TECHNICAL FIELD

The present disclosure relates to a pressure reducer. More specifically, the present disclosure relates to an improved design of the pressure reducer, which allows efficient working of the pressure reducer.

BACKGROUND

Pressure reducers are found in many common domestic and industrial applications. For example, pressure reducers are used in gas grills to regulate propane, in home heating furnaces to regulate natural gases, in medical and dental equipment to regulate oxygen and anesthesia gases, in pneumatic automation systems to regulate compressed air, in engines to regulate fuel and in gardening systems to regulate irrigation among other applications. As this partial list demonstrates there are numerous applications for pressure reducers yet, in each of them, the pressure reducers provide the same function. The pressure reducers reduce a supply (or inlet) pressure to a lower outlet pressure and work to maintain this outlet pressure despite fluctuations in the inlet pressure. The reduction of the inlet pressure to the lower outlet pressure is the key characteristic of the pressure reducers.

The pressure reducer includes a spring-operated hollow piston rod, a diaphragm operatively coupled with the piston rod, a valve, and a sealing element disposed between the piston rod and the valve in a pressure reducer chamber along an axial direction of the pressure reducer. The valve opens and closes due to the rocking motion of the piston rod in the axial direction in the pressure reducer chamber. The valve closes when the piston rod contacts a planar sealing surface of the sealing element. However, during contact between the piston rod and the sealing element with such an arrangement of the pressure reducer, vibrations or pulsations often occur and potentially result in an unwanted noise, leakage and drop in overall efficiency of the pressure reducer.

A pressure reducer is provided in United States patent 10,906,052 (hereinafter referred to as ’052 reference). The ’052 reference provides a pressure regulator that includes a housing having an inlet cap with an inlet flow passage and an outlet cap with an outlet flow passage. A plunger is reciprocally mounted in the housing. A stationary regulator valve seat is disposed between the inlet flow passage and an inlet to the plunger. The plunger is sealed when moved to contact with the regulator valve seat to momentarily block the inlet flow. However, there is still a need for a simple and improved pressure reducer design that may improve the overall efficiency of the pressure reducer and substantially reduce or eliminate the drawbacks such as vibrations, among others, as discussed above.

A further pressure regulator is disclosed in US patent US 5,257,646 A (hereinafter referred to as ‘646 reference). The ‘646 reference discloses a flow regulator of the flow-through type, with an inlet provided at one end of an upstream section, and an outlet provided at a distal end of a downstream section. Within the upstream section of the regulator housing a replaceable, plastic regulator seat having a conical center portion and an annular seat surface, is mounted. A regulator plunger slides or reciprocates within a housing of the flow regulator. One end of the plunger is formed with a tapered edge to insure precise contact with the seat surface. The plunger is slidable within the flow regulator from a first open position to a second closed position where the lower edge of the plunger is seated on the seat surface. Further, the flow regulator comprises a flexible diaphragm. At all times, the upstream end of the chamber is sealed by the diaphragm. In the first open position, fluid flows through the regulator from the inlet section towards the outlet section around the seat and through the plunger and the outlet section. Therefore, the ‘646 reference unambiguously discloses an axial sealing of the lower edge of the plunger with the seat surface of the regulator seat. However, there is still a need for a simple and improved pressure reducer design that may improve the overall efficiency of the pressure reducer and substantially reduce or eliminate the drawbacks such as vibrations, among others, as discussed above.

SUMMARY

In view of the above, it is an objective of the present invention to solve or at least reduce the drawbacks discussed above. The objective is at least partially achieved by a pressure reducer for reducing a fluid pressure. The pressure reducer 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 such that the inlet section and the outlet section allow inlet and outlet of the fluid respectively. The pressure reducer chamber further includes a spring-operated piston rod, a sealing component operatively coupled with the piston rod in the pressure reducer chamber for preventing fluid in the outlet section from leaking back to the pressure reducer chamber, and a valve. The valve opens and closes due to rocking motion of the piston rod, and is coupled to the inlet section of the pressure reducer chamber. Further, a sealing element is disposed between the valve and the piston rod, wherein the piston rod is configured to stop a supply of fluid by engagement with the sealing element of the valve. The pressure reducer is characterized in that the valve defines a sealing seat for the sealing element, wherein the sealing element rests upon the sealing seat, and, when the piston rod stops the supply of fluid, the piston rod is sealed radially by the sealing element to prevent the fluid from entering the piston rod.

Thus, the present disclosure provides an improved pressure reducer that is simple in construction and easy to install. By sealing the piston rod radially an improved sealing over a mere axis sealing as known from the state of art is achieved. The pressure reducer with its novel design slowly reduces volume of fluid from the inlet section towards zero.

According to an embodiment of the present disclosure, the at least one of the sealing seat and the sealing element has a non-uniform geometry such that the piston rod is adapted to be sealed in a phased manner. The resulting slow reduction in flow volume prevents pressure shocks, and vibrations in the pressure reducer thereby improving the efficiency and service life of the pressure reducer.

According to an embodiment of the present disclosure, a sealing edge of the piston rod contacting the sealing element is a sharp edge. The sharp edges of the piston rod may reduce noise in an operating state of the pressure reducer.

According to an embodiment of the present disclosure, the sealing edge of the piston rod contacting the sealing element is a blunt edge. The blunt edge of the piston rod may avoid the damaging of the sealing element due to its circular profile when the sealing edge contacts or engages with the sealing element. Further, the blunt edge of the piston rod may avoid or at least reduce turbulences of the fluid flowing through the pressure reducer.

According to an embodiment of the present disclosure, the sealing edge has a non-uniform geometry. The non-uniform geometry of the sealing edge allows for gradual sealing of the piston rod there by preventing vibrations in the pressure reducer while it is operational.

According to an embodiment of the present disclosure, the valve is threadedly engaged to the pressure reducer body. The valve may be easily and conveniently engaged with the pressure reducer body. Further, the threaded engagement allows for easy displacement of the valve along the longitudinal direction of the pressure reducer as per application requirements of the pressure reducer.

According to an embodiment of the present disclosure, the pressure reducer generates a constant output pressure of 4 bars. Further, in some embodiments, the pressure reducer generates a constant output pressure of 1.5 bars. The constant output pressure may be pre-determined and preset during the manufacturing of the pressure reducer according to the application requirements of the pressure reducer. For example, the constant output pressure of 1.5 bars is well suited and optimal for the operation of drip heads and spray nozzles used for gardening operations.

According to an embodiment of the present disclosure, the pressure reducer is used for drip-irrigation. The pressure reducer of the present disclosure finds its application with the gardening operations such as, but not limited to, dripirrigation. However, the pressure reducer of the present disclosure is not restricted with its application area. The pressure reducer may conveniently and efficiently be used for any domestic or industrial application.

According to an embodiment of the present disclosure, the sealing component is a diaphragm. The diaphragm communicates an excess fluid pressure at the outlet section to the piston rod for downward stroke of the piston rod. Further, the diaphragm allows the sealing of the coupling between the flange and the pressure reducer body. The multiple usage or application of the diaphragm means no separate sealing elements such as O-rings are required for the sealing. Hence, the pressure reducer is easy to assemble with all its necessary components or accessories with further advantage of lower manufacturing expenses due to less components or material required for the assembly or manufacturing of the pressure reducer.

Other features and aspects of this invention will be apparent from the following description and the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention will be described in more detail with reference to the enclosed drawings, wherein:

FIG. 1 shows a perspective view of a pressure reducer assembly, in accordance with an aspect of the present disclosure;

FIG. 2 shows a cross-section view of a pressure reducer assembly, in accordance with an aspect of the present disclosure;

FIG. 3A shows a cross-section view of a valve assembly, in accordance with an aspect of the present disclosure;

FIG. 3B shows a perspective view of a valve and a sealing element, in accordance with an aspect of the present disclosure;

FIG. 3C shows a perspective view of a valve assembly, in accordance with an aspect of the present disclosure;

FIG. 4 shows a cross-section view of a pressure reducer, in accordance with an aspect of the present disclosure;

FIGS. 5A-C show various stages in gradual sealing of a piston rod, in accordance with an aspect of the present disclosure;

FIGS. 6A-E show various non-uniform geometries for a sealing seat, in accordance with an aspect of the present disclosure; and

FIGS. 7A-B show various non-uniform geometries for a sealing element, in accordance with an aspect of the present disclosure. DESCRIPTION OF EMBODIMENTS

The present invention will be described more fully hereinafter with reference to the accompanying drawings, in which example embodiments of the invention incorporating one or more aspects of the present invention are shown. This invention may, however, 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 present invention may be utilized in other embodiments and even other types of structures and/or methods. In the drawings, like numbers refer to like elements.

Certain terminology is used herein for convenience only and is not to be taken as a limitation on the invention. For example, "upper", "lower", "front", "rear", "side", "longitudinal", "lateral", "transverse", "upwards", "downwards", "forward", "backward", "sideward", "left," "right," "horizontal," "vertical," "upward", "inner", "outer", "inward", "outward", "top", "bottom", "higher", "above", "below", "central", "middle", "intermediate", "between", "end", "adjacent", "proximate", "near", "distal", "remote", "radial", "circumferential", or the like, merely describe the configuration shown in the Figures. Indeed, the components may be oriented in any direction and the terminology, therefore, should be understood as encompassing such variations unless specified otherwise.

FIG. 1 illustrates a pressure reducer 100. The pressure reducer 100 of the present disclosure is used for reducing a fluid pressure of the fluid intended to be used for drip-irrigation or other gardening operations. However, the pressure reducer 100 of the present disclosure is not restricted with its application area. The pressure reducer 100 may conveniently and efficiently be used for any other domestic or industrial applications.

Further, the fluid used with the pressure reducer 100 may be a liquid (say water) or a gas (say air) depending on the application requirement of the pressure reducer 100. The fluid may selectively be provided by a fluid source (not shown) at a pressure equal to more than the output pressure requirements of the application for which the pressure reducer 100 is used.

The fluid source may advantageously be provided with a valve such as to regulate the outflow of the fluid from the fluid source. Further, the fluid source may be provided with an automatic operatable accessory that may automatically regulate the outflow of the fluid from the fluid source. For example, the fluid source may be provided with a watering computer when the fluid is water. The watering computer may allow and regulate outflow of the water from the fluid source (or water source) depending upon the time of the day, preset water outflow timings, among other factors.

The fluid source may be fluidly coupled to the pressure reducer 100 via a hose or any other means commonly known and understood in the related art without limiting the scope of the present disclosure. In some embodiments, the fluid source may be fluidly coupled to a plurality of pressure reducers 100 by way of fluid distributors (commonly available in the related art).

The pressure reducer 100, as illustrated in FIGS. 1 and 2, includes a pressure reducer body 110. The pressure reducer body 110 of the present disclosure is a cylindrical body having a central axis X-X’ along a longitudinal direction of the pressure reducer 100. However, in actual implementation of the present disclosure, the pressure reducer body 110 may have any other shape without restricting the scope of the present disclosure. The pressure reducer body 110 may be made of brass, plastic, and aluminum. Various grades of stainless steel (such as 303, 304, and 316) may also be used for the manufacture of the pressure reducer body 110. However, any other material available to handle various fluids and operating environments may be employed for making or manufacturing the pressure reducer body 110. Further, any suitable manufacturing process may be employed for manufacturing of the pressure reducer body 110 without restricting the scope of the present disclosure.

The pressure reducer body 110 defines at least one pressure reducer chamber 120 along the central axis X-X’. The pressure reducer chamber 120 includes an inlet section 122 and an outlet section 124 fluidly coupled with the inlet section 122 such that the inlet section 122 and the outlet section 124 allow inlet and outlet of the fluid 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, as shown in FIG. 2, the central axes Y-Y’, Z-Z’ and X-X’ coincide with each other along the longitudinal direction of the pressure reducer 100. In some embodiments, the central axes Y-Y’, Z-Z’ and X-X’ may be parallel to each other but may not necessarily coincide with each other. In some embodiments, the central axes Y-Y’, Z-Z’ and the X-X’ may have any other angular orientation with respect to each other or with respect to the longitudinal direction of the pressure reducer 100 without restricting the scope of the present disclosure in any manner.

The inlet section 122 is fluidly coupled to the fluid source via a coupling nipple 126, as shown in FIGS. 1 and 2. The coupling nipple 126 may advantageously be designed in a manner such that the coupling nipple 126 selectively allows passage of fluid therethrough (received from the fluid source) only when it is fluidly coupled with the inlet section 122 of the pressure reducer 100. Such a design of the coupling nipple 126 may substantially prevent fluid leakages when the pressure reducer 100 is not operational or not in use. In some embodiments, the inlet section 122 may be sealingly coupled to the coupling nipple 126. The sealing may be provided by a sealing gasket, O-ring, or any other known and easily available sealing means (or sealing element).

The inlet section 122 further includes a threaded portion 123 such that the threaded portion 123 threadedly engages with a complimentary threaded portion 127 of the coupling nipple 126. Thus, in the preferred embodiment of the present disclosure, the inlet section 122, and the coupling nipple 126 are threadedly engaged or coupled with each other. However, in actual implementation of the present disclosure, the fluid coupling between the inlet section 122 and the coupling nipple 126 may be accomplished by any suitable means known and understood in the related art.

In the preferred embodiment of the present disclosure, as illustrated in FIG. 2, the inlet section 122 further includes a filter element 125. The filter element 125 may be operatively coupled to the inlet section 122 such that the filter element 125 filters the fluid received from the fluid source before it enters the pressure reducer chamber 120. The filter element 125 prevents clogging of the inlet section 122 and thereby promotes smooth operations of the pressure reducer 100. The filter element 125 may be coupled to the inlet section 122 by any means known in the related art. For example, the filter element 125 may be glued to the inlet section.

Further, the filter element 125 may have any shape, size, and type as per the application requirements. In some embodiments, the filter element 125 may be a surface filter made of closely woven fabric or treated paper with a uniform pore size. Fluid from the fluid source flows through the pores of the filter element 125 and contaminants are stopped on the filter element surface. In some embodiments, the filter element 125 may be a depth filter made of layers of fabric or fibers, which provide many tortuous paths for the fluid to flow through. The pores or passages are larger than the rated size of the filter element 125 for particles to be retained in the depth of the media rather than on the surface. In some embodiments, the filter element 125 may be of 5-micron, woven mesh, micronic, porous metal, or magnetic type. The micronic and 5-micron elements have non-cleanable filter media and may be disposed of when they are removed whereas the porous metal, woven mesh and magnetic filter elements are designed to be cleaned and reused.

Further, as illustrated in FIG. 2, the inlet section 122 of the pressure reducer chamber 120 includes a valve 129. The valve 29 may be made from plastic or any other suitable valve material traditionally used in the related art. The valve 129 selectively allows the fluid from the fluid source to pass through the pressure reducer chamber 120. The valve 129 selectively allows and disallows passage of fluid via the inlet section 122. The valve 129 selectively allows the passage of fluid to the outlet section 124 such as to maintain constant output pressure of the pressure reducer 100.

The valve 129 is located downstream of the filter element 125 in the direction of the fluid flow. In some embodiments, the valve 129 may be located inside the filter element 125. In some embodiments, the valve 129 may be at least partially located in the filter element. The location of the valve 129 relative to the filter element 125 is such that the filter element prevents contamination of the valve. The filter element 125 prevents valve 129 from exposure to foreign elements (mixed with the fluid received from the fluid source) to improve the longevity and service life of the valve 129.

The valve 129 may be coupled to the inlet section 122 of the pressure reducer body 110 or the pressure reducer chamber 120 by any suitable means known in the art. However, in the preferred embodiment, the valve 129 is coupled to the pressure reducer body 110 in a form- fitting form. The valve 129 is screwed or threaded into the inlet section 122 of the pressure reducer chamber 120. The valve 129 is threadedly engaged to the pressure reducer body 110. The valve 129 (as shown in FIGS. 3A-C) includes a fourth threaded portion 142 and the inlet 122 of the pressure chamber 120 includes a fifth threaded portion 143 such that the fourth threaded portion 142 and the fifth threaded portion 143 have the same thread pitch. The valve 129 is screwed or threaded into the inlet section 122 by virtue of the fourth threaded portion 142 and the fifth threaded portion 143.

The screw or threaded coupling between the valve 129 and the inlet section 122 allows for movement of the valve 129 relative to the inlet section along the longitudinal direction of the pressure reducer 100 as per the application requirement of the pressure reducer 100. The movement of the valve 129 along the longitudinal direction of the pressure reducer 100 may also help in adjusting the constant output pressure generated by the pressure reducer 100.

In some embodiments, the valve 129 may be along the central axis X-X’ of the pressure reducer body 110. In some embodiments, the valve 129 may be along the central axis Y-Y’ of the inlet section 122. In some embodiments, the valve 129 may be parallel to the central axis X-X’ of the pressure reducer body 110. In some embodiments, the valve 129 may be offset to the central axis X-X’ of the pressure reducer body 110. In some embodiments, the valve 129 may be at an angle to the central axis X-X’ of the pressure reducer body 110. In some embodiments, the valve 129 may be parallel to the central axis Y-Y’ of the inlet section 122. In some embodiments, the valve 129 may be offset to the central axis Y-Y’ of the inlet section 122. In some embodiments, the valve 129 may be at an angle to the central axis Y-Y’ of the inlet section 122. The valve 129 may have any suitable orientation relative to the longitudinal direction of the pressure reducer 100 without restricting the scope of the present disclosure in any manner.

The valve 129, as illustrated in FIGS. 2, 3A, 3B and 3C, defines a Ilshaped geometry. The U-shaped geometry may be used to conveniently adjust the valve 129 along the longitudinal direction of the pressure reducer 100. The U- shaped geometry may be used to adjust or move the valve 129 without tools for adjusting the constant output pressure generated by the pressure reducer 100.

The valve 129 defines a sealing seat 139. In some embodiments, the sealing seat 139 may be integrally formed with the valve 129. In some embodiments, the sealing seat 139 may be removably coupled with the valve 129. In some embodiments, the sealing seat 139 may be in the form of a groove. The sealing seat 139 in actual implementation of the present disclosure, may have any other form and arrangement without limiting the scope of the present disclosure in any manner.

The valve 129 further includes a sealing element 130. The sealing element 130 rests upon the sealing seat 139 defined by the valve 129. The sealing element 130 also moves with the movement of the valve 129. The sealing element 130 may be an O-ring or any other type of seal generally available in the related art. The sealing element 130 mounts on the sealing seat 139 of the valve 129. The sealing element 130 is further supported by a bracket 141 formed with the sealing seat 139. The bracket 141 prevents displacement of the sealing element 130 due to factors such as fluid force, among others. The bracket 141 at least partially covers or presses the sealing element 130 along the longitudinal direction of the pressure reducer 100 such that the sealing element 130 maintains its position in the pressure reducer throughout the working of the pressure reducer 100. In some embodiments, the bracket 141 may be conical in shape. However, in actual implementation, the bracket 141 may have any other shape without limiting the scope of the present disclosure in any manner. In some embodiments, the sealing element 130 may be a flat seal. However, in the preferred embodiment of the present disclosure, the sealing element 130 is a radial seal, i.e., providing sealing of the fluid in the radial direction.

With continued reference to FIG. 2, the pressure reducer chamber 120 further includes a spring-operated piston rod 121. The piston rod 121 is a hollow rod allowing passage of the fluid of which the pressure is to be reduced in the pressure reducer 100. The valve 129 opens and closes due to rocking motion of the piston rod 121 in the pressure reducer chamber 120. Further, the sealing element 130 as discussed above, is disposed between the valve 129 and the piston rod 121. A sealing edge 144 of the piston rod 121 contacting the sealing element 130 is sharp edge. The sharp edges of the piston rod 121 may reduce noise in an operating state of the pressure reducer 100. The sharp edges of the piston rod 121 may reduce noise during rocking motion of the piston rod 121. The sharp edges of the piston rod 121 may reduce noise at high inlet pressures and low fluid flow conditions. Further, the inside of the hollow piston rod 121 also provides reinforcement to the sealing element 130.

In some embodiments, the sealing edge 144 of the piston rod 121 contacting the sealing element 130 is a blunt edge. The blunt edge of the piston rod 121 may avoid the damaging of the sealing element 130 due to its circular profile when the sealing edge 144 contacts or engages with the sealing element 130. Further, the blunt edge of the piston rod 121 may avoid or at least reduce turbulences of the fluid flowing through the pressure reducer 100 which may result in an increase in the flow rate by up to 20%.

The spring 131 may be compression spring or any other known type of spring commonly used to operate the piston rod 121. In some embodiments, the spring 131 may wrap along the outer peripheral surface of the piston rodl21. In some embodiments, the spring 131 may be a plurality of springs 131 equidistantly positioned along the outer peripheral surface of the piston rod 121 such that the plurality of springs 131 are oriented along the longitudinal direction of the pressure reducer 100. The spring 131 may have strength enough to operate the piston rod 121. The spring 131 may have length enough to generate strength to operate the piston rod 121. The spring 131 may not have strength more than what is required to operate the piston rod 121 as the greater strength of the spring 131 leads to greater installation space of the spring 131 and thus an unnecessary increase in size of the pressure reducer 100.

Further, the piston rod 121 may be concentric with the pressure reducer body 110 or the pressure reducer chamber 120. In some embodiments, the piston rod 121 may have any other suitable orientation relative to the earlier defined central axes X-X’, Y-Y’ and Z-Z’ in accordance with the operational feasibility of the pressure reducer 100. The piston rod 121 of the present disclosure is configured to oscillate back and forth or exhibit the rocking motion substantially within the pressure reducer chamber 120. The back-and-forth motion of the piston rod 121 is due to differential force experienced by the piston rod 121. The piston rod 121 is forced to exhibit a downward stroke i.e., towards the inlet section 122 when the pressure at the outlet section 124 is more than required for the application for which the pressure reducer 100 is intended for use. Further, the piston rod 121 exhibits an upward stroke i.e., towards the outlet section 124 when the pressure at the outlet section 124 is equal to pressure required for the application for which the pressure reducer 100 is intended for use.

The fluid in the outlet section 124 is prevented from leaking back to the pressure reducer chamber 120 by a sealing component 128 operatively coupled with the piston rod 121 in the pressure reducer chamber 120. The sealing component 128 may be a lip seal, an O-ring, or any other known type of the sealing component 128 known and understood in the related art. However, in the preferred embodiment of the present disclosure, the sealing component 128 is a diaphragm 128. The diaphragm 128 communicates an excess fluid pressure at the outlet section 124 to the piston rod 121 for downward stroke of the piston rod 121. Further, for rest of the disclosure, the sealing component 128 will be treated as the diaphragm 128.

Referring to the differential force experienced by the piston rod 121, the force experienced by the piston rod 121 is due to the spring 131 and a diaphragm 128 operatively coupled with the piston rod 121 in the pressure reducer chamber 120. The direction of motion of the piston rod 121 at any particular time instant is governed by the direction of net force generated upon the piston rod 121 by the spring 131 and the diaphragm 128. For example, the piston rod 121 moves in upstream direction when the net force is in upstream direction due to higher magnitude of force generated by the diaphragm 128 relative to the force generated by the spring 131.

The constant output pressure generated by the pressure reducer 100 may be adjusted by varying the initial distance or the gap between the piston rod 121 and the sealing element 130 during the manufacturing of the pressure reducer 100. The gap may be varied without the help of the tool. For example, the constant output pressure may be pre-determined and preset during the manufacturing of the pressure reducer according to the application requirements of the pressure reducer 100. Some applications may demand the constant output pressure of 4 bars while other applications such as drip heads and spray nozzles used for gardening operations may demand the constant output pressure of 1.5 bars. Accordingly, the initial distance or the gap between the piston rod 121 and the sealing element 130 is increased for generating constant output pressure of 4 bars while it is comparatively reduced for generating constant output pressure of 1.5 bars.

With continued reference to FIG. 2, the pressure reducer body 110 includes a first threaded portion 112 on its outside surface facing opposite to the pressure reducer chamber 120. The first threaded portion 112 may be used for coupling the pressure reducer body 110 with other accessories of the pressure reducer 100. The pressure reducer body 110 further includes a pressure compensation hole 114 in the first threaded portion 112. The pressure compensation hole 114 ensures unrestricted mobility of the piston rod 121. The pressure compensation hole 114 allows release of air pressure generated in the pressure reducer chamber 120 when the piston rod 121 moves in the upstream direction of the fluid flow in the pressure reducer 100. The pressure compensation hole 114 allows air to escape from the pressure reducer chamber 120 when the piston rod 121 moves in the upstream direction of the fluid flow in the pressure reducer 100. Conversely, the pressure compensation hole 114 allows suction of the surrounding air (external to the pressure reducer 100) when the piston rod 121 moves in the downstream direction of the fluid flow in the pressure reducer 100.

In some embodiments, the pressure compensation hole 114 is a circular hole. The hole is preferably circular as it is easy to drill a circular hole. Further, it substantially prevents material wastage when compared with manufacturing or producing holes of other shapes. However, the hole may have any other suitable shape without restricting the scope of the present disclosure.

In some embodiments, air in the pressure reducer chamber 120 surrounding the spring-operated piston rod 121 is sealed from the valve 129 using a sealing element 133. The sealing element 133 prevents mixing of air in the pressure reducer chamber 120 with the fluid introduce in the pressure reducer 100 via the inlet section 122. The sealing element 133 may be O-ring or any other commonly available sealing element known in the art without restricting the scope of the present disclosure.

With reference to FIGS. 1 and 2, a flange 132 is sealingly coupled with the pressure reducer body 110 such that the sealing disallows the backflow of fluid past the outlet section 124. The flange 132 is concentric with the pressure reducer body 110. The diaphragm 128 (alternatively, the sealing component 128) seals the coupling between the flange 132 and the pressure reducer body 110. The boundaries or the extremities of the diaphragm 128 are abutted or pressed between the flange 132 and the pressure reducer body 110, thereby providing a fluid-tight sealing. The fluid tight sealing is the outcome of the contact pressure exerted on the diaphragm 128 due to the coupling between the flange 132 and the pressure reducer body 110.

The sealing prevents or disallows the backflow of fluid past the outlet section 124, thereby eliminating any possible leakage and improving the overall efficiency of the pressure reducer 100. Further, the multiple usage or application of the diaphragm 128 means no separate sealing elements such as O-rings are required for the sealing. Hence, the pressure reducer 100 is easy to assemble with all its necessary components or accessories with further advantage of lower manufacturing expenses due to less components or material required for the assembly or manufacturing of the pressure reducer 100. Further, due to less components, pressure reducer maintenance cost is also reduced. Furthermore, the sealing may prevent ingress of air in the outlet section 124, thereby preventing mixing of air drawn-in from the compensation hole with the fluid (say liquid).

The flange 132 has a second threaded portion 134 complimentary to the first threaded portion 112 such that the pressure reducer body 110 and the flange 132 are threadedly coupled to each other through the first and the second threaded portion 112, 134. The flange 132 further includes a third threaded portion 136. The third threaded portion 136 is formed on an outer surface of the flange 132 contrary to the second threaded portion 134, which is formed on an inner surface of the flange 132. The third threaded portion 136 faces the pressure reducer body 110 while the second threaded portion 134, faces away from the pressure reducer body 110 in an opposite direction.

The second threaded portion 134 couples the flange 132 with the pressure reducer body 110 whereas the third threaded portion 136 couples the flange 132 with a connector 138 (or a nipple 138). The connector 138 may complete the pressure reducer assembly and may allow the fluid with the reduced pressure to be transported for various domestic and industrial applications. The coupling between the flange 132 and the connector 138 is a threaded coupling due to threaded engagement of the third threaded portion 136 and a threaded portion 140 of the connector 138. However, in some embodiments, the coupling between the flange 132 and the connector 138 may be due to any other coupling means known and understood in the related art.

In some embodiments of the pressure reducer 100 of the present disclosure, as illustrated in FIG. 4, the sealing edge 144 of the piston rod 121 internally contacting the sealing element 130 has a non-uniform geometry. The non-uniform geometry of the sealing edge 144 of the piston rod 121 allows for gradual sealing of the piston rod 121 thereby preventing vibrations in the pressure reducer 100 while it is operational. The non-uniform geometry of the sealing edge 144 may correspond to an angular geometry or any other known geometry without limiting the scope of the present disclosure in any manner. The gradual or phased sealing of the piston rod 121 is illustrated in FIGS. 5A, 5B and 5C. A portion of the sealing edge 144 of the piston rod 121 at least partially surrounds or engages with the sealing element 130 before the remaining portion of the sealing edge 144. A portion of the sealing element 130 engages with the sealing edge 144 before the remaining portion of the sealing element 130.

Further, in some embodiments, as illustrated in FIGS. 6A-E and 7A-B, at least one of the sealing seat 139 and the sealing element 130 has an non-uniform geometry such that the piston rod 121 is adapted to be radially sealed in a phased manner. The sealing between the sealing element 130 and the piston rod 121 takes place gradually. The sealing seat 139 may be formed as slanted body, semidiagonal body, v shape recessed body, u shape recessed body, or roof-recess body as illustrated in FIGS. 6A-E respectively. Any shape of the sealing seat 139 may be selected amongst the described shapes, or any other non-uniform geometrical shapes to prevent shocks, vibrations during operation of the pressure reducer 100 among other benefits. Alternatively, the sealing element 130 may be formed as slanted or v shape body, or any other type of non-uniform or body as illustrated in FIGS. 7A-B respectively.

The piston rod 121 with the non-uniform geometry in conjunction with the at least one of the sealing seat 139 and the sealing element 130 with the non- uniform geometry improve the overall efficiency of the pressure reducer 100 by allowing gradual radial sealing between the piston rod 121 and the sealing element 130 such that the gradual radial sealing prevents or eliminates the shocks and the vibrations when the piston rod 121 momentarily stops the flow of the fluid from the inlet section 122 towards the outlet section 124. The non-uniform geometries of the piston rod 121, the sealing seat 139 or the sealing element 130 slowly reduces the volume flow towards zero such that there is no production or occurrence of the shock or vibration in the pressure reducer 100.

In operation, the fluid from the fluid source enters the pressure reducer 100 at high pressure from the inlet section 122. The fluid is filtered using filter element 125 before it reaches the valve 129. The valve 129 selectively allows the passage of the fluid towards the spring-operated hollow piston rod 121. The fluid from the piston rod 121 flows outwards towards the flange 132 and finally towards the connector 138 for use with various domestic and industrial applications.

The pressure of the high-pressure fluid from the fluid source is reduced by the oscillating or rocking motion of the piston rod 121 substantially within the pressure reducer chamber 120. The piston rod 121 oscillates to reduce the fluid pressure to the constant output pressure. The piston rod 121 momentarily stops or obstructs the supply of fluid from the inlet section 122 towards the outlet section 124. The piston rod 121 stops the supply of fluid by engagement with the sealing element 130 of the valve 129. The sealing element 130 radially seals the piston rod 121 to prevent the fluid from entering the piston rod 121.

The piston rod 121 momentarily stops the supply of fluid from the inlet section 122 when it is pressed by the diaphragm 128 against the spring force towards the upstream direction of the fluid flow. Further, the fluid may also lose some energy when the fluid presses the diaphragm 128 such that diaphragm further presses the piston rod 121 to make it move towards the upstream direction of the fluid flow. This way, the high fluid pressure is reduced to the final output pressure.

Further, when the fluid pressure near the output section 124 is reduced to the final value, the spring 131 may overcome the force of the diaphragm 128 such that the piston rod 121 moves in the downstream direction towards its original position. The oscillating movement of the piston rod 121 is assisted by the pressure compensation hole 114 as already discussed above.

Thus, the present disclosure provides an improved pressure reducer 100 that is simple in construction and easy to install. The pressure reducer 100 with its novel design slowly reduces volume of fluid from the inlet section 122 towards zero. The slow reduction in flow volume prevents pressure shocks, and vibrations in the pressure reducer 100 thereby improving the efficiency and service life of the pressure reducer 100.

In the drawings and specification, there have been disclosed preferred embodiments and examples of the invention and, although specific terms are employed, they are used in a generic and descriptive sense only and not for the purpose of limitation of the scope of the invention being set forth in the following claims.

LIST OF ELEMENTS

100 Pressure Reducer

110 Pressure Reducer Body

112 First Threaded Portion

114 Pressure Compensation Hole

120 Pressure Reducer Chamber

121 Piston Rod

122 Inlet Section

123 Threaded Portion

124 Outlet Section

125 Filter Element

126 Coupling Nipple

127 Threaded Portion

128 Sealing Component

129 Valve

130 Sealing Element

131 Spring

132 Flange

133 Sealing Element

134 Second Threaded Portion

136 Third Threaded Portion

138 Connector/N ipple

139 Sealing Seat

140 Threaded Portion

141 Bracket

142 Four Threaded Portion 143 Fifth Threaded Portion

144 Sealing Edge

X-X’ Central Axis

Y-Y’ Central Axis

Z-Z’ Central Axis