Pressure reducer assembly

Abstract

A pressure reducer assembly includes a pressure reducer body defining at least one pressure reducer chamber along a central axis. The pressure reducer chamber includes an inlet section and an outlet section fluidly coupled with the inlet section. The pressure reducer assembly further includes a spring-operated hollow piston rod having a center along the central axis, a cylindrical inner peripheral surface including an inner diameter, and a cylindrical outer peripheral surface including an outer diameter. A diaphragm made of an elastic material is adapted to be operatively coupled with the piston rod. The diaphragm includes a central hole having a center along the central axis and a diameter. Wherein, in an uninstalled state, the outer diameter of the piston rod is greater than the diameter of the central hole of the diaphragm, and in an installed state, the outer diameter of the piston rod is the same as the diameter of the central hole of the diaphragm, and the diaphragm is assembled on the piston rod such that the central axis of the piston rod coincides with the central axis of the diaphragm.

Description

Technical Field

[0001] This disclosure relates to a pressure reducer assembly. More specifically, this disclosure relates to an improved and cost-effective pressure reducer diaphragm. Background Technology

[0002] Pressure regulators are found in many common household and industrial applications. For example, they are used to regulate propane in gas grills, natural gas in domestic furnaces, oxygen and anesthetic gases in medical and dental equipment, compressed air in pneumatic automation systems, fuel in engines, and irrigation in gardening systems. As this partial list indicates, pressure regulators have many applications; however, in each of these applications, they provide the same function. A pressure regulator reduces the supply (or inlet) pressure to a lower outlet pressure and maintains this outlet pressure despite fluctuations in the inlet pressure. The reduction of the inlet pressure to a lower outlet pressure is a key characteristic of pressure regulators.

[0003] The pressure regulator includes a regulator body defining a pressure compensation orifice, and also includes a spring-operated piston rod and a radially sealed diaphragm-like structure that radially seals within the regulator body and allows for pressure control. However, due to the axial movement of the piston rod, grooves may form in the sealing surface over time, potentially leading to leakage. The pressure regulator may leak and lose fluid through the pressure compensation orifice, thereby reducing the regulator's functional accuracy.

[0004] Efforts have been made over time to overcome the aforementioned drawbacks. Improved designs include pressure reducers with rolling diaphragm technology. The axial movement of this diaphragm is caused by the oscillating motion of a U-shaped geometry. However, this diaphragm has a larger diameter, requires more installation space, and is expensive to manufacture. An example of a rolling diaphragm is provided in Chinese Utility Model 206,429,714.

[0005] Furthermore, pressure reducers exist with flat diaphragms that are reinforced in the middle with a fabric insert and are non-stretchable. These flat diaphragms are axially pressed between two metal discs, resulting in high assembly and manufacturing costs. Moreover, because the flat diaphragms are non-stretchable, their stroke is very small (up to 2 mm).

[0006] Furthermore, U.S. Patent Application US 2018 / 0120866 A1 (hereinafter referred to as '866 Reference) discloses an example of a regulator device including a diaphragm. '866 Reference discloses a regulator device comprising a hollow body having an inlet and an outlet for a liquid, a tubular valve member housed within the hollow body, a resilient diaphragm, and a helical spring disposed at the periphery of the valve member. The tubular valve member includes an outer annular flange to which the inner peripheral edge of the annular resilient diaphragm is mounted. Furthermore, the outer annular edge of the resilient diaphragm is fastened to the hollow body via an open annular edge of a sleeve. The helical spring has a calibrated spring modulus and is disposed at the periphery of the valve member. The helical spring acts on the valve member to counteract the force generated on the flange by the pressure of the liquid collected in the regulating chamber, thereby holding the regulating end at a normal distance from the liquid inlet. Additionally, the diameter of the central hole of the annular resilient diaphragm is larger than the outer diameter of the cylindrical outer surface of the tubular valve member. The disclosed annular elastic diaphragm is axially clamped between corresponding components of the regulating device at its inner and outer peripheral edges, respectively. Furthermore, the stroke of the hollow valve component is geometrically limited. Simultaneously, the function of the regulating device depends on the axial clamping connection, making it inherently fragile.

[0007] Therefore, there is a need for an improved and cost-effective diaphragm design that can help maintain the functional accuracy of the pressure reducer over long periods of time. Summary of the Invention

[0008] In view of the foregoing, the object of the present invention is to solve or at least reduce the aforementioned disadvantages. This object is achieved at least in part by a pressure reducer assembly. The pressure reducer assembly includes a pressure reducer body defining at least one pressure reducer chamber along a central axis. The pressure reducer chamber includes an inlet section and an outlet section, the outlet section being fluidly connected to the inlet section such that the inlet section and the outlet section respectively allow fluid to enter and exit. The assembly also includes a spring-operated piston rod having a center, an inner diameter, and an outer diameter along the central axis. Furthermore, a diaphragm made of an elastic material is adapted to be operatively coupled to the piston rod. The diaphragm includes a central aperture having a center and a diameter along the central axis. The outer diameter of the piston rod is larger than the diameter of the central aperture of the diaphragm, and the diaphragm is assembled on the piston rod such that the central axis of the piston rod coincides with the central axis of the diaphragm.

[0009] Furthermore, the piston rod is a hollow piston rod, which also has a cylindrical inner circumferential surface that defines the inner diameter and a cylindrical outer circumferential surface that defines the outer diameter. The outer diameter of the piston rod is larger than the diameter of the central hole of the diaphragm in the uninstalled state, while in the installed state, the outer diameter of the piston rod is the same as the diameter of the central hole of the diaphragm.

[0010] Therefore, this disclosure provides an improved diaphragm design for a pressure reducer. Advantageously, the diaphragm includes a central bore, the diameter of which, in the uninstalled state, is smaller than the outer diameter of the piston rod, such that when the diaphragm is forcibly installed or assembled onto the piston rod, the diaphragm deforms due to radial stress. This deformation of the diaphragm significantly improves the stroke length of the diaphragm.

[0011] The inner diameter is the diameter of the hollow portion of the piston rod. The outer diameter is the diameter of the outer cylindrical surface. Furthermore, the inner cylindrical surface is opposite to the outer cylindrical surface.

[0012] According to one embodiment of this disclosure, in the uninstalled state, the diameter of the central hole of the diaphragm is equal to the inner diameter of the piston rod. The diameter of the central hole of the diaphragm is preferably smaller than the outer diameter of the piston rod in the uninstalled state, so as to generate radial stress on the diaphragm, which causes deformation of the diaphragm when it is in the installed state. The deformation shown in this disclosure is a conical deformation, such that the conical deformation of the diaphragm leads to bistable buckling of the diaphragm.

[0013] According to one embodiment of this disclosure, the diaphragm is made of silicone resin. Silicone resin is known to maintain flexibility and low compressibility under extreme heat or cold. Silicone rubber is very durable and generally possesses good mechanical properties. Due to its durability, it is extremely reliable and trusted to maintain performance over long periods. Therefore, silicone resin diaphragms can be durable and cost-effective, as they may require less maintenance. Furthermore, silicone resin diaphragms provide good electrical insulation, are flame-retardant, and have low chemical reactivity.

[0014] According to one embodiment of this disclosure, the diaphragm is manufactured by stamping. The stamping process is cost-effective, rapid, and requires minimal labor and machine operation. Furthermore, the stamping process reduces material waste, improves precision, and can be automated.

[0015] According to one embodiment of this disclosure, the piston rod includes a diaphragm support surface. The diaphragm support surface prevents the diaphragm from sliding away from the piston rod. Furthermore, it transmits fluid forces to the piston rod, causing axial displacement of the piston rod.

[0016] According to one embodiment of this disclosure, the annular nose is configured adjacent to the diaphragm to press the diaphragm downward when the spring is in the extended state, such that the spring presses the diaphragm in a direction opposite to the direction of the force transmitted by the annular nose when pressing the diaphragm. This prevents the diaphragm from slipping and can help hold the diaphragm in place during operation of the pressure reducing assembly.

[0017] In a further improved embodiment, the annular nose further includes a stop surface that engages with the inclined surface of the diaphragm support surface when the spring is in the extended state. This engagement between the stop surface and the inclined surface prevents all forces from being transmitted to the diaphragm. Therefore, the engagement between the stop surface and the inclined surface further prevents damage to the diaphragm and diaphragm adhesion to the annular nose.

[0018] Other features and aspects of the invention will be apparent from the following description and drawings. Attached Figure Description

[0019] The invention will be described in more detail with reference to the accompanying drawings, in which:

[0020] Figure 1 A cross-sectional view of a pressure reducer assembly according to one aspect of this disclosure is shown;

[0021] Figure 2A A cross-sectional view of the piston rod and diaphragm before assembly is shown according to one aspect of this disclosure;

[0022] Figure 2B A cross-sectional view of the assembled piston rod and diaphragm according to one aspect of this disclosure is shown;

[0023] Figure 3A A cross-sectional view of a pressure reducer according to one aspect of this disclosure is shown;

[0024] Figure 3B Another cross-sectional view of a pressure reducer according to one aspect of this disclosure is shown; and

[0025] Figure 4 A perspective view of the pressure reducing device body according to one aspect of this disclosure is shown. Detailed Implementation

[0026] The invention will now be described more fully with reference to the accompanying drawings, in which exemplary embodiments of the invention incorporating one or more aspects thereof are illustrated. However, the invention may be embodied in many different forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art. For example, one or more aspects of the invention may be used in other embodiments, and even in other types of structures and / or methods. In the drawings, the same numerals denote the same elements.

[0027] Certain terms are used herein for convenience only and should not be considered as limiting the invention. For example, “upper,” “lower,” “front,” “rear,” “side,” “longitudinal,” “lateral,” “transverse,” “upward,” “downward,” “forward,” “backward,” “left,” “right,” “horizontal,” “vertical,” “upward,” “inner,” “outer,” “inward,” “outer,” “top,” “bottom,” “higher,” “above,” “below,” “center,” “middle,” “between,” “end,” “adjacent,” “near,” “far,” “radial,” “circumferential,” etc., describe only the constructions shown in the figures. In practice, components may be oriented in any direction, and therefore, the terms should be understood to cover such variations unless otherwise specified.

[0028] Figure 1 A pressure reducer assembly 100 is shown. The pressure reducer assembly 100 of this disclosure is used to reduce the fluid pressure of fluids intended for drip irrigation or other gardening operations. However, the pressure reducer assembly 100 of this disclosure is not limited to its application areas. The pressure reducer assembly 100 can be conveniently and effectively used in any other domestic or industrial application.

[0029] Furthermore, the fluid used with the pressure regulator assembly 100 can be a liquid (such as water) or a gas (such as air), depending on the application requirements of the pressure regulator assembly 100. The fluid can be selectively supplied by a fluid source (not shown) at a pressure equal to or greater than the output pressure requirement of the application using the pressure regulator assembly 100.

[0030] The fluid source can advantageously be equipped with valves, for example, to regulate the flow of fluid from the fluid source. Furthermore, the fluid source can be equipped with automatically operable accessories that can automatically regulate the flow of fluid from the fluid source. For example, when the fluid is water, the fluid source can be equipped with a water supply computer. The water supply computer can allow and regulate the flow of water from the fluid source (or water source) based on factors such as the time of day and preset water outflow timing.

[0031] A fluid source may be fluidly connected to the pressure regulator assembly 100 via a hose or any other means known and understood in the relevant art, without limiting the scope of this disclosure. In some embodiments, the fluid source may be fluidly connected to multiple pressure regulator assemblies 100 via a fluid distributor (which is typically available in the relevant art).

[0032] like Figure 1As shown, the pressure reducer assembly 100 includes a pressure reducer body 110. The pressure reducer body 110 of this disclosure is a cylindrical body having a central axis X-X' along the longitudinal direction of the pressure reducer assembly 100. However, in practical implementations of this disclosure, the pressure reducer body 110 may have any other shape without limiting the scope of this disclosure. The pressure reducer body 110 may be made of brass, plastic, and aluminum. Various grades of stainless steel (e.g., 303, 304, and 316) may also be used to manufacture the pressure reducer body 110. However, any other material suitable for handling various fluids and operating environments may be used to make or manufacture the pressure reducer body 110. Furthermore, without limiting the scope of this disclosure, any suitable manufacturing process may be used to manufacture the pressure reducer body 110.

[0033] A pressure reducer body 110 defines at least one pressure reducer chamber 120. The pressure reducer chamber 120 is defined along a central axis X-X'. The pressure reducer chamber 120 includes an inlet section 122 and an outlet section 124 fluidly connected to the inlet section 122, such that the inlet section 122 and the outlet section 124 allow fluid to enter and exit, respectively. The inlet section 122 is defined along a central axis Y-Y', and the outlet section 124 is defined along a central axis Z-Z'. In some embodiments, such as Figure 1 As shown, the central axes Y-Y', Z-Z', and X-X' coincide with each other along the longitudinal direction of the pressure reducer assembly 100. In some embodiments, the central axes Y-Y', Z-Z', and X-X' may be parallel to each other, but do not necessarily have to coincide with each other. In some embodiments, the central axes Y-Y', Z-Z', and X-X' may have any other angular orientation relative to each other or relative to the longitudinal direction of the pressure reducer assembly 100, without limiting the scope of this disclosure in any way.

[0034] Inlet section 122 is fluidly connected to a fluid source via coupling 126. Coupling 126 can be advantageously designed such that it selectively allows fluid to pass through (receive from the fluid source) only when it is fluidly connected to inlet section 122 of pressure regulator assembly 100. This design of coupling 126 substantially prevents fluid leakage when pressure regulator assembly 100 is not in operation or not in use. In some embodiments, inlet section 122 may be sealingly connected to coupling 126. This seal may be provided by a gasket, O-ring, or any other known and readily available sealing device (or sealing element).

[0035] The inlet section 122 also includes a threaded portion 123 such that the threaded portion 123 threadedly engages with the complementary threaded portion 127 of the coupling joint 126. Therefore, in a preferred embodiment of this disclosure, the inlet section 122 and the coupling joint 126 are threadedly engaged or connected to each other. However, in a practical implementation of this disclosure, the fluid connection between the inlet section 122 and the coupling joint 126 can be achieved by any means known and understood in the relevant art.

[0036] In a preferred embodiment of this disclosure, such as Figure 1 As shown, the inlet section 122 also includes a filter element 125. The filter element 125 is operatively coupled to the inlet section 122 such that it filters the fluid received from the fluid source before it enters the pressure regulator chamber 120. The filter element 125 prevents clogging of the inlet section 122, thereby promoting smooth operation of the pressure regulator assembly 100. The filter element 125 can be coupled to the inlet section 122 in any manner known in the art. For example, the filter element 125 can be glued to the inlet section.

[0037] Furthermore, depending on the application requirements, the filter element 125 can have any shape, size, and type. In some embodiments, the filter element 125 can be a surface filter made of tightly woven fabric or treated paper with uniform pore size. Fluid from a fluid source flows through the pores of the filter element 125, causing contaminants to be stopped on the surface of the filter element. In some embodiments, the filter element 125 can be a depth filter made of layers of fabric or fibers, providing numerous tortuous paths for fluid flow. The pores or channels are larger than the rated size of the filter element 125 so that particles are retained in the depth of the medium rather than on the surface. In some embodiments, the filter element 125 can be 5-micron, woven mesh, micron-scale, porous metal, or magnetic types. Micron-scale and 5-micron elements have non-washable filter media and can be disposed of when removed, while porous metal, woven mesh, and magnetic filter elements are designed to be washed and reused.

[0038] In addition, such as Figure 1As shown, inlet section 122 includes valve 129. Valve 129 selectively allows fluid from a fluid source through pressure reducing chamber 120. Valve 129 selectively allows and blocks fluid flow via inlet section 122. Valve 129 selectively allows fluid to flow to outlet section 124, for example, to maintain a constant output pressure of pressure reducing assembly 100. Valve 129 is located downstream of filter element 125 in the direction of fluid flow. Valve 129 can be connected to inlet section 122 by any suitable means known in the art. However, in a preferred embodiment, valve 129 is screwed into inlet section 122. The threaded connection between valve 129 and inlet section 122 allows valve 129 to move relative to inlet section along the longitudinal direction of pressure reducing assembly 100. Movement of valve 129 along the longitudinal direction of pressure reducing assembly 100 can also help regulate the constant output pressure generated by pressure reducing assembly 100.

[0039] In some embodiments, valve 129 may be along the central axis X-X' of pressure reducer body 110. In some embodiments, valve 129 may be along the central axis Y-Y' of inlet section 122. In some embodiments, valve 129 may be parallel to the central axis X-X' of pressure reducer body 110. In some embodiments, valve 129 may be offset relative to the central axis X-X' of pressure reducer body 110. In some embodiments, valve 129 may be at an angle to the central axis X-X' of pressure reducer body 110. In some embodiments, valve 129 may be parallel to the central axis Y-Y' of inlet section 122. In some embodiments, valve 129 may be offset relative to the central axis Y-Y' of inlet section 122. In some embodiments, valve 129 may be at an angle to the central axis Y-Y' of inlet section 122. Valve 129 may have an orientation relative to the longitudinal direction of pressure reducer assembly 100 without limiting the scope of this disclosure in any way.

[0040] Valve 129 also includes a seal 130. Seal 130 may be an O-ring or any other type of seal commonly available in the relevant field. In some embodiments, seal 130 may be a flat seal. In some embodiments, seal 130 may be a radial seal, i.e., providing a seal for fluid in the radial direction.

[0041] Continue to refer to Figure 1 And further reference Figure 2A and Figure 2BThe pressure reducing chamber 120 also includes a spring-operated piston rod 121. The piston rod 121 is a hollow rod that allows fluid with reduced pressure to pass through the pressure reducing assembly 100. When the piston rod 121 is assembled in the pressure reducing chamber 120, the piston rod 121 has a center “X” along the central axis X-X'. Furthermore, the piston rod 121 has an inner diameter “A” and an outer diameter “B”. In some embodiments, the inner diameter “A” is 0.6 times the outer diameter “B”. In some embodiments, the inner diameter “A” is 0.45 times the outer diameter “B”. In some embodiments, the inner diameter “A” is equal to the outer diameter “B”.

[0042] Spring 131 may be a compression spring or any other known type of spring commonly used to operate piston rod 121. In some embodiments, spring 131 may be wound along the outer peripheral surface of piston rod 121. In some embodiments, spring 131 may be a plurality of springs 131 equidistantly positioned along the outer peripheral surface of piston rod 121, such that the plurality of springs 131 are oriented along the longitudinal direction of pressure reducer assembly 100. Spring 131 may have a strength sufficient to operate piston rod 121. Spring 131 may have a length sufficient to produce the strength required to operate piston rod 121. The strength of spring 131 may not exceed the strength required to operate piston rod 121, because a greater strength of spring 131 would result in a larger installation space for spring 131, and thus an unnecessarily larger size of pressure reducer assembly 100.

[0043] Furthermore, the piston rod 121 may be concentric with the pressure reducer body 110 or the pressure reducer chamber 120. In some embodiments, depending on the operational feasibility of the pressure reducer assembly 100, the piston rod 121 may have any other orientation relative to the previously defined central axes X-X', Y-Y', and Z-Z'. The piston rod 121 of this disclosure is configured to oscillate substantially back and forth within the pressure reducer chamber 120. The back and forth movement of the piston rod 121 is due to a differential force experienced by the piston rod 121. The force experienced by the piston rod 121 is due to the spring 131 and the diaphragm 128 being operatively connected to the piston rod 121 within the pressure reducer chamber 120. The direction of movement of the piston rod 121 at any given moment is determined by the direction of the net force generated by the spring 131 and the diaphragm 128 on the piston rod 121. For example, when the net force is in the upstream direction, the piston rod 121 moves in the upstream direction because the force generated by the diaphragm 128 is greater than the force generated by the spring 131.

[0044] During the manufacture of the pressure regulator assembly 100, the constant output pressure generated by the pressure regulator assembly 100 can be adjusted by changing the initial distance or gap between the piston rod 121 and the seal 130. For example, the constant output pressure can be predetermined and preset during the manufacture of the pressure regulator assembly 100 according to the application requirements of the pressure regulator assembly 100. Some applications may require a constant output pressure of 4 bar, while other applications, such as drippers and nozzles for gardening operations, may require a constant output pressure of 1.5 bar. Therefore, the initial distance or gap between the piston rod 121 and the seal 130 is increased to produce a constant output pressure of 4 bar, while it is relatively decreased to produce a constant output pressure of 1.5 bar.

[0045] As described above, the diaphragm 128 is made of an elastic material, preferably silicone resin. Silicone resin is known to maintain flexibility and low compression set under extreme heat or cold. Silicone rubber is very durable and generally has good mechanical properties. Due to its durability, it is extremely reliable and trusted to maintain performance over long periods. The silicone diaphragm 128 can therefore be durable and cost-effective, as it may require less maintenance. Furthermore, the silicone diaphragm 128 provides good electrical insulation, is flame-retardant, and has low chemical reactivity.

[0046] like Figure 2A As shown, the diaphragm 128 is preferably circular or disc-shaped, having a central hole 150 with a center "Y" and a diameter "C" along the central axis W-W'. However, the diaphragm 128 may have any other shape with the central hole 150, depending on factors such as, but not limited to, the shape of the pressure reducer body 110 or the pressure reducer chamber 120. The diaphragm 128 is preferably and advantageously produced or manufactured using a stamping process. Stamping is a cost-effective, rapid process that requires little labor and machine operation. Furthermore, stamping reduces material waste, increases precision, and can be automated. In some embodiments of this disclosure, the diaphragm 128 can be produced by 1K or 2K injection molding.

[0047] Furthermore, in the preferred embodiment, such as Figure 2A and Figure 2BAs shown, the diaphragm 128 is designed such that the outer diameter "B" of the piston rod 121 is larger than the diameter "C" of the central bore 150 of the diaphragm 128. In some embodiments, the diameter "C" of the central bore 150 of the diaphragm 128 is equal to the outer diameter "B" of the piston rod 121. The diameter "C" of the central bore 150 of the diaphragm 128 is preferably smaller than the outer diameter "B" of the piston rod 121 so that radial stress is generated on the diaphragm 128 when the diaphragm 128 is pressed against the piston rod 121 by any means known in the art, causing the central axis X-X' to coincide with the central axis W-W'. However, the diameter "C" of the central bore 150 of the diaphragm 128 cannot be too small, so that the diaphragm 128 tears, ruptures, or breaks when it is pressed against the piston rod 121.

[0048] In some implementations, such as Figure 3A and Figure 3B As shown, the central axis W-W' coincides with the central axes X-X', Y-Y', and Z-Z'. In some embodiments, the central axis W-W' may coincide with one of the central axes X-X' and Y-Y' or Z-Z'. In some embodiments, the central axis W-W' may coincide with only the central axis X-X'.

[0049] Furthermore, the magnitude of the radial stress on the diaphragm 128 can depend on factors such as, but not limited to, the material properties of the diaphragm 128, the dimensions of the diaphragm 128, and the dimensions of the piston rod 121. The radial stress on the diaphragm 128 causes deformation of the diaphragm 128. The deformation shown in this disclosure is a conical deformation, such that the conical deformation of the diaphragm 128 leads to bistable buckling of the diaphragm 128 (e.g., Figure 3A and Figure 3B (As shown). The conical deformation also significantly and advantageously improves the stroke length of the diaphragm 128. In some embodiments, the stroke length of the diaphragm 128 is increased to 6 mm. In practical implementations of this disclosure, deformation can result in some other non-conical shapes of the diaphragm 128 without departing from the spirit of this disclosure.

[0050] In addition, such as Figure 2A , Figure 2B , Figure 3A and Figure 3BAs shown, the piston rod 121 includes a diaphragm support surface 160 in a direction perpendicular to the longitudinal direction of the pressure reducing body 110. The diaphragm support surface 160 prevents the diaphragm 128 from sliding away from the piston rod 121. The diaphragm support surface 160 allows the diaphragm 128 to be functionally stable. Furthermore, it transmits fluid forces to the piston rod 121, causing the piston rod 121 to be axially displaced. In some embodiments, an additional diaphragm support surface 170 is present, such that the diaphragm 128 is positioned between the diaphragm support surfaces 160 and 170 for better support. In some embodiments, the diaphragm support surfaces 160 and 170 are annular surfaces. In some embodiments, the diaphragm support surfaces 160 and 170 are a set of discrete surfaces on the periphery or circumference of the piston rod 121.

[0051] In some embodiments, the thickness "T" of the diaphragm 128 is equal to the spacing between the diaphragm support surfaces 160 and 170. In some embodiments, the thickness "T" of the diaphragm 128 is greater than the space between the diaphragm support surfaces 160 and 170. In some embodiments, the diaphragm support surfaces 160 and 170 may include protrusions or the like to provide better clamping and support for the diaphragm 128 sandwiched between the diaphragm support surfaces 160 and 170.

[0052] In some embodiments, the annular nose 171 is positioned adjacent to the diaphragm 128 to press the diaphragm downward when the spring 131 is extended, such that the spring 131 presses the diaphragm 128 upward in the opposite direction to the force transmitted by the annular nose 171 when pressing the diaphragm 128. This prevents the diaphragm 128 from slipping and can help hold the diaphragm 128 in place during operation of the pressure relief assembly 100. The annular nose 171 further includes a stop surface 172 that engages with the inclined surface 173 of the diaphragm support surface 170 when the spring 131 is extended. This engagement between the stop surface 172 and the inclined surface 173 prevents all force from being transmitted to the diaphragm 128. The engagement between the stop surface 172 and the inclined surface 173 further prevents damage to the diaphragm 128 and adhesion of the diaphragm 128 to the component 171.

[0053] Multiple ribs 180 spaced equally or unequally on the inner surface of the pressure reducer body 110 (e.g., ...) Figure 3A , Figure 3B and Figure 4 (As shown), this also prevents the diaphragm 128 from sliding. In some embodiments, the rib 180 may be integrally formed with the pressure reducer body 110. In some embodiments, the rib 180 may be removably attached to the pressure reducer body 110 to facilitate maintenance of the pressure reducer body 110.

[0054] Continue to refer to Figure 1 , Figure 3A, Figure 3B and Figure 4 The pressure reducer body 110 includes a first threaded portion 112 on its outer surface facing the direction opposite to the pressure reducer chamber 120. The first threaded portion 112 can be used to connect the pressure reducer body 110 to other accessories of the pressure reducer assembly 100. The pressure reducer body 110 also includes a pressure compensation port 114. The pressure compensation port 114 ensures unrestricted movement of the piston rod 121. When the piston rod 121 moves upstream of the fluid flow in the pressure reducer assembly 100, the pressure compensation port 114 allows the release of air pressure generated in the pressure reducer chamber 120. When the piston rod 121 moves upstream of the fluid flow in the pressure reducer assembly 100, the pressure compensation port 114 allows air to escape from the pressure reducer chamber 120. Conversely, when the piston rod 121 moves downstream of the fluid flow in the pressure reducer assembly 100, the pressure compensation port 114 allows the suction of surrounding air (outside the pressure reducer assembly 100).

[0055] In some embodiments, the pressure compensation hole 114 is a circular hole. The hole is preferably circular because it is easier to drill a circular hole. Furthermore, it essentially prevents material waste compared to manufacturing or producing holes of other shapes. However, the hole can have any other suitable shape without limiting the scope of this disclosure.

[0056] In some embodiments of this disclosure, the pressure compensation orifice 114 may be a channel extending at least partially along the length of the pressure reducer body 110. This channel provides a relatively large area for fluid ventilation during operation of the pressure reducer assembly 100. Therefore, even if the channel is partially blocked due to unforeseen or uncontrollable external factors or disturbances, fluid ventilation is still sufficient to facilitate unobstructed operation of the pressure reducer assembly 100. Furthermore, the channel may be a straight channel, a zigzag channel, or a channel with any other configuration, without limiting the scope of this disclosure.

[0057] In some embodiments, a sealing element 133 is used to seal and isolate air in the pressure regulator chamber 120 surrounding the spring-operated piston rod 121 from the valve 129. The sealing element 133 prevents air in the pressure regulator chamber 120 from mixing with fluid introduced into the pressure regulator assembly 100 via the inlet section 122. The sealing element 133 may be an O-ring or any other commonly available sealing element known in the art, without limiting the scope of this disclosure.

[0058] Furthermore, flange 132 is sealingly connected to pressure regulator body 110, preventing fluid backflow through outlet section 124. Flange 132 is concentric with pressure regulator body 110. Diaphragm 128 seals the connection between flange 132 and pressure regulator body 110. The boundary or end of diaphragm 128 abuts or presses between flange 132 and pressure regulator body 110, thereby providing a fluid-impermeable seal. This fluid-impermeable seal is a result of the contact pressure applied to diaphragm 128 due to the connection between flange 132 and pressure regulator body 110.

[0059] The seal prevents or disallows fluid backflow through the outlet section 124, thereby eliminating any potential leakage and improving the overall efficiency of the pressure regulator assembly 100. Furthermore, the multiple uses or applications of the diaphragm 128 mean that the seal does not require a separate sealing element such as an O-ring. Therefore, the pressure regulator assembly 100 is easy to assemble with all its necessary parts or accessories, and a further advantage is lower manufacturing costs due to the fewer parts or materials required to assemble or manufacture the pressure regulator assembly 100. Additionally, the reduced number of parts also lowers pressure regulator maintenance costs. Moreover, the seal prevents air from entering the outlet section 124, thereby preventing air drawn in from the pressure compensation port 114 from mixing with the fluid (such as a liquid).

[0060] Flange 132 has a second threaded portion 134 that is complementary to the first threaded portion 112, such that the pressure reducer body 110 and flange 132 are threadedly connected to each other via the first threaded portion 112 and the second threaded portion 134. However, in some embodiments of this disclosure, flange 132 may be attached to pressure reducer body 110 by any other suitable means (e.g., using an adhesive) without limiting the scope of this disclosure.

[0061] The flange 132 also includes a third threaded portion 136. The third threaded portion 136 is formed on the outer surface of the flange 132, opposite to the second threaded portion 134 formed on the inner surface of the flange 132. The third threaded portion 136 faces the pressure reducer body 110, while the second threaded portion 134 is opposite to the pressure reducer body 110 in the opposite direction.

[0062] The second threaded portion 134 connects the flange 132 to the pressure reducer body 110, while the third threaded portion 136 connects the flange 132 to the connector 138 (or fitting 138). The connector 138 completes the pressure reducer assembly 100 and allows fluid with reduced pressure to be transported for various domestic and industrial applications. The connection between the flange 132 and the connector 138 is a threaded connection due to the threaded engagement of the third threaded portion 136 and the threaded portion 140 of the connector 138. However, in some embodiments, the connection between the flange 132 and the connector 138 may be due to any other connection method known and understood in the relevant art.

[0063] In operation, fluid from a fluid source enters the pressure regulator assembly 100 at high pressure from inlet section 122. The fluid is filtered using filter element 125 before reaching valve 129. Valve 129 selectively allows fluid to pass toward a spring-operated hollow piston rod 121. Fluid from piston rod 121 flows outward toward flange 132 and ultimately to connector 138 for use in various domestic and industrial applications.

[0064] The pressure of the high-pressure fluid from the fluid source is reduced by the oscillating motion of the piston rod 121, which is essentially within the pressure reducing chamber 120. The piston rod 121 oscillates to reduce the fluid pressure to a constant output pressure, temporarily preventing fluid supply from the inlet section 122 towards the outlet section 124. The piston rod 121 also prevents fluid supply by engaging a seal 130 with the valve 129, which can seal the piston rod 121 axially or radially to prevent fluid from entering the piston rod 121.

[0065] When the piston rod 121 is pressed upstream of the fluid flow by the diaphragm 128 against the spring force, it temporarily blocks the supply of fluid from the inlet section 122. Furthermore, as the fluid presses against the diaphragm 128, it may also lose some energy, causing the diaphragm to further press against the piston rod 121, moving it upstream of the fluid flow. This reduces the high fluid pressure to the final output pressure.

[0066] Furthermore, when the fluid pressure near the output section 124 decreases to its final value, the spring 131 can overcome the force of the diaphragm 128, causing the piston rod 121 to move downstream toward its initial position. As discussed above, the pressure compensation orifice 114 assists in the oscillating motion of the piston rod 121.

[0067] Therefore, this disclosure provides an improved diaphragm design for a pressure reducing device assembly 100. The diaphragm 128 advantageously includes a central bore 150 with a diameter “C” smaller than the outer diameter “B” of the piston rod 121, such that when the diaphragm 128 is pressed against the piston rod 121, the diaphragm 128 deforms due to radial stress. This deformation of the diaphragm 128 significantly improves the stroke length of the diaphragm 128.

[0068] Preferred embodiments and examples of the invention have been disclosed in the accompanying drawings and description, and although specific terminology has been used, it is used in a general and descriptive sense only and not to limit the scope of the invention as set forth in the appended claims.

[0069] Component list

[0070] 100 pressure reducer assembly

[0071] 110 pressure reducer body

[0072] 112 First thread section

[0073] 114 Pressure Compensation Hole

[0074] 120 pressure reducing chamber

[0075] 121 Piston Rod

[0076] 122 entrance section

[0077] 123 threaded section

[0078] 124 Exit Section

[0079] 125 filter element

[0080] 126 connector

[0081] 127 threaded portion

[0082] 128 diaphragm

[0083] 129 valve

[0084] 130 seal

[0085] 131 spring

[0086] 132 flange

[0087] 133 sealing element

[0088] 134 Second thread section

[0089] 136 Third thread section

[0090] 138 connector / connector

[0091] 140 threaded section

[0092] 150 center hole

[0093] 160, 170 diaphragm support surface

[0094] 171 Nose

[0095] 172 Stop surface

[0096] 173 Inclined Surface

[0097] 180 ribs

[0098] AInner diameter

[0099] B outer diameter

[0100] C diameter

[0101] X Center

[0102] Y Center

[0103] Thickness T

[0104] X-X' central axis

[0105] Y-Y' central axis

[0106] Z-Z' central axis

[0107] W-W' central axis

Claims

1. A pressure reducer assembly (100), comprising: A pressure reducer body (110) defines at least one pressure reducer chamber (120) along the central axis of the pressure reducer body, the pressure reducer chamber (120) comprising: An inlet section (122) and an outlet section (124) are fluidly connected to the inlet section (122), such that the inlet section (122) and the outlet section (124) allow fluid to enter and exit, respectively. The spring-operated hollow piston rod (121) has a cylindrical inner circumferential surface including an inner diameter (A) and a cylindrical outer circumferential surface including an outer diameter (B) along the center axis of the pressure reducing device body; and A diaphragm (128), made of an elastic material and adapted to be operatively coupled to the piston rod (121), wherein the diaphragm (128) has a central hole (150) having a center and a diameter (C) along the central axis of the central hole. Its features are: In the uninstalled state, the outer diameter (B) of the piston rod (121) is larger than the diameter (C) of the central hole (150) of the diaphragm (128). In the installed state, the outer diameter (B) of the piston rod (121) is the same as the diameter (C) of the central hole (150) of the diaphragm (128); The diaphragm (128) is assembled on the piston rod (121) such that the central axis of the pressure reducing device body coincides with the central axis of the central hole. The radial stress causes deformation of the diaphragm (128), which is a conical deformation.

2. The pressure reducer assembly (100) according to claim 1, characterized in that, In the uninstalled state, the diameter (C) of the central hole (150) of the diaphragm (128) is equal to the inner diameter (A) of the piston rod (121).

3. The pressure reducer assembly (100) according to claim 1 or 2, characterized in that, The diaphragm (128) is made of silicone resin.

4. The pressure reducer assembly (100) according to claim 1, characterized in that, The diaphragm (128) is formed by stamping.

5. The pressure reducer assembly (100) according to claim 1, characterized in that, The piston rod (121) includes a diaphragm support surface (160).

6. The pressure reducer assembly (100) according to claim 1, characterized in that, The annular nose (171) is configured to be adjacent to the diaphragm (128) so that when the spring (131) is in the extended state, the diaphragm (128) is pressed in a direction opposite to the direction of the force transmitted by the annular nose (171) when the diaphragm (128) is pressed.

7. The pressure reducer assembly (100) according to claim 6, characterized in that, The annular nose (171) includes a stop surface (172) that engages with the inclined surface (173) of an additional diaphragm support surface (170) when the spring (131) is in the extended state.

Images