the body 20 and the valve seat 70, and other materials can be used.

[0060] Turning to Figure 11 , the seat disc 60 includes an outer surface 61 and an inner surface 62, and bounds a void 63. The seat disc 60 is bowl-shaped and symmetric about its longitudinal axis. The seat disc 60 is configured to close the valve 10 by compressing and sealing the valve seat 70.

[0061] The outer surface 61 includes a flat and circular first surface 61a, a linearly sloped and annular second surface 61b, a flat and cylindrical third surface 61c, a linearly sloped and annular fourth surface 61d, and a flat and annular fifth surface 61e.

[0062] The inner surface 62 includes a cylindrical first surface 62a, a flat and annular second surface 62b, a flat and cylindrical third surface 62c, and a flat and circular fourth surface 62d. The inner surface 62 includes a circumferentially and curved sealing surface 64 that joins the fifth outer surface 61e and the first inner surface 62a. The sealing surface 64 is configured to press against the valve seat 70. More specifically, at least a portion of the sealing surface 64 sealingly engages the valve seat 70 along the circumferential 76c when the valve 10 is closed, as shown in Figure 10

[0063] More specifically, the piston 50 and attached seat disc 60 are movable between a sealing position (e.g., a closed position) and a non-sealing position (e.g., an open position). When the piston 50 and attached seat disc 60 are in the sealing position, the sealing surface 64 of the seat disc 60 sealingly engages the valve seat 70 to prevent fluid from flowing through the valve 10 from the inlet void 22a to the outlet void 22d and the valve 10 is thus closed. On the other hand, when the piston 50 and attached seat disc 60 are in the non-sealing position, the sealing surface 64 of the seat disc 60 is displaced from the valve seat 70 and does not sealingly engage the valve seat 70, meaning that fluid can flow through the valve 10 from the inlet void 22a to the outlet void 22d. The spring 40 biases the piston 50 and seat disc 60 to the sealing position, and thus the valve 10 is biased in the closed and / or sealing position.

[0064] In certain embodiments, the piston and attached seat disc have multiple sealing and non-sealing positions. The non-sealing positions correspond to positions of the piston and seat disc when the seat disc is disengaged from the valve seat, and the sealing positions correspond to positions of the piston and seat disc when the seat disc sealingly engages the valve seat.

[0065] The longitudinal axes of some components (e.g., the longitudinal axes of the piston 50 and seat disc 60) can be slightly misaligned relative to the longitudinal axis L B of the body 20 in use (e.g., at a 1 degree angle or less than a 1.5 degree angle). As such, the circumferential 76c can not be perfectly perpendicular to the longitudinal axis L B . Because the sealing surface 64 bears inward on the valve seat 70, this misalignment does not necessarily impair the quality of the seal between the seat disc 60 and the valve seat 70. In other words, even when these longitudinal axes are misaligned, a 360 degree seal is maintained around the valve seat 70.

[0066] This is in contrast to prior art designs in which the seat disc bears outward on the inner surface of the valve seat. In these prior art designs, misalignment between the longitudinal axes of the seat disc and the valve seat introduces a leak between the seat disc and the valve seat. In other words, when the seat disc bears outward on the valve seat, misalignment of the seat disc relative to the valve seat will cause at least a portion of the seat disc to no longer contact the valve seat and a 360 degree seal will not be maintained.

[0067] ​The void 63 includes a cylindrical first void 63a having a diameter defined by the first inner surface 62a and a cylindrical second void 63b having a diameter defined by the third inner surface 62c. The diameter of the first void 63a exceeds the diameter of the second void 63b. The length (in the longitudinal direction) of the first void 63a exceeds the length (in the longitudinal direction) of the second void 63b.

[0068] The valve seat 70 can be made of a second material (e.g., stainless steel) and the seat disc 60 can be made of a different third material (e.g., a polymer such as rubber or plastic). Such third material is preferably compressible and has a greater coefficient of thermal expansion than the second material, such that the seat disc 60 shrinks a greater degree than the valve seat 70 when the valve 10 is subjected to a low temperature. This differential shrinkage improves the quality of the seal (i.e., the tightness or compression of the seal along the third circumference 76c and the sealing surface 64). Thus, when the valve 10 is subjected to a low temperature and closed, the seal between the seat disc 60 and the valve seat 70 is improved. In other words, the shrinkage of the seat disc 60 relative to the valve seat 70 improves the quality of the seal.

[0069] In operation, the valve 10 is attached to a pressurized container (e.g., a tank or conduit, not shown) storing a pressurized fluid via threads on the first outer surface 23a of the body 20 such that the inlet void 22a is in constant fluid communication with the pressurized container. The pressurized fluid can be stored in the container at a low temperature. The outlet void 22d is configured to be in constant fluid communication with the ambient atmosphere.

[0070] The inlet void 22a is in constant fluid communication with the valve seat void 75. The pressurized fluid in the valve seat void 75 opposes the biasing force exerted by the spring 40 on the piston 50 and seat disc 60. When the pressurized fluid in the container exceeds a threshold pressure, and in particular when the force of the pressurized fluid exerted on the seat disc 60 exceeds the biasing force of the spring 40, the seat disc 60 disengages the valve seat 70, i.e., moves from the sealed position to the unsealed position. This opens the valve 10 and enables fluid to flow from the valve seat void 75 through the gaps 11a to 11d between the body 20 and the piston 50, into the piston 50 via the first and second openings 52 and 53, and through the opening in the set screw 30 to the outlet void 22d and then to the ambient atmosphere.

[0071] After sufficient fluid discharge, the force of the pressurized fluid exerted on the seat disc 60 drops below the biasing force exerted by the spring 40. Accordingly, the spring 40 forces the piston 50 and attached seat disc 60 to move from the unsealed position to the sealed position, thereby closing the valve 10.

[0072] This section lists some of the advantages of the disclosed embodiments. Additional advantages of the disclosed embodiments should be readily apparent from a reading of the rest of the specification.

[0073] The bowl design of the seat disc 60 enables the seat disc 60 to absorb the impact of foreign particles when the valve 10 is opened. More specifically, the first, second, third, and fourth inner surfaces 62a, 62b, 62c, and 62d of the seat disc 60 are configured to absorb the impact of foreign particles (e.g., dust) when the valve 10 is opened. The momentum of the foreign particles causes the foreign particles to collide with the inner surfaces 62 of the seat disc 60 while fluid is being discharged through the sealing surface 64 and the outer surface 61 when the valve 10 is opened.

[0074] Additionally, the bowl design of the seat disc 60 and / or the outer diameter of the receiver 51a enables the seat disc 60 and / or the receiver 51a to deflect foreign particles from the valve seat 70 (e.g., the third circumference 76c of the valve seat 70) when the valve 10 is closed. More specifically, these particles can enter the valve 10 through the outlet void 22d and fall under the force of gravity toward the piston 50 and the seat disc 60 when the valve 10 is closed. These particles can eventually enter one or more of the gaps 11a-11d and fall under the force of gravity toward the surface 21d of the body 20. Because the piston 50 and the seat disc 60 both vertically and circumferentially surround or cover the valve seat 70, the foreign particles will not contact the valve seat 70 and, in particular, the third circumference 76c of the valve seat 70. With reference to Figure 2 It can be seen that the gaps 11a-11d defined between the body 20 and the piston 50 are offset from the valve seat 70 such that a longitudinally extending reference line through the gaps 11a-11d does not intersect the valve seat 70.

[0075] Furthermore, the surface 21d of the body 20 is flat and horizontal (and, according to some embodiments, outwardly sloped downward) with respect to the longitudinal axis L B when the longitudinal axis L V of the valve 10 (which can be collinear with the longitudinal axis L B ) is oriented parallel to the vertical direction, particles resting on the surface 21d do not experience the force of gravity pulling the particles toward the valve seat 70. In other words, the surface 21d of the body 20 is not sloped (with respect to the longitudinal direction) toward the valve seat 70, and the surface 21d of the body 20 is configured to counteract the force of gravity and thereby inhibit downward movement of particles encountering the surface 21d. The surface 21d of the body thus serves as a resting surface or trap for foreign particles. Even if a particle encountering the surface 21d moves radially inward toward the valve seat 70, the third circumference 76c of the valve seat 70 is positioned vertically above the surface 21d such that the particle will have to move longitudinally upward against the force of gravity to reach the third circumference 76c.

[0076] As stated above, according to some embodiments, the body 20, the valve seat 70, and the seat disk 60 are each symmetrical about their respective longitudinal axes. According to some embodiments, the total surface area of the gaps 11a-11d is greater than or equal to the total surface area of the valve seat void 75. According to some embodiments, the total surface area of the first opening 52 plus the second opening 53 is greater than or equal to the total surface area of the valve seat void 75. According to some embodiments, the surface area of the central void defined by the spring 40 is greater than or equal to the total surface area of the valve seat void 75. The surface areas are taken along a plane that is perpendicular to the intended fluid flow direction.

[0077] Figures 12A to 20 Another embodiment of a pressure relief valve of the present disclosure, identified as pressure relief valve 100, is illustrated. The pressure relief valve 100 includes a body 200, a set screw 300, a spring 400, a piston 500, a seat disk 600, and a valve seat 700.

[0078] As Figure 12A and 12B best shown in FIGS. 1-3, the body 200 houses the set screw 300, the spring 400, the piston 500, the seat disk 600, and the valve seat 700. The body 200 is identical to the body 20. The element numbers used to describe the body 200 below are identical to the corresponding numbers used to describe the body 20 above, but with an additional “0” appended to the end (e.g., 21e becomes 210e, 22a becomes 220a, etc.). Similarly, the valve seat 700 is identical to the valve seat 70. The element numbers used to describe the valve seat 700 below are identical to the corresponding numbers used to describe the valve seat 70 above, but with an additional “0” appended to the end (e.g., 72 becomes 720, 75 becomes 750, etc.).

[0079] As Figure 18 and 19 best shown in FIGS. 1-3, the set screw 300 includes a body that includes a tubular outer wall 310, a generally circular upper wall 320, and a tubular inner wall 330. The tubular outer wall 310 is externally threaded and is configured to threadably engage the threads of the sixth inner surface 210f of the body 200. The upper wall 320 includes a plurality of surfaces 320a, 320b, and 320c each defining a kidney-shaped opening through the upper wall 320. The inner wall 330 includes a cylindrical inner surface 330a that defines a bore and a cylindrical outer surface 330b. The outer surface 330b has a diameter that is just smaller than the inner diameter of the spring 400. As Figure 12A and 12B best shown in FIGS. 1-3, the inner wall 330 is received in the inner cavity of the spring 400 such that the spring 400 is partially disposed around the inner wall 330 and contacts (or is slightly spaced apart from) the outer surface 330b. This reduces or prevents radial movement of the spring 400 and holds it in place.

[0080] As Figure 14 and15 As best shown in FIG. 5, the piston 500 includes a body that includes a tubular outer wall 580, a tubular inner wall 510, and an annular connecting wall 520 extending between and connecting the inner and outer walls 510 and 580.

[0081] The outer wall 580 has a box-shaped exterior formed by four body guide surfaces 580a and four connecting surfaces 580b. Each connecting surface 580b extends between two different body guide surfaces 580a. The outer wall 580 has cylindrical inner surfaces 580c and 580d. The inner wall 510 includes a cylindrical outer surface 510a and cylindrical inner surfaces 510b and 510c. The connecting wall 520 includes an annular upper surface 520a that joins the inner surface 580c of the outer wall 580 with the outer surface 510a of the inner wall 510. The connecting wall 520 also includes an annular lower surface 520b that joins the inner surface 580d of the outer wall 580 with the inner surface 510c of the inner wall 510.

[0082] The inner surfaces 510b and 510c of the inner wall 510 generally define a seat disk receiving hole (not labeled) sized and shaped to receive and retain a portion of the seat disk 600 (as described below). Also, the lower surface 520b of the connecting wall 520 and the inner surface 580d of the outer wall 580 generally define a seat disk receiving void (not labeled) sized and shaped to receive and retain another portion of the seat disk 600, as described below.

[0083] The inner surface 580c of the outer wall 580, the upper surface 520a of the connecting wall 520, and the outer surface 510a of the inner wall 510 generally define a spring receiving void (not labeled) sized and shaped to receive the spring 400. Also, the diameter of the outer surface 510a of the inner wall 510 is just smaller than the inner diameter of the spring 400. As Figure 12A and 12B As best shown in FIG. 5, the inner wall 510 is received in the inner cavity of the spring 400 such that the spring 400 is partially disposed around the inner wall 510 and contacts (or is slightly spaced from) the outer surface 510a. This reduces or prevents radial movement of the spring 400 and holds it in place (along with the inner wall 330 of the seat disk 600).

[0084] The piston 500 is preferably symmetric about a plane extending through the opposite body guide surfaces 580a. The piston 500 is sized and shaped to be received in the void 220d formed in the body 200. As Figure 13The body guide surface 580a best demonstrates that, when the piston 500 is received in the body 200, the body guide surface 580a positions the piston 500 within the body 200 to define a small gap between the piston 500 and the inner wall 210e of the body 200. In this embodiment, the body guide surface 580a has a radius of curvature equal to the radius of curvature of the inner wall 210e of the body 200. This small gap between the body guide surface 580a and the inner wall 210e and the equal radius of curvature forms a plurality of partial cylindrical gaps 110a, 110b, 110c, and 110d between the body guide surface 580a and the fifth inner surface 210e of the body 200.

[0085] The presence of the gaps 110a through 110d between the body 200 and the piston 500 advantageously prevents foreign particles (e.g., dust) from accumulating on the inner surface 210e of the body 200 and thus hindering the longitudinal movement of the piston 500. In particular, the presence of the gaps 110a through 110d causes particles that enter the valve 100 via the valve outlet 220d to fall downward through the gaps 110a through 110d and past the inner surface 210e until reaching the fourth inner surface 210d of the body 200. Additionally, the gaps 110a through 110d advantageously allow debris from a pressurized container (e.g., a tank) to flow through the valve 100 rather than accumulating within the body 200.

[0086] Additionally, the body guide surface 580a is configured to align the piston 500 relative to the body 200 by proximally guiding the piston 500 along the circumference of the fifth inner surface 210e of the body 200. By aligning the piston 500 relative to the body 200, the body guide surface 580a aligns the spring 400 relative to the body 200 and the seat disk 600 relative to the valve seat 700. Moreover, this alignment and guidance between the inner surface 210e of the body 200 and the body guide surface 580a prevents the piston 500 from rattling and clanking within the body 200. According to some embodiments, the piston 500 is configured to be proximally positioned relative to the body 200 (via the body guide surface 580a) along the entire longitudinal length of the piston 500 to prevent any other portion of the piston 500 from radially colliding with the body 200.

[0087] Turning to Figure 16 and 17The seat 600 includes a body (not labeled) having a seat head (or first portion) 610 extending from a seat body (or second) portion 620. The seat head 610 includes an exterior formed by a circular first surface 610a, a tapered annular second surface 610b extending from the first surface 610a, and a cylindrical third surface 610c extending from the second surface 610b. The seat body 620 includes an exterior formed by an annular first surface 620a extending from the third surface 610c of the seat head 610, a tapered annular second surface 620b extending from the first surface 620a, a cylindrical third surface 620c extending from the second surface 620b, and an annular fourth surface 620d extending from the third surface 620c. The body defines a nipple-like void formed by a cylindrical surface 620f, an annular surface 620g extending from the surface 620f, a tapered annular surface 620h extending from the surface 620g, a cylindrical surface 610d extending from the surface 620h, and a tapered surface 610e extending from the surface 610d. The seat 600 is symmetric about its longitudinal axis.

[0088] As Figure 12A , 12B and best shown in FIGS. 20, the seat 600 is received and retained by the piston 500 via an interference fit. Specifically, the seat head 610 is received in and extends through a seat receiving bore defined generally by the inner surfaces 510b and 510c of the inner wall 510 of the piston 500, and the seat body 620 is received in a seat receiving void defined generally by the lower surface 520b of the connecting wall 520 of the piston 500 and the inner surface 580d of the outer wall 580. The diameter of the seat receiving bore is slightly smaller than the diameter of the seat head 610, and the diameter of the seat receiving void is slightly smaller than the diameter of the seat body 620. This enables the piston 500 to retain the seat 600 in those voids via an interference fit, such that the piston 500 and seat 600 move integrally.

[0089] The seat 600 also includes a sealing surface 640 extending circumferentially between the surfaces 620d and 620f. The sealing surface 640 is configured to press against the valve seat 700, as described below. More specifically, at least a portion of the sealing surface 640 sealingly engages the valve seat 700 along the circumference 760c when the valve 100 is closed, as shown in Figure 20 .

[0090] More specifically, the piston 500 and attached seat 600 can be in a sealed position (i.e., closed position) (FIG. 18) Figure 12A and an unsealed position (i.e., open position) (FIG. 19) Figure 12BThe piston 500 and its attached seat 600 move between the valve seat 700 and the valve 100. When the piston 500 and its attached seat 600 are in the sealed position, the sealing surface 640 of the seat 600 seals against the valve seat 700 to prevent fluid from flowing from the inlet gap 220a through the valve 100 to the outlet gap 220d, and the valve 100 is thus closed. On the other hand, when the piston 500 and its attached seat 600 are in the unsealed position, the sealing surface 640 of the seat 600 displaces from the valve seat 700 and unseales against the valve seat 700, meaning that fluid can flow from the inlet gap 220a through the valve 100 to the outlet gap 220d. The spring 400 biases the piston 500 and the seat 600 to the sealed position, and thus the valve 100 is biased into the closed and / or sealed position.

[0091] In operation, valve 100 is threaded onto a pressurized container (e.g., a tank or conduit, not shown) storing pressurized fluid via a first outer surface 230a of body 200, such that inlet opening 220a is in constant fluid communication with the pressurized container. The pressurized fluid can be stored in the container at a cryogenic temperature. Outlet opening 220d is configured to be in constant fluid communication with the ambient atmosphere.

[0092] The inlet clearance 220a is in constant fluid communication with the seat clearance 750. The pressurized fluid in the seat clearance 750 resists the biasing force exerted by the spring 400 on the piston 500 and the seat plate 600. When the pressurized fluid in the container exceeds a threshold pressure, and especially when the force exerted by the pressurized fluid on the seat plate 600 exceeds the biasing force of the spring 400, the seat plate 600 disengages from the seat 700 and moves from a sealed position to an unsealed position. This opens the valve 100 and allows fluid to flow from the seat clearance 750 through the gaps 110a to 110d between the body 200 and the piston 500, through the opening in the retaining screw 300, to the outlet clearance 220d, and then to the ambient atmosphere.

[0093] After sufficient fluid discharge, the force exerted by the pressurized fluid on the seat 600 decreases below the biasing force applied by the spring 400. Therefore, the spring 400 forces the piston 500 and the attached seat 600 to the sealing position, thereby closing the valve 100.

[0094] Figure 21A and 21B Another embodiment of the pressure relief valve of this disclosure, identified as pressure relief valve 1000, is described. Pressure relief valve 1000 includes a body 2000, a fixing screw 3000, a spring 4000, a piston 5000, a seat 6000, and a valve seat 7000.

[0095] like Figure 21A and 21BAs best shown below, body 2000 houses fixing screw 3000, spring 4000, piston 5000, seat 6000, and valve seat 7000. Body 2000 is preferably substantially the same as body 200, except for the differences that are further indicated and discussed in detail below. Therefore, most component numbers used below to describe body 2000 are the same as their corresponding numbers used above to describe body 200, but with an additional "0" appended to the end (e.g., 210e becomes 2100e, 220a becomes 2200a, etc.). Similarly, valve seat 7000 is preferably substantially the same as valve seat 700. Component numbers used below to describe valve seat 7000 are the same as their corresponding numbers used above to describe valve seat 700, but with an additional "0" appended to the end (e.g., 720 becomes 7200, 750 becomes 7500, etc.).

[0096] like Figure 21A and 21B As best illustrated, the plate 6000 is received and held by the piston 5000 via an interference fit. Specifically, the plate head 6100 is received by the inner surface of the inner wall of the piston 5000 (e.g., ...). Figure 15 The inner surfaces 510b and 510c of the inner wall 510 define the seat receiving hole and extend through the seat receiving hole, and the seat body 6200 is received by the lower surface of the connecting wall of the piston 5000 and the inner surface of the outer wall (e.g., Figure 15 The lower surface 520b, connecting wall 520, inner surface 580d, and outer wall 580 define the receiving gap of the plate. The diameter of the receiving hole is slightly smaller than the diameter of the plate head 6100, and the diameter of the receiving gap is slightly smaller than the diameter of the plate body 6200. This allows the piston 5000 to hold the plate 6000 in those gaps via an interference fit, so that the piston 5000 and the plate 6000 can move together.

[0097] The base plate 6000 also includes a surface (e.g., Figure 17 A sealing surface 6400 extending circumferentially between surfaces 620d and 620f. The sealing surface 6400 is configured to press against the valve seat 7000, as described below. More specifically, when the valve 1000 is closed, at least a portion of the sealing surface 6400 extends circumferentially (e.g., ...). Figure 20 The circumference 760c) is sealed to the valve seat 7000.

[0098] More specifically, the piston 5000 and its attached seat plate 6000 can be in a sealed and / or closed position (e.g., Figure 12A , 21A 21B) and non-sealed and / or open positions (e.g., Figure 12B) when the piston 5000 and attached seat disc 6000 are in the sealed position, the sealing surface 6400 of the seat disc 6000 sealingly engages the valve seat 7000 to prevent fluid flow from the inlet void 2200a through the valve 1000 to the outlet void 2200d and the valve 1000 is thus closed. On the other hand, when the piston 5000 and attached seat disc 6000 are in the unsealed position, the sealing surface 6400 of the seat disc 6000 is displaced from the valve seat 7000 and does not sealingly engage the valve seat 7000, which means that fluid can flow from the inlet void 2200a through the valve 1000 to the outlet void 2200d. The spring 4000 biases the piston 5000 and seat disc 6000 to the sealed position and thus the valve 1000 is biased in the closed and / or sealed position.

[0099] As best shown in Figure 21A and 21B The body 2000 has an outer surface 2300 that tapers at a slight angle relative to the longitudinal axis L V The eighth outer surface 2300h has a first outer diameter 1010 and a second outer diameter 1020 that is less than the first outer diameter 1010 to define a taper of the eighth outer surface 2300h. The body 2000 further has a ninth outer surface 2300i that is angled (e.g., 45 degrees) relative to the longitudinal axis L V The ninth outer surface 2300i has a tenth outer surface 2300j that is parallel relative to the longitudinal axis L V The tenth outer surface 2300j has an outer diameter 1030 that is less than each of the first outer diameter 1010 and the second outer diameter 1020 of the eighth outer surface 2300h of the body 2000.

[0100] In the illustrated example, the ninth outer surface 2300i is angled (e.g., 45 degrees) toward the longitudinal axis L V inclined inwardly to connect the eighth outer surface 2300h and the tenth outer surface 2300j. As such, the eighth outer surface 2300h, the ninth outer surface 2300i, and the tenth outer surface 2300j define one or more tapered portions of the outer surface 2300 of the body 2000. For example, a first tapered portion 1040 (i.e., a first portion) is formed along the eighth outer surface 2300h and a second tapered portion 1050 (i.e., a second portion) is formed along the ninth outer surface 2300i and the tenth outer surface 2300j. In some examples, an amount of taper in the second tapered portion 1060 is defined by an angle at which the ninth outer surface 2300i is inclined to connect the eighth outer surface 2300h to the tenth outer surface 2300j. As Figure 21A and 21B In the illustrated example, the ninth outer surface 2300i is angled (e.g., 45 degrees) toward the longitudinal axis L VThe tapering is such that the diameter (e.g., the first outer diameter 1010) of the first tapered portion 1040 is greater than the diameter (e.g., the outer diameter 1020) of the second tapered portion. This tapering can be modified or eliminated and is not critical to the operation of the devices disclosed herein.

[0101] In operation, the valve 1000 is attached to a pressurized vessel (not shown) that stores pressurized fluid via the conduit 1060. In one non-limiting example, the body 2000 includes a set of threads 1070 configured to threadably engage a corresponding set of threads 1080 on the conduit 1060 to removably couple the body 2000 to the conduit 1060. The conduit 1060 further includes a conduit void 1090 that includes an inner surface 1100 that defines an inner diameter 1110 of the conduit 1060. Thus, in some examples, when the threads 1070 of the body 2000 are threaded into the corresponding threads 1080 of the conduit 1060, the inner surface 1100 of the conduit 1060 sealingly engages the eighth outer surface 2300h of the body 2000. While Figure 21A and 21B While the use of threads to removably couple the body 2000 to the conduit 1060 is shown, it will be understood that the valve 1000 can be coupled to the conduit 1060 using other coupling mechanisms, such as an interference fit, a compression fit, and / or other such coupling mechanisms.

[0102] As Figure 21B explained in the Background, the inner diameter 1110 of the conduit 1060 is greater than the outer diameter 1030 of the tenth outer surface 2300j of the body 2000. Thus, when the body 2000 is sealingly engaged with the conduit 1060, a circumferential void 1120 is defined between the ninth outer surface 2300i and the tenth outer surface 2300j of the body 2000 and the inner surface 1100 of the conduit 1060. Further, during operation, the conduit void 1090 is in constant fluid communication with the inlet void 2200a and the valve seat void 7500. Pressurized fluid entering the valve seat void 7500 via the conduit void 1090 and the inlet void 2200a opposes the biasing force exerted by the spring 4000 on the piston 5000 and the seat disc 6000. The presence of the circumferential void 1100 advantageously accumulates particles (e.g., dust) and other such debris present in the pressurized fluid within the conduit 1060. More specifically, the circumferential void 1100 accumulates particles and other such debris from entering the inlet 2200a and building up on the inner surfaces and components of the valve 1000.

[0103] When the pressurized fluid in the vessel exceeds a threshold pressure, and particularly when the force exerted by the pressurized fluid on the seat disc 6000 exceeds the biasing force of the spring 4000, the seat disc 6000 disengages the valve seat 7000 and moves from a sealing position (e.g. Figure 21A and 21B ) to a non-sealing position (e.g.Figure 12B ). This opens the valve 1000 and enables fluid to flow from the valve seat void 7500 through the gap between the body 2000 and the piston 5000 (e.g., gap 110a-d of FIG. 1 1 ) and through the opening in the set screw 3000 into the outlet void 2200d and then to ambient atmosphere. Figure 13

[0104] After sufficient fluid discharge, the force exerted by the pressurized fluid on the seat disc 6000 drops below the biasing force exerted by the spring 4000. Thus, the spring 4000 forces the piston 5000 and attached seat disc 6000 to the sealed position, thereby closing the valve 1000.

[0105] While specific embodiments of the application have been described in detail, those skilled in the art will appreciate that various modifications and alternatives to those details could be developed in light of the overall teachings of the disclosure. Accordingly, the particular arrangements disclosed are meant to be illustrative only and not limiting as to the scope of the application, which is to be given the full breadth of the appended claims and any and all equivalents thereof.

[0106] Various embodiments of a valve for delivering fluid of the present disclosure have a closed position and an open position and include a body, a valve seat disposed in the body, a retainer disposed in the body, and a seat disc. The valve seat includes one or more inner surfaces and an outer surface, and the one or more inner surfaces define an inner void. The seat disc is connected to the retainer and is movable with the retainer between a first position in which the seat disc sealingly engages the outer surface of the valve seat and a second position in which the seat disc disengages from the outer surface of the valve seat. The valve is in the closed position when the seat disc is in the first position and is in the open position when the seat disc is in the second position.

[0107] In one such embodiment, the valve further includes a spring that biases the seat disc toward the second position.

[0108] In another such embodiment, the retainer defines a second inner void in which at least a portion of the spring is received.

[0109] In another such embodiment, the retainer defines a first opening and a second opening.

[0110] In another such embodiment, the first opening is disposed below the second opening with respect to a longitudinal axis of the body.

[0111] In another such embodiment, the first and second openings have different geometries.

[0112] ​In another such embodiment, a gap is formed between the holder and the body such that, when the valve is in the open position, the gap is in fluid communication with the inner void of the valve seat, the first opening, and the second opening.

[0113] In another such embodiment, the holder includes a plurality of body guide surfaces that guide the holder relative to the body.

[0114] In another such embodiment, each body guide surface includes a radius of curvature.

[0115] In another such embodiment, a plurality of gaps are defined between the holder and the body, each of the plurality of gaps disposed between two consecutive body guide surfaces. The plurality of gaps are in fluid communication with the inner void of the valve seat when the valve is in the open position.

[0116] In another such embodiment, the valve seat guides one or more inner surfaces of the body.

[0117] In another such embodiment, the body is made of a first material and the valve seat is made of a different second material. The first material of the body includes a greater coefficient of thermal expansion than the second material of the valve seat.

[0118] In another such embodiment, the body and the valve seat are configured such that, as the temperature approaches a cryogenic temperature, the body compresses the valve seat radially inward to a greater extent.

[0119] In another such embodiment, the valve seat disc includes one or more outer surfaces and one or more inner surfaces, the one or more inner surfaces defining an inner void of the valve seat disc.

[0120] In another such embodiment, when the valve seat disc is in the first position, the valve seat extends at least partially into the inner void of the valve seat disc.

[0121] In another such embodiment, when the valve seat disc is in the first position, at least one of the one or more inner surfaces of the valve seat disc contacts the outer surface of the valve seat.

[0122] In another such embodiment, the valve is configured to have one or more closed positions, including the closed position, and one or more open positions, including the open position. The valve seat disc is configured to have a plurality of positions, including the first position and the second position.

[0123] In another such embodiment, the retainer defines a first inner void and a plurality of undercuts that at least partially surround a perimeter of the first inner void. The plurality of undercuts can deformably compress the valve seat disc to secure the valve seat disc in the first inner void.

[0124] In another such embodiment, the valve further includes a spring that biases the valve seat disc toward the second position. The retainer includes a first spring retaining wall around which the spring is partially disposed.

[0125] In another such embodiment, the valve further includes a set screw that includes a second spring retaining wall around which the spring is partially disposed such that the spring extends between the set screw and the retainer.

[0126] In another such embodiment, the valve further includes a taper defined in the body. The tapered portion circumferentially surrounds an inlet of the body.

[0127] In another such embodiment, the tapered portion includes a first portion having a first diameter and a second portion having a second diameter that is less than the first tapered portion diameter.

[0128] In another such embodiment, the retainer includes an outer wall, an inner wall, and an annular connecting wall extending between and connected to each of the outer wall and the inner wall.

[0129] In another such embodiment, the outer wall, the inner wall, and the annular connecting wall of the retainer define a receiving aperture and a receiving void configured to receive and retain the valve seat disc.

[0130] In another such embodiment, the valve seat disc includes a disc body and a disc head extending from the disc body. The disc body is received in the receiving void and the disc head extends through the receiving aperture.

[0131] In another such embodiment, the receiving void receives the disc body and the receiving aperture retains the disc head via an interference fit.

Claims

1. A valve for delivering a fluid, the valve having a closed position and an open position and comprising: a body; a valve seat disposed in the body, the valve seat comprising one or more inner surfaces and an outer surface, the one or more inner surfaces defining an inner void, the outer surface being curved, wherein the valve seat is sized and shaped for an interference fit with the body, and wherein the body is made of a first material and the valve seat is made of a different second material, and wherein the first material of the body includes a greater coefficient of thermal expansion than the second material of the valve seat; a holder disposed in the body; and a valve seat disc comprising an inner surface comprising a sealing surface, the seat disc being connected to the holder and movable with the holder between a first position in which the sealing surface of the valve seat disc sealingly engages the outer surface of the valve seat and a second position in which the sealing surface of the valve seat disc is disengaged from the outer surface of the valve seat, wherein the valve is in the closed position when the valve seat disc is in the first position and the valve is in the open position when the valve seat disc is in the second position.

2. The valve of claim 1, further comprising a spring biasing the valve seat disc toward the second position.

3. The valve of claim 2, wherein the holder defines a second inner void in which at least a portion of the spring is received.

4. The valve of claim 1, wherein the holder comprises a plurality of body guide surfaces that guide the holder relative to the body.

5. The valve of claim 4, wherein each body guide surface includes a radius of curvature.

6. The valve of claim 4, wherein a plurality of gaps are defined between the holder and the body, each of the plurality of gaps being disposed between two consecutive body guide surfaces; and wherein the plurality of gaps are in fluid communication with the inner void of the valve seat when the valve is in the open position.

7. The valve of claim 1, wherein the valve seat engages one or more inner surfaces that guide the body.

8. The valve of claim 1, wherein the body and the valve seat are configured such that as temperature approaches a cryogenic temperature, the body compresses the valve seat radially inward to a greater extent.

9. The valve of claim 1, wherein the valve seat disc comprises one or more outer surfaces and one or more inner surfaces, the one or more inner surfaces defining an inner void of the valve seat disc.

10. The valve of claim 9, wherein when the valve seat disc is in the first position, the valve seat at least partially extends into the inner void of the valve seat disc.

11. The valve of claim 10, wherein when the valve seat disc is in the first position, at least one of the one or more inner surfaces of the valve seat disc contacts the outer surface of the valve seat. ​ 12. The valve of claim 1, wherein the valve is configured to have one or more closed positions and one or more open positions, the one or more closed positions including the closed position, and the one or more open positions including the open position; and wherein the valve seat disc is configured to have a plurality of positions, the plurality of positions including the first position and the second position.

13. The valve of claim 2, wherein the retainer includes a first spring retaining wall around which the spring is partially disposed.

14. The valve of claim 13, further comprising a set screw including a second spring retaining wall around which the spring is partially disposed such that the spring extends between the set screw and the retainer.

15. The valve of claim 1, further comprising a tapered portion defined in the body, wherein the tapered portion circumferentially surrounds an inlet of the body.

16. A valve for delivering a fluid, the valve having a closed position and an open position and comprising: a body; a valve seat disposed in the body, the valve seat including one or more inner surfaces and an outer surface, the one or more inner surfaces defining an inner void; a retainer disposed in the body, wherein the retainer includes an outer wall, an inner wall, and an annular connecting wall extending between and connected to each of the outer wall and the inner wall; and a valve seat disc including an inner surface including a sealing surface, the seat disc connected to the retainer and movable with the retainer between a first position in which the sealing surface of the valve seat disc sealingly engages the outer surface of the valve seat and a second position in which the sealing surface of the valve seat disc is disengaged from the outer surface of the valve seat, wherein the outer wall, the inner wall, and the annular connecting wall of the retainer define a receiving aperture and a receiving void configured to receive and retain the valve seat disc, wherein the valve seat disc includes a seat disc body and a seat disc head extending from the seat disc body, and wherein the seat disc body is received in the receiving void and the seat disc head extends through the receiving aperture, wherein the valve is in the closed position when the valve seat disc is in the first position and the valve is in the open position when the valve seat disc is in the second position.

17. The valve of claim 16, wherein the receiving void receives the seat disc body and the receiving aperture retains the seat disc head via an interference fit.

18. The valve of claim 1, wherein the sealing surface of the valve seat disc is a curved sealing surface configured to sealingly engage a circumference of the valve seat when the valve is in the closed position.

19. The valve of claim 1, wherein the sealing surface of the valve seat disc is configured to bear inwardly on the valve seat when the valve is in the closed position such that a seal is maintained about the valve seat when a longitudinal axis of the retainer is misaligned with a longitudinal axis of the valve seat.

20. The valve of claim 1, wherein the outer surface of the valve seat is curved such that the valve seat is partially spherical.

21. The valve of claim 20, wherein the body is configured to contact the valve seat along a first circumference and a second circumference of the valve seat, and wherein at least a portion of the sealing surface is configured to sealingly engage the valve seat along a third circumference of the valve seat.

22. A valve for delivering a fluid, the valve having a closed position and an open position and comprising: a body including a first inner surface defining a cylindrical first void, a second inner surface defining a frustoconical second void, and a third inner surface defining a cylindrical third void; a valve seat disposed in the body, the valve seat including one or more inner surfaces defining an inner void and an outer surface that is curved such that the valve seat is partially spherical, wherein the first inner surface of the body is configured to contact the valve seat along a first circumference on the outer surface of the valve seat, and wherein the second inner surface of the body is configured to contact the valve seat along a second circumference on the outer surface of the valve seat; a retainer disposed in the body; and a valve seat disk connected to the retainer and movable with the retainer between a first position in which the valve seat disk sealingly engages the valve seat along a third circumference of the outer surface of the valve seat and a second position in which the sealing surface of the valve seat disk is disengaged from the outer surface of the valve seat, wherein the valve is in the closed position when the valve seat disk is in the first position and the valve is in the open position when the valve seat disk is in the second position.

23. The valve of claim 22, wherein the valve seat is sized such that a diameter of the first circumference of the valve seat is greater than a diameter of the cylindrical third void of the body and a diameter of the second circumference of the valve seat is greater than a diameter of a portion of the frustoconical second void of the body.

24. The valve of claim 22, wherein the outer surface of the valve seat is smooth polished to prevent accumulation of particles on the outer surface of the valve seat that would disrupt a seal quality between the valve seat disk and the valve seat.

25. The valve of claim 24, wherein the valve seat is sized and shaped for an interference fit with the body, and wherein the body includes an inner surface having a rough surface finish to grip the outer surface of the valve seat.

26. The valve of claim 22, wherein the body is made of a first material and the valve seat is made of a second material.

27. The valve of claim 26, wherein the first material of the body has a greater coefficient of thermal expansion than the second material of the valve seat to increase a compressive force exerted by the body on the valve seat when subjected to cryogenic temperatures.

28. The valve of claim 26, wherein the valve seat disk is made of a third material. ​ 29. The valve of claim 28, wherein the third material of the valve seat disc has a greater coefficient of thermal expansion than the second material of the valve seat, such that the valve seat disc is configured to contract a greater degree than the valve seat when subjected to cryogenic temperatures to improve the tightness of the seal between the valve seat disc and the valve seat in the closed position.

30. The valve of claim 28, wherein the first material is brass, the second material is stainless steel, and the third material is a polymer.

31. A valve for delivering a fluid, the valve comprising: a body including one or more inner surfaces; a valve seat including a partially spherical outer surface configured to contact at least one of the one or more inner surfaces of the body to secure and form a sealed connection with the body, wherein the body is made of a first material having a first coefficient of thermal expansion and the valve seat is made of a second, different material having a second coefficient of thermal expansion, and wherein the first coefficient of thermal expansion is greater than the second coefficient of thermal expansion; and a valve seat disc configured to move between a closed position in which the valve seat disc sealingly engages the outer surface of the valve seat and an open position in which the valve seat disc is disengaged from the outer surface of the valve seat.

32. The valve of claim 31, wherein the body is configured to compress radially inward when subjected to cryogenic temperatures to further form the sealed connection with the valve seat.

33. The valve of claim 31, wherein the valve seat disc includes one or more inner surfaces, wherein at least one of the inner surfaces of the valve seat disc is configured to contact the outer surface of the valve seat in the closed position.

34. The valve of claim 33, wherein the one or more inner surfaces of the valve seat disc define an inner void, wherein the valve seat is configured to extend at least partially into the inner void in the closed position.

35. The valve of claim 31, further comprising a spring configured to bias the valve seat disc toward the closed position.

36. The valve of claim 31, wherein the valve seat disc is made of a third material.

37. The valve of claim 36, wherein the third material has a third coefficient of thermal expansion that is greater than the second coefficient of thermal expansion, such that the valve seat disc is configured to contract a greater degree than the valve seat when subjected to cryogenic temperatures to further form the sealed connection between the valve seat disc and the valve seat in the closed position.

38. A valve for delivering a fluid, the valve comprising: a body including a plurality of inner surfaces; a valve seat including a partially spherical outer surface, wherein a first portion of the partially spherical outer surface is configured to contact at least one of the plurality of inner surfaces of the body to secure the valve seat within the body; and a valve seat disc configured to move between a closed position in which the valve seat disc sealingly engages the outer surface of the valve seat and an open position in which the valve seat disc is disengaged from the outer surface of the valve seat. a valve seat disc configured to move between a closed position in which the valve seat disc sealingly engages a second outer surface of the partially spherical outer surface of the valve seat and an open position in which the valve seat disc is disengaged from the partially spherical outer surface of the valve seat.

39. The valve of claim 38, wherein the body is configured to compress radially inward to further form the sealing connection with the valve seat when subjected to cryogenic temperatures.

40. The valve of claim 39, wherein the plurality of inner surfaces includes a first inner surface defining a cylindrical first void and a second inner surface defining a frustoconical second void.

41. The valve of claim 40, wherein the first inner surface and the second inner surface are configured to contact the first portion of the partially spherical outer surface of the valve seat to secure the valve seat in place.

42. The valve of claim 38, wherein the valve seat is secured to the body via an interference fit.

43. The valve of claim 42, wherein at least one of the plurality of inner surfaces of the body has a rough surface finish to grip the partially spherical outer surface of the valve seat.

44. The valve of claim 38, wherein the partially spherical outer surface of the valve seat is smoothly polished to prevent particle accumulation on the partially spherical outer surface of the valve seat.

45. The valve of claim 38, wherein the body is made of a first material having a first coefficient of thermal expansion and the valve seat is made of a second material having a second coefficient of thermal expansion, and wherein the first coefficient of thermal expansion is greater than the second coefficient of thermal expansion to increase a compressive force exerted by the body on the valve seat at cryogenic temperatures.

46. The valve of claim 45, wherein the valve seat disc is made of a third material, wherein the third material has a third coefficient of thermal expansion that is greater than the second coefficient of thermal expansion, such that the valve seat disc is configured to shrink a greater extent than the valve seat when subjected to cryogenic temperatures to further form the sealing connection between the valve seat disc and the valve seat in the closed position.

47. The valve of claim 46, wherein the second material is stainless steel and the third material is a polymer.

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