Patent Description:
A control valve may incorporate a device to break up a fluid stream into a plurality of flow paths to reduce noise resulting from the flowing fluid. These devices, known as fluid resistant devices, noise attenuators, or flow stabilizers, may be used to reduce high static-pressure of liquid or gas flow, preferably without the undesirable by-products of a high aerodynamic noise level (in the case of a compressible fluid, such as gas), or cavitation and erosion (in case of a liquid). Such devices may include spaced apart perforated plates, tubes, and braces. Some of these existing devices may suffer from one or more deficiencies, and thus further improvements in those devices may be desired. Examples of known control valves are: <CIT>, which discloses a process device for attenuating noise caused by a valve during the expansion of a fluid; <CIT>, which discloses a control valve arranged in a pipe; and <CIT>, which discloses a low vibration, low noise flow mechanism. <CIT> discloses a flow stabilizer according to the preamble of claim <NUM>.

The flow stabilizer of the invention is defined by the features of claim <NUM>. Further aspects of the invention are detailed in the dependent claims.

The features of this invention which are believed to be novel are set forth with particularity in the appended claims. The invention may be best understood by reference to the following description taken in conjunction with the accompanying drawings, in which like reference numerals identify like elements in the several Figures, in which:.

Although the following text sets forth a detailed description of one or more exemplary embodiments of the invention, it should be understood that the legal scope of the invention is defined by the words of the claims set forth at the end of this patent. The following detailed description is to be construed as exemplary only and does not describe every possible embodiment of the invention, as describing every possible embodiment would be impractical, if not impossible. Numerous alternative embodiments could be implemented, using either current technology or technology developed after the filing date of this patent, and such alternative embodiments would still fall within the scope of the claims defining the invention.

In <FIG>, a flow stabilizer <NUM>, which is disposed in an outlet passage <NUM> of a control valve <NUM> (and in this example, a rotary valve <NUM>) according to the present disclosure and generally relates to a device for attenuating the noise of fluid (preferably gas) in non-axisymmetric turbulent flow. The flow stabilizer <NUM> attenuates the noise of gas in the outlet passage <NUM> of the control valve <NUM>, and includes a plurality of nested shells disposed in an eccentric arrangement at a first or inlet end <NUM> of the flow stabilizer <NUM> as shown in <FIG>, and in a concentric arrangement at a second or outlet end <NUM> of the flow stabilizer <NUM> as shown in <FIG>. The flow stabilizer <NUM> extends from the eccentric arrangement to the concentric arrangement along an axis A of a main body or outer shell <NUM> of the flow stabilizer <NUM>. In the illustrated example, the axis A of the main body <NUM> (also referred herein as the "main body axis A") is coaxially aligned with the longitudinal axis of the outlet passage <NUM>. The flow stabilizer <NUM> is illustrated in the context of converting turbulent flow in the outlet passage <NUM> of the rotary valve <NUM>, however, in other examples, the flow stabilizer <NUM> may be disposed in a different type of control valve to attenuate noise through an outlet passage or through a conduit other than the outlet passage of the valve.

As shown in <FIG>, the flow stabilizer <NUM> includes a main body or outer shell <NUM> having an axis A, the first or inlet end <NUM>, and the second or outlet end <NUM>. As used herein, the first or inlet end <NUM> of the outer shell or main body <NUM> is also referred to as the first or inlet end <NUM> of the flow stabilizer <NUM> (<FIG>), and the second or outlet end <NUM> of the outer shell or main body <NUM> is also referred to as the second or outlet end <NUM> of the flow stabilizer <NUM> (<FIG>). The flow stabilizer <NUM> includes three nested shells-a first inner shell <NUM>, a second inner shell <NUM>, and a third inner shell <NUM>-at least partially if not entirely disposed (e.g., formed) within the outer shell or main body <NUM>. In other examples, however, the flow stabilizer <NUM> may include more or fewer nested shells. Preferably, the nested shells are perforated along their lengths to provide fluid communication between adjacent nested shells.

In <FIG>, the flow stabilizer <NUM> is illustrated partially cut along two vertical planes: a plane extending along axis A and a plane extending along an axis T, which is transverse to axis A. The general orientation of the flow stabilizer <NUM>, with respect to at least the location of the inlet end <NUM> and the outlet end <NUM>, is different than its orientation in <FIG>. In <FIG>, the first inner shell <NUM>, which is preferably a metallic shell, is disposed at least partially (if not entirely) within the main body <NUM> and is centered about, or includes, an axis B (also referred herein as the "first shell axis"), a first or inlet end <NUM>, and a second or outlet end <NUM>. The second inner shell <NUM>, which is also preferably a metallic shell, is disposed at least partially (if not entirely) within the main body <NUM> and at least partially (if not entirely) within the first shell <NUM>. The second shell <NUM> is centered about an axis C (also referred herein as the "second shell axis") and includes a first or inlet end <NUM> and a second or outlet end <NUM>. The third inner shell <NUM>, which is also preferably a metallic shell, is disposed at least partially (if not entirely) within the main body <NUM> and at least partially (if not entirely) within the second shell <NUM>. The third shell <NUM> is centered about an axis D (also referred herein as the "third shell axis") and includes a first or inlet end <NUM> and a second or outlet end <NUM>.

As shown in <FIG>, each of the first shell <NUM>, the second shell <NUM>, and the third shell <NUM> has a circular cross-sectional shape taken at any point along the axis A of the main body <NUM> between the first end <NUM> and the second end <NUM> of the flow stabilizer <NUM>, albeit each shell has a differently sized cross-sectional shape (e.g., the cross-sectional shape of the shell <NUM> is larger than the cross-sectional shape of the shell <NUM>).

In the illustrated example of <FIG>, the main body <NUM> has a cylindrical shape and the first, second, and third shells <NUM>, <NUM>, and <NUM> are entirely disposed within a main body interior area or portion <NUM> that is enclosed by a cylindrical internal surface <NUM> of the main body <NUM>. In other examples, however, the first, second, and/or third shells <NUM>, <NUM>, and <NUM> may only be partially disposed within the main body interior portion <NUM> or disposed in a different manner. In any case, the first, second, and third shells <NUM>, <NUM>, and <NUM> are generally disposed within the main body interior portion <NUM> in an angled or non-parallel configuration. More particularly, as illustrated in <FIG>, the shells <NUM>, <NUM>, and <NUM> are disposed so that the first shell axis B is angled relative (i.e., not parallel) to the main body axis A, the second shell axis C is angled relative (i.e., not parallel) to the main body axis A, and the third shell axis D is angled relative (i.e., not parallel) to the main body axis A. In this example, the first shell axis B is oriented at an angle relative to the main body axis A, the second shell axis C is oriented at a different angle relative to the main body axis A, and the third shell axis D is oriented at a different angle relative to the main body A. The angled orientation of each shell depends on the diameter of that particular shell and the length of the flow stabilizer <NUM> (i.e. distance from the inlet end <NUM> to the outlet end <NUM>). Thus, in this example, the shell axes B, C, and D are angled relative to one another so that the second shell axis C is also angled relative (i.e., not parallel) to the first shell axis B, and the third shell axis D is also angled relative (i.e., not parallel) to the second shell axis C. In other examples, however, two or more of the first shell axis B, the second shell axis C, and the third shell axis D may be oriented parallel to one another. Further, in other examples, one or two (but not all three) of the first shell axis B, the second shell axis C, and the third shell axis D may be oriented parallel to the main body axis A.

As a result, and as best shown in <FIG>, the inlet end <NUM> of the flow stabilizer <NUM> has an eccentric arrangement (the shells <NUM>, <NUM>, and <NUM> are eccentrically mounted within the main body <NUM> and one another at the inlet end <NUM>), and as best shown in <FIG> the outlet end <NUM> of the flow stabilizer <NUM> has a concentric arrangement (the shells <NUM>, <NUM>, and <NUM> are concentrically mounted within the main body <NUM> and one another at the outlet end <NUM>). Thus, when the inlet end <NUM> is arranged in the outlet passage <NUM> of the rotary valve <NUM>, as shown in <FIG>, the flow stabilizer <NUM> receives a non-axisymmetric fluid flow at the eccentrically arranged inlet end <NUM>, guides the fluid flow through a plurality of flow paths 80A-H of the flow stabilizer <NUM>, and delivers the flow through the concentrically arranged outlet end <NUM>. In other words, each shell <NUM>, <NUM>, and <NUM> is configured to transition from the eccentric arrangement at the first end <NUM> of the main body <NUM> to the concentric arrangement at the second end <NUM> of the main body <NUM>, thereby converting the fluid flow.

As shown in <FIG>, the non-parallel configuration of the shells <NUM>, <NUM>, and <NUM> (relative to the main body <NUM>) define a plurality of flow paths 80A, 80B, 80C, 80D, 80E, 80F, <NUM>, and <NUM>, where each flow path 80A-<NUM> slopes relative to the longitudinal, main body axis A as the flow stabilizer <NUM> extends from the inlet end <NUM> to the outlet end <NUM>. Each shell <NUM>, <NUM>, and <NUM> extending along its respective axis B, C, and D defines at least one linear flow path 80A-<NUM> with the adjacent shell <NUM>, <NUM>, and <NUM>. The flow paths 80A-<NUM> of the illustrated flow stabilizer <NUM> slope in a substantially linear manner relative to the main body axis A from a lower, inner surface <NUM> of the main body <NUM> toward an upper, inner surface <NUM> of the main body <NUM>. The flow paths 80A-<NUM> slope as the flow stabilizer <NUM> transitions from the eccentric arrangement at the first or inlet end <NUM> to the concentric arrangement at the second or outlet end <NUM>. In other words, incoming or upstream flow entering the flow paths 80A-<NUM> at the inlet <NUM> of the flow stabilizer <NUM> is different from outgoing or downstream flow exiting the flow paths 80A-<NUM> at the outlet <NUM> of the flow stabilizer <NUM>.

Specifically, and as illustrated in <FIG>, a first flow path 80D, which may be separated from or combined with an upper flow path <NUM>, is at least partially defined by the main body <NUM> and the first shell <NUM>. A second flow path 80C, which may be separated from or combined with an upper flow path 80F, is at least partially defined by the first shell <NUM> and the second shell <NUM>. A third flow path 80B, which may be separated from or combined with an upper flow path 80E, is at least partially defined by the second shell <NUM> and the third shell <NUM>. A fourth flow path 80A, which may be separated from or combined with an upper flow path <NUM> is at least partially defined by an interior surface of the third shell <NUM>. As shown in <FIG>, the flow paths 80D, 80C, 80B, and 80A are separate from their respective upper flow paths <NUM>, 80F, 80E, and <NUM> by a first brace <NUM> and a second brace <NUM>, which will be described in more detail below.

As shown in <FIG>, the flow paths 80A-<NUM> slope relative to the main body axis A from the lower, inner surface <NUM> of the main body <NUM> toward the upper, inner surface <NUM> of the main body <NUM>, such that the shells <NUM>, <NUM>, and <NUM> are spaced closer to one another at or adjacent the upper, inner surface <NUM> than at or adjacent the lower, inner surface <NUM> at the inlet end <NUM>. This sloped transition from eccentric to concentric arrangements helps reduce noise and vibration associated with control valves by reducing the level of turbulence entering the outlet passage <NUM> as well as eliminating direct excitation of the passage <NUM> by the non-axisymmetric flow discharging from the rotary valve <NUM>. In another example, the shells <NUM>, <NUM>, and <NUM> are nested and in contact with one another at the lower, inner surface <NUM> of the main body <NUM>. More particularly, and best shown in <FIG>, an outer surface of the first shell <NUM> is in line contact with an internal surface of the main body <NUM>. Likewise, an outer surface of the second shell <NUM> is in line contact with an inner surface of the first shell <NUM>, an outer surface of the third shell <NUM> is in line contact with an inner surface of the second shell <NUM>, and so on.

The flow stabilizer <NUM> includes a plurality of braces that separate or further define the plurality of flow paths 80A-H, beneficially provide structural support (e.g., rigidify, strengthen), and help maintain the orientation of the shells <NUM>, <NUM>, and <NUM> relative to the main body <NUM>. In this example, the flow stabilizer <NUM> includes a generally vertically extending brace <NUM> and a generally horizontally extending brace <NUM>. The generally vertically extending brace <NUM> connects the shells <NUM>, <NUM>, and <NUM> to the main body <NUM> (and one another) along or in the generally vertical direction, while the generally horizontally extending brace <NUM>, which is non-parallel (and in some cases perpendicular) to the brace <NUM>, connects the shells <NUM>, <NUM>, and <NUM> to the main body <NUM> (and one another) along or in the generally horizontal direction, relative to the orientation shown in the figures. The braces <NUM> and <NUM> may be integrally formed with the main body <NUM> and the first, second, and third shells <NUM>, <NUM>, and <NUM> during manufacturing. Alternatively, the braces <NUM> and <NUM> (as well as any other braces) may be separately formed and then welded or otherwise secured to the main body <NUM> and the first, second, and third shells <NUM>, <NUM>, and <NUM>. In other examples, the flow stabilizer <NUM> can include greater, fewer, and/or different braces. As an example, the brace <NUM> and/or the brace <NUM> may be formed of a plurality of smaller, interconnected braces or brace segments.

As shown in <FIG>, the shells <NUM>, <NUM>, and <NUM> are evenly spaced apart from one another in the concentric arrangement, however in other examples, the cross-sectional diameter of one or more shells <NUM>, <NUM>, and <NUM> may be increased or decreased to minimize or maximize the space between surrounding adjacent shells. In any event, the flow stabilizer <NUM> allows eccentricity at the inlet end <NUM> to be maximized while maintaining consistency with design for mechanical strength to withstand high forces involved in many applications. The concentric outlet <NUM> provides for a preferred fluid flow outlet path. The flow stabilizer <NUM> reduces the distance required for pipe flow to transition from eccentric to concentric flow.

In <FIG>, another example of a flow stabilizer <NUM> constructed in accordance with the teachings of the present disclosure is provided. For ease of reference, and to the extent possible, the same or similar components will retain the same reference numbers as outlined above with respect to the flow stabilizer <NUM> discussed above, although the reference numbers will be increased by <NUM>. The flow stabilizer <NUM> is similar to the flow stabilizer <NUM> described above in many respects, and may be used in a control valve <NUM> (such as the control valve <NUM> of <FIG>) in the same arrangement as the flow stabilizer <NUM>. However, unlike the flow stabilizer <NUM>, which has a plurality of flow paths that slope in a substantially linear manner, the flow stabilizer <NUM> define a plurality of flow paths 180A-<NUM> that are curved as the flow stabilizer <NUM> extends from an inlet end <NUM> to an outlet end <NUM>. Each shell <NUM>, <NUM>, and <NUM> extending along its respective axis defines at least one curved flow path 180A-<NUM> with the adjacent shell <NUM>, <NUM>, and <NUM>. The flow paths 180A-<NUM> of the illustrated flow stabilizer <NUM> slope in a curved manner relative to the main body axis from a lower, inner surface <NUM> of a main body <NUM> toward an upper, inner surface <NUM> of the main body <NUM>. The flow paths 180A-<NUM> slope as the flow stabilizer <NUM> transitions from the eccentric arrangement at the first or inlet end <NUM> to the concentric arrangement at the second or outlet end <NUM>.

Turning now to <FIG>, the fluid stabilizer <NUM> is disposed in the rotary valve <NUM> of <FIG>, and is depicted from a top view relative to the orientation of the rotary valve <NUM> shown in <FIG>. The rotary valve <NUM> of <FIG>, <FIG> includes, in relevant part, a valve body <NUM> having a chamber <NUM>, an upstream face surface <NUM>, a downstream face surface <NUM>, and a non-axisymmetric opening valve plug or control member <NUM> operated by stub shafts 72A and 72B journaled in the valve body <NUM>. The rotary valve <NUM> includes a seal <NUM> held in place by a seal ring <NUM>. The seal ring <NUM> is retained on the valve body <NUM> by suitable fasteners <NUM>, such as, for example, through bolts, cap screws, or other suitable means. The rotary valve <NUM> is positioned between a first flange <NUM> of a conduit (e.g., pipe) <NUM> and a second flange <NUM> of a conduit (e.g., pipe) <NUM>. In this example, the rotary valve <NUM> is clamped between the flanges <NUM> and <NUM> using fasteners <NUM>. The fasteners <NUM>, which are spaced circumferentially about the rotary valve <NUM>, can also clamp the flow stabilizer <NUM> in place. In preferred examples, the flow stabilizer <NUM> includes an annular flange <NUM> that is secured to an outermost surface of the main body <NUM> and, so positioned, can be clamped between the rotary valve <NUM> and the flange <NUM> via fasteners <NUM>.

Normally, the rotary valve <NUM> would be installed such that the outer surface of the plug <NUM> faces upstream (left in <FIG>) when it is in the closed position. While the rotary valve <NUM> may be installed in such manner, the rotary valve <NUM> is preferably installed in a reverse flow configuration, i.e., so that the outer surface of the rotary valve plug <NUM> faces downstream (right in <FIG>) when it is in the closed position. In either case, the flow stabilizer <NUM> described herein is arranged immediately downstream of the non-axisymmetric opening valve plug <NUM> so as to render the flow substantially axisymmetric and to attenuate the noise of fluid in turbulent flow. Moreover, in the illustrated example, the lower, inner surface <NUM> of the flow stabilizer <NUM> is arranged to receive fluid flow before the upper, inner surface <NUM> when the valve plug <NUM> is opened, as illustrated in <FIG>.

When the rotary valve plug <NUM> is closed, as shown in <FIG>, for example, fluid flow F will abut the inner surface of the rotary valve plug <NUM>. As shown in <FIG>, as the valve plug <NUM> opens to permit non-axisymmetric flow from the valve body <NUM>, fluid will pass through the bore in the seal ring <NUM> and enter the flow paths 80A-H formed by the main body <NUM> and the shells <NUM>, <NUM>, and <NUM> at the lower, inner surface <NUM> of the flow stabilizer. Eventually, the fluid will substantially fill each shell <NUM>, <NUM>, and <NUM> (and each of the flow paths 80A-<NUM>) from the lower, inner surface <NUM> to the upper, inner surface <NUM> of the flow stabilizer <NUM>, entering the smallest shell <NUM> first, so that by the time the fluid exits the flow stabilizer <NUM>, the main body <NUM> and the shells <NUM>, <NUM>, and <NUM> are substantially filled, and the fluid is converted to fully developed pipe flow (i.e., substantially axisymmetric flow). The noise of the fluid will be attenuated as the fluid spreads radially and passes through other shells <NUM>, <NUM>, and <NUM> as it flows axially from the inlet end <NUM> to the outlet end <NUM> of the flow stabilizer <NUM>. The smooth transition to axisymmetric flow in the conduit <NUM> downstream of the rotary valve <NUM> is at a reduced level of turbulence and thus, noise and system vibration are minimized for both gas and liquid systems. High velocity jets in the conduit <NUM> downstream of the rotary valve <NUM> are eliminated. The pressure gradient of the gas in adjacent shells is reduced, helping to reduce the turbulence of the fluid and hence, the noise and vibration caused in the downstream conduit <NUM>.

The flow stabilizer <NUM> can be installed in a different manner and yet still operate as intended. As an example, the flow stabilizer <NUM> can be mounted in a vertical pipe or at an angle. However, it is highly preferable that the flow stabilizer <NUM> be installed so that its smallest shell, in this example the third shell <NUM>, is aligned with the initial opening of the rotary valve <NUM> or the source of non-axisymmetric flow, so that initial flow from the opening is directed into the smallest shell <NUM>. The orientation of the flow stabilizer <NUM> relative to the valve plug <NUM> has been found to produce optimal results.

The walls of each of the shells and the walls of braces are perforated (as opposed to being solid), as best shown in another example of a flow stabilizer <NUM> constructed in accordance with the teachings of the present disclosure and depicted in <FIG>, not belonging to the claimed invention. The flow stabilizer <NUM> is disposed adjacent to a downstream surface face <NUM> of a valve body <NUM> and interior to a tailpiece <NUM> being immediately adjacent to a source of non-axisymmetric flow, for example a sharp turn or a rotary valve <NUM> (e.g., the rotary valve <NUM> of <FIG>), formed by the flow path of a control member <NUM>. For ease of reference, and to the extent possible, the same or similar components will retain the same reference numbers as outlined above with respect to the flow stabilizer <NUM> discussed above, although the reference numbers will be increased by <NUM>.

As illustrated, the flow stabilizer <NUM> may include five shells <NUM>, <NUM>, <NUM>, <NUM>, and <NUM>, and a plurality of braces <NUM> disposed between the shells <NUM>, <NUM>, <NUM>, <NUM>, and <NUM>. Each of the shells <NUM>, <NUM>, <NUM>, <NUM>, and <NUM> is perforated, i.e., has apertures <NUM> formed therein. As an example, apertures <NUM> formed in the shell <NUM> fluidly connects an inner surface 246B and an outer surface 246A of the shell <NUM>. Likewise, each of the braces <NUM> is perforated, i.e., has apertures <NUM> formed therein that fluidly connect two flow paths separated by the brace <NUM>. The apertures <NUM> and <NUM> may be uniform or varied and/or may be a variety of shapes (e.g., circular, triangular, diamond) and sizes. As an example, the apertures <NUM> and <NUM> may be about <NUM> (<NUM>/<NUM> inch) in diameter and up to <NUM> (<NUM>/<NUM> inch) in diameter for silencers where the diameter of the largest shell is approximately <NUM> (<NUM> inches). In tests to date, best results have been obtained with <NUM> (<NUM>/<NUM> inch) diameter apertures <NUM>, <NUM> and where the total open area is about forty percent (<NUM>%) of the outer surface area of a shell. For larger silencers, e.g., those having an approximately <NUM> inch outside diameter, thicker metal would be used for the shells and larger apertures <NUM>, <NUM>, e.g., apertures having a diameter of <NUM> (<NUM>/<NUM> inch) or even <NUM> (<NUM>/<NUM> inch), would be needed.

As illustrated, the flow stabilizer <NUM> includes a plurality of flow paths <NUM> that extend between a first end <NUM> and a second end <NUM>, and the apertures <NUM> and <NUM> fluidly connect adjacent flow paths <NUM>. For example, a first flow path <NUM> is at least partially defined by the main body <NUM>, the first shell <NUM>, and two different braces <NUM> dispsoed between the main body <NUM> and the first shell <NUM>. A second, different flow path 280I is at least partially defined by the third shell <NUM> and the fourth shell <NUM>. The flow path 280I is fluidly connected to adjacent flow paths <NUM> by way of apertures <NUM> in the third shell <NUM> and fourth shell <NUM>, as well as apertures <NUM> in the brace <NUM>.

Moreover, it will be appreciated that the location of the braces <NUM> relative to the shells <NUM>, <NUM>, <NUM>, <NUM>, and <NUM> may or may not be evenly dispersed to obtain a desired flow path between the shells. Additionally, the braces <NUM> are angled (or non-parallel) relative to each other, as illustrated in <FIG>, though in other examples, the braces may be parallel <NUM>, such as different brace segments of the brace <NUM> of <FIG>.

Turning now to <FIG>, not belonging to the claimed invention, another example of a flow stabilizer <NUM> constructed in accordance with the teachings of the present disclosure is provided. The flow stabilizer <NUM> operates in a similar manner as the flow stabilizers <NUM>, <NUM>, and <NUM> described above, but unlike the flow stabilizers <NUM>, <NUM>, and <NUM>, the flow stabilizer <NUM> does not include a main body. For ease of reference, and to the extent possible, the same or similar components will retain the same reference numbers as outlined above with respect to the flow stabilizer <NUM> and rotary valve <NUM> discussed above, although the reference numbers will be increased by <NUM>.

In <FIG>, the flow stabilizer <NUM> includes a plurality of braces <NUM> that may be directly connected to an interior wall <NUM> of a tailpiece <NUM> of a rotary valve <NUM> through welding or other means known in the art. Further, the flow stabilizer <NUM> may be directly formed and integral to the tailpiece <NUM> via additive manufacturing described in additional detail below.

In accordance with the teachings of the present disclosure, the shells should preferably have a characteristic length of at least <NUM> times the characteristic inlet bore dimension of a base (such as the base of seal ring <NUM> in <FIG>) containing the source of the non-axisymmetric flow. Best results are expected when the shells have a characteristic length of from <NUM> to <NUM> times the characteristic inlet bore dimension of the base. Normally, the seal ring <NUM> and the conduit <NUM> have the same cross-sectional configuration and the seal ring <NUM> has the same or a smaller diameter than the conduit <NUM>.

Further, while the flow stabilizers <NUM>, <NUM>, <NUM>, and <NUM> are described in connection with the rotary valve <NUM>, it will be understood that any of the flow stabilizers of the present disclosure can be used with other control valves and preferably other rotary valves, such as, for example, a segmented ball valve or a butterfly valve. For a butterfly valve, the flow stabilizer <NUM>, <NUM>, <NUM>, or <NUM> may, for example, be adapted to include two eccentric inlet ends and one concentric outlet end.

The flow stabilizers <NUM>, <NUM>, <NUM>, and <NUM> of the present disclosure are manufactured to effectively reduce turbulent flow downstream of a non-axisymmetric discharging valve and convert the non-axisymmetric flow to substantially axisymmetric flow, i.e., fully developed pipe flow. Additionally, the flow stabilizers <NUM>, <NUM>, <NUM>, and <NUM> of the present disclosure are easier and less costly to manufacture than conventional flow stabilizers.

More specifically, the flow stabilizers <NUM>, <NUM>, <NUM>, and <NUM> may be manufactured using additive manufacturing techniques. The additive manufacturing technique may be any additive manufacturing technique or process that builds three-dimensional objects by adding successive layers of material on a material. The additive manufacturing technique may be performed by any suitable machine or combination of machines. The additive manufacturing technique may typically involve or use a computer, three-dimensional modeling software (e.g., Computer Aided Design, or CAD, software), machine equipment, and layering material. Once a CAD model is produced, the machine equipment may read in data from the CAD file and layer or add successive layers of liquid, powder, sheet material (for example) in a layer-upon-layer fashion to fabricate a three-dimensional object. The additive manufacturing technique may include any of several techniques or processes, such as, for example, a stereolithography ("SLA") process, a fused deposition modeling ("FDM") process, multi-jet modeling ("MJM") process, a selective laser sintering ("SLS") process, an electronic beam additive manufacturing process, and an arc welding additive manufacturing process. In some embodiments, the additive manufacturing process may include a directed energy laser deposition process. Such a directed energy laser deposition process may be performed by a multi-axis computer-numerically-controlled ("CNC") lathe with directed energy laser deposition capabilities.

Claim 1:
A flow stabilizer (<NUM>, <NUM>, <NUM>, <NUM>) adapted to be disposed in an outlet passage (<NUM>) of a control valve (<NUM>, <NUM>, <NUM>), the flow stabilizer comprising:
a main body or outer shell (<NUM>, <NUM>, <NUM>, <NUM>), having a cylindrical inner surface and having a main body or outer shell axis (A) coaxially aligned with a longitudinal axis of the outlet passage (<NUM>), a first end (<NUM>, <NUM>, <NUM>, <NUM>), and a second end (<NUM>, <NUM>, <NUM>, <NUM>);
a first inner shell (<NUM>, <NUM>, <NUM>, <NUM>) disposed at least partially within the main body or outer shell, the first inner shell having an axis (B), a first end (<NUM>, <NUM>), and a second end (<NUM>), wherein the first inner shell has a circular cross-sectional shape from the first to the second end;
a second inner shell (<NUM>, <NUM>, <NUM>, <NUM>) disposed at least partially within the main body or outer shell and at least partially within the first inner shell, wherein the second inner shell has an axis (C), a first end and a second end, wherein the second inner shell has a circular cross-sectional shape from the first to the second end;
further comprising a plurality of flow paths (80A-H, 180A-H, <NUM>, <NUM>) extending between the first end of the main body or outer shell and the second end of the main body or outer shell, and wherein a first path (80D, <NUM>, 180D, <NUM>) of the plurality of flow paths is at least partially defined by the main body or outer shell and the first inner shell, and a second path (80C, 80F, 180C, 180F) of the plurality of flow paths is at least partially defined by the first inner shell and the second inner shell; and
further comprising a plurality of braces (<NUM>, <NUM>, <NUM>, <NUM>, <NUM>, <NUM>) separating the plurality of flow paths, wherein a first brace (<NUM>, <NUM>) of the plurality of braces connects the main body or outer shell and the first inner shell and a second brace (<NUM>, <NUM>) of the plurality of braces connects the first inner shell and the second inner shell, wherein the plurality of braces extend between the first end of the main body or outer shell and the second end of the main body or outer shell, characterised in that
the axis of the first inner shell is angled relative to the axis of the main body and the axis of the second inner shell is angled relative to the axis of the main body or outer shell.