JP6209531B2 - Shape optimized header and manufacturing method thereof - Google Patents

Description

BACKGROUND The present disclosure relates to a header having an optimized shape and a manufacturing method thereof.

  Industrial plants such as chemical plants and power generation facilities often use headers to collect fluids (eg, steam and / or other steam). These headers and associated distribution hardware always have a circular cross-sectional geometry of uniform wall thickness. Such geometric attributes are selected because they can be easily manufactured from off-the-shelf pipes, by rolling and seam welding plates or by centrifugal casting. Manufacturing ease determines the shape and wall thickness of the header geometry.

  FIG. 1 shows a front view and a side view of a commercially available header 100 (also referred to herein as a “comparison header”). As can be seen from FIG. 1, the header 100 has a uniform circular cross-sectional inner diameter “d” and a wall thickness “t” in communication with the array of tubes 104 that enter the header along its length. A shell 102 is included. The shell 102 serves to collect fluid that is expelled into the shell through the array of tubes 104.

  The shell 102 has a first end 106 and a second end 108 opposite to the first end 106. The first end 106 is sealed to the outside, while the second end 108 communicates with an exit port (not shown), which collects in the header 100. The discharged fluid can be discharged to the outside.

  In the drawing shown in FIG. 1, the steam pressure and / or fluid flow rate into the header 100 is lowest in the arrangement of tubes 104 closest to the first end 106, whereas it is highest at the opposite end. Highest in the array of near tubes 104. The inner diameter “d” of the shell 102 is determined by considering the pressure drop within the shell 102. This is done to ensure that the arrangement of tubes 104 controls the resistance in the system. The diameter d of the shell 102 is also calculated in a form that limits the friction loss in the header itself. This inner diameter d thus defines the bore of the tube used to manufacture the shell 102. Since the entire inner diameter is based on the accumulated flow of fluid entering the shell 102, the header design shown in FIG. 1 is larger than necessary except at the exit plane, resulting in an efficient design. Use a larger amount of material than is needed for. This increases material costs and results in headers that are expensive and occupy more space in the plant than necessary.

  Since more expensive materials are used to manufacture the header, these older designs can be cost prohibitive. It is desirable to use geometries and wall thicknesses that allow cost savings while at the same time reducing maintenance costs and component failures. It is also desirable to produce a header and associated distribution system that can operate under existing conditions in the plant for the same or longer period as an existing header design.

A shell and a tube that act to collect fluid, wherein the inner diameter and / or wall thickness of the shell changes with changes in pressure in the shell and / or changes in fluid flow rate. Disclosed herein is a shape-optimized header comprising: a tube in communication with the shell and acting to transfer fluid into the shell.

  A method comprising fixedly attaching a tube to a shell, wherein the shell acts to collect fluid, the inner diameter and / or wall thickness of the shell being a change in pressure and / or a change in fluid flow in the shell. A method is disclosed herein that varies with and the tube is in communication with the shell and acts to transfer fluid into the shell.

A front view and a side view of a header 100 (also referred to herein as a “comparison header”) currently on the market are shown. Fig. 2 shows an embodiment in which the shape of the comparison header of Fig. 1 is optimized according to the present invention. 2 is a front view of an exemplary embodiment showing the header 200 of FIG. 2 except that the cross-sectional area of the shell is increased stepwise from the first end 206 to the second end 208. FIG. is there. The comparison structure (prior art) of the header 100 which has several exit is shown. 5B shows an optimized configuration of the same header of FIG. 5A with multiple outlets according to the present invention. A comparative configuration (prior art) of a header 100 having a central T-tube is shown. Fig. 4 shows a configuration optimized for the same header 200 with one outlet according to the present invention. 6B is a cross-sectional view of the comparative header wall 100 at a location where the tube 104 contacts the wall of the shell 102 of FIG. 6A. FIG. 6B shows a cross-sectional view of the wall portion of the header 200 with optimized shape in FIG. 6B.

DETAILED DESCRIPTION The invention will now be described more fully hereinafter with reference to the accompanying drawings, in which various embodiments are shown. However, the present 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. Throughout, the same symbols indicate the same elements.

  When one element is “on” another element, it is understood that the one element may be directly on another element or there may be intervening elements between them. . In contrast, when one element is “directly on” another element, there are no intervening elements present. As used herein, “and / or” includes any and all combinations of one or more of the associated listed items.

  Although the terms first, second, third, etc. may be used herein to describe various elements, components, regions, layers and / or sections, these elements, components, It is understood that regions, layers and / or sections should not be limited by these terms. These terms are only used to distinguish one element, component, region, layer or section from another element, component, region, layer or section. That is, a first element, component, region, layer or section described below may be referred to as a second element, component, region, layer or section without departing from the disclosure of the present invention. .

  The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting. As used herein, the singular description is intended to include the plural unless the context clearly indicates otherwise. “Including” and / or “including”, or “having” and / or “having”, as used herein, refers to the feature, region, integer, step, operation, element mentioned It is further understood that identifying the presence of and / or a component does not exclude the presence or addition of one or more other features, regions, integers, steps, operations, elements, components and / or groups thereof. The

  Further, relative terms such as “lower” or “lower” and “upper” or “upper” herein refer to the relationship of one element to another, as illustrated in the drawings. It may be used here to illustrate. Relative terms are intended to include various orientations of the device in addition to the orientation shown. For example, if a device in one of the drawings is flipped, an element that has been described as “lower” of the other element will now be oriented “upper” of the other element. . Thus, the typical term “lower” can include both “lower” and “upper” orientations, depending on the particular orientation of the drawing. Similarly, when a device in one of the drawings is flipped, an element described as being “below” or “below” another element is now oriented “below” the other element. Will be. The typical term “down” or “down” can include both up and down orientations.

  Unless defined otherwise, all terms used herein (including technical and scientific terms) have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. Have Terms as defined in commonly used dictionaries should be construed as having a meaning consistent with the meaning in the context of the related art and this disclosure, and are not so explicitly defined here As long as it is not interpreted in an idealized or overly formal sense.

  Exemplary embodiments will now be described with reference to cross-sectional views that are schematic illustrations of idealized embodiments. This predicts, for example, deviations from the example shape as a result of manufacturing techniques and / or tolerances. That is, the embodiments described herein should not be construed as limited to the particular shapes of the regions as exemplified herein, but include, for example, shape shifts resulting from manufacturing. For example, a region illustrated or described as flat may typically have coarse and / or non-linear features. Furthermore, the illustrated acute angles may be rounded. That is, the illustrated regions are schematic in nature, and their shapes are not intended to exemplify the exact shape of a region, nor are they intended to limit the scope of the claims herein. .

  The connective word “includes” encompasses connective words such as “consisting essentially of” and “consisting of”.

  All numerical ranges disclosed herein include endpoints. In addition, all numbers and values in any range (including those not expressly stated herein) are understood to be inherently included in the invention. All numbers included here are compatible.

  Optimized shape with cross-sectional area and wall thickness optimized for local operating stresses and fluid (e.g. water, steam and / or other steam or fluid) velocities that occur during header operation Headers and associated conduits (hereinafter referred to as “shape optimized headers”) are disclosed herein. The shape-optimized header has a variable cross-sectional area and / or wall thickness shell. The cross-sectional area and / or wall thickness of a particular part of the shell of the header is a combination of the accumulated flow in the head of the incoming fluid and the geometry of the connecting pipe, and the velocity and / or inflow of the fluid in that particular part of the shell Depending on the chemical composition of the fluid to be changed in proportion to local flow and local stress. Shape-optimized headers are more than (in other cross-sectional areas and wall thicknesses of the same header) only in those local areas where the header produces higher stresses (due to the geometry of the inlet pipe) and fluid flow rates It is designed in such a way that it has a large cross-sectional area and possibly a larger wall thickness.

  These portions of the shell that produce a lower flow rate than the portion near the outlet are smaller cross-sectional areas and smaller walls than the corresponding cross-sectional areas and wall thicknesses of shells designed in a conventional manner as shown in FIG. Have a thickness.

  The resulting shape-optimized header can have multiple cross-sectional areas and wall thicknesses depending on the local stresses and flow rates that occur during operation. In one embodiment, the shape-optimized header may use different construction materials depending on the chemical properties of the fluid that occurs in the various parts. The shape-optimized header can be formed from special materials that are more expensive than those used in the header shown in FIG. 1, but the optimized design makes the header of FIG. The cost can be reduced as compared with the case where it is formed from the above material.

  These shape-optimized headers occupy less floor space and volume space in the plant and can be used during operation for the same or longer duration as headers designed in the form shown in FIG. It is also advantageous in that it can be done.

FIG. 2 shows an aspect in which the shape of the comparison header in FIG. 1 is optimized. In FIG. 2, a shape-optimized header 200 has a shell 202 (in the form of a conical portion) having a circular cross-sectional inner diameter, which is (stress and / or fluid flow rate). From the minimum diameter value d ₁ at the lowest end (to the maximum stress and / or fluid flow rate) to the maximum diameter value d ₂ at the opposite end. The wall thickness also varies from the minimum wall thickness t ₁ (at the end where stress and / or fluid flow is lowest) to the maximum wall thickness t ₂ at the opposite end (where stress and / or fluid flow is maximum). doing.

  The header 202 has a first end portion 206 and a second end portion 208 opposite to the first end portion 206. Whereas the first end 206 is sealed to the outside (ie, external fluid cannot enter or exit the shell 202 through the first end 206). The second end 208 is in communication with an outlet port (not shown), which allows the header 200 to be discharged to the outside. FIG. 2 shows a smooth linear change in header cross-sectional area and a smooth linear change in wall thickness from the first end 206 to the second end 208, but other changes. May be used. For example, changes in cross-sectional area or thickness can be non-linear according to local stresses and / or fluid flow into the header (eg, curves that change according to exponential or spline functions, curves that change randomly in a discontinuous manner) Or a combination thereof. The inner surface 218 or the outer surface 220 of the header 200 may be a continuously changing surface, or a discontinuously changing surface (ie, having a change similar to a step function), or A combination thereof may also be used.

ここで、ｄ₂、ｄ₁、ｔ₂およびｔ₁は図２に示されており、ｐ₂は、ヘッダの様々な部分において生じる最高圧力であり、ｐ₁は最低圧力である。 In one embodiment, the increase in shell diameter and / or wall thickness is proportional to the local pressure rise that occurs in various parts of the header and can be represented by equation (1) as follows: it can:

Here, d ₂ , d ₁ , t _2, and t ₁ are shown in FIG. 2, where p ₂ is the highest pressure that occurs at various parts of the header, and p ₁ is the lowest pressure.

ここで、Δｄ₂は、シェルの第２の部分の内径の変化であり、Δｄ₁は、シェルの第１の部分の内径の変化であり、Δｔ₂は、シェルの第２の部分の壁厚の変化であり、Δｔ₁は、シェルの第１の部分の壁厚の変化であり、Δｐ₂は、シェルの第２の部分において生じる圧力変化であり、Δｐ₁は、シェルの第１の部分において生じる圧力の変化である。 In another embodiment, the change in diameter and / or change in shell wall thickness is proportional to the change in local pressure that occurs in the shell and is determined by equation (1a):

Where Δd ₂ is the change in inner diameter of the second portion of the shell, Δd ₁ is the change in inner diameter of the first portion of the shell, and Δt ₂ is the wall thickness of the second portion of the shell. Δt ₁ is the change in wall thickness of the first part of the shell, Δp ₂ is the pressure change that occurs in the second part of the shell, and Δp ₁ is the first part of the shell The change in pressure that occurs in

ここで、ｄ₂、ｄ₁、ｔ₂およびｔ₁は図２に示されており、ｆ₂は、ヘッダの様々な部分において生じる最大流体流量であり、ｆ₁は最小流体流量である。 In yet another embodiment, the increase in shell diameter and / or wall thickness is proportional to the increase in fluid flow rate that occurs in various portions of the header and can be represented by equation (2) as follows: it can:

Here, d ₂ , d ₁ , t ₂ and t ₁ are shown in FIG. 2, where f ₂ is the maximum fluid flow that occurs at various parts of the header, and f ₁ is the minimum fluid flow.

ここで、Δｄ₂は、シェルの第２の部分の内径の変化であり、Δｄ₁は、シェルの第１の部分の内径の変化であり、Δｔ₂は、シェルの第２の部分の壁厚の変化であり、Δｔ₁は、シェルの第１の部分の壁厚であり、Δｆ₂は、シェルの第２の部分において生じる流体流量の変化であり、Δｆ₁は、シェルの第１の部分において生じる流体流量の変化である。 In another embodiment, the change in diameter and / or change in shell wall thickness is proportional to the change in fluid flow rate occurring in the shell and is determined by equation (2a):

Where Δd ₂ is the change in inner diameter of the second portion of the shell, Δd ₁ is the change in inner diameter of the first portion of the shell, and Δt ₂ is the wall thickness of the second portion of the shell. Δt ₁ is the wall thickness of the first portion of the shell, Δf ₂ is the change in fluid flow that occurs in the second portion of the shell, and Δf ₁ is the first portion of the shell. Is the change in fluid flow rate that occurs in

ここで、ｆ₂は、シェルの第２の部分において生じる流体流量であり、ｆ₁は、シェルの第１の部分において生じる流体流量であり、Ａ₁およびＡ₂は、流体流量ｆ₁およびｆ₂を生じるシェルの部分の断面積であるのに対し、ｄ₁およびｄ₂は、流体流量ｆ₁およびｆ₂を生じるシェルの部分におけるヘッダのそれぞれの内径である。 In one embodiment, in one form of designing the header, page 7 [0], it is desirable to maintain a uniform velocity or fluid flow along the length of the header. The flow rate or velocity is proportional to the cross-sectional area of the header and is therefore proportional to the square of the header's inner diameter as shown in equation (3):

Where f ₂ is the fluid flow rate occurring in the second part of the shell, f ₁ is the fluid flow rate occurring in the first part of the shell, and A ₁ and A ₂ are the fluid flow rates f ₁ and f while the cross-sectional area of the portion of the shell to produce _2, d ₁ and d ₂ are the respective internal diameter of the header in the portion of the shell to produce fluid flow f ₁ and f _2.

ここで、ｐは、ヘッダの任意の部分における圧力であり、ｄは、ヘッダの内径であり、ｔは、ヘッダの壁厚である。 The thickness of the header is varied to maintain a uniform stress due to the pressure at the header. Stress is equal to the product of pressure and diameter divided by thickness. In other words, the stress is proportional to the diameter, but inversely proportional to the thickness as shown in equations (4) and (5):

Where p is the pressure at any part of the header, d is the inner diameter of the header, and t is the wall thickness of the header.

ここで、ｄ₂は、シェルの第２の部分の内径であり、ｄ₁は、シェルの第１の部分の内径であり、ｔ₂は、シェルの第２の部分の壁厚であり、ｔ₁は、シェルの第１の部分の壁厚であり、ｐ₂は、シェルの第２の部分において生じた圧力であり、ｐ₁は、シェルの第１の部分において生じた圧力であり、σ₂およびσ₁は、シェルの第２の部分およびシェルの第１の部分においてそれぞれ生じた応力である。等式（４）および（５）から、任意の圧力の場合、応力は、直径および壁厚を同じ大きさだけ減じることにより一定に維持されることが分かる。

Where d ₂ is the inner diameter of the second portion of the shell, d ₁ is the inner diameter of the first portion of the shell, t ₂ is the wall thickness of the second portion of the shell, and t ₁ is the wall thickness of the first part of the shell, p ₂ is the pressure generated in the second part of the shell, p ₁ is the pressure generated in the first part of the shell, and σ ₂ and σ ₁ are the stresses produced in the second part of the shell and the first part of the shell, respectively. From equations (4) and (5) it can be seen that for any pressure, the stress is kept constant by reducing the diameter and wall thickness by the same amount.

  FIG. 4 illustrates an exemplary embodiment showing the header 200 of FIG. 2 except that the cross-sectional area of the shell is increased stepwise from the first end 206 to the second end 208. FIG. This increase in cross-sectional area varies with increasing local pressure and / or fluid flow, as shown in equations (1) and (2) above. As the cross-sectional area is increased, the wall thickness t is also increased to compensate for increased pressure and / or fluid flow.

From FIG. 4, the cross-sectional area increases from d ₁ to d ₂ and d _{3 as} the pressure increases from p ₁ to p ₂ and p ₃ and / or the fluid flow rate increases from f ₁ to f ₂ and f ₃ . It can be seen that the wall thickness increases from t ₁ to t ₂ and t ₃ .

  The header 200 in FIGS. 2 and 4 each has one outlet at the second end 208, although more than one outlet may be provided if desired. FIG. 5 shows a header 200 having a plurality of outlets. FIG. 5A shows a comparative configuration for a header 100 with multiple outlets, while FIG. 5B shows a shape-optimized configuration for the same header 200 with multiple outlets. ing. In FIG. 5B, the cross-sectional area of the shell 202 is maximized near the outlet at the first end 206 and the second end 208. This is because these regions produce the highest pressures and / or fluid flow rates. The wall thickness in the exit area is greater than the wall thickness in other areas of the header. As described above, the outlets located near the first end 206 and the second end 208 of the header are used to remove the fluid or vapor carried by the header from the header 200. .

  FIG. 6A shows a comparative header with a shape-optimized header for a design with a central tee serving as an outlet. FIG. 6A shows a comparative configuration for a header 100 with a central tee, whereas FIG. 6B shows a shape optimized configuration for the same header 200 with one outlet. Show. The central tee 212 is used as an outlet in FIG. 6B but is shown as 112 in FIG. 6A.

  From FIG. 6B, it can be seen that the cross-sectional area of the shell is largest at the center of the header. This is because this is the region where pressure and / or fluid flow is maximum. Similarly, the wall thickness is maximum at the center. The wall thickness of the shell is the thinnest at both ends 206 and 208 where pressure and / or fluid flow is minimal.

  In the absence of tube (204) entry into the wall of the header and / or the absence of any other entry, the wall thickness is determined by the internal pressure that the header must withstand during normal operation, or by an incorrect case As determined, or by other conditions as defined by dominant rules, standards or other design rules. This principle generally applies to the wall thickness in the region where the tube is also fixed to the header wall. However, these areas can be weakened by the addition of tubes to the walls. In addition, these areas have greater utility because all of the fluid entering the header contacts the tube 204. The fluid entering the header also contacts the area of the header around the tube 204 due to the proximity of the area to the fluid entry location. Thus, the area where the fluid enters the header is weakened faster than the other areas of the header.

  In one embodiment, the region where the tube is secured to the wall of the header 200 is added to the region normally weakened by the removal of material to provide a passage for fluid entry from the tube into the shell. The thickness may be increased to provide general reinforcement. The enhancement also provides a longer life cycle for areas that have greater usage than other areas during the course of header operation. This increase in thickness is local and can only be undertaken in close proximity to the area where the tube 204 is fixedly attached to the header.

  In one embodiment shown in FIG. 7B, the area of the wall to which the tube 204 is fixedly attached is the material removed by forming an indentation for the tube to communicate with the shell. It is thickened to compensate locally or to overcome wear and degradation that occurs with increased usage. This increased local thickness provides the header with an increased life cycle while simultaneously reducing the weight of the header and reducing material costs.

FIG. 7A is a cross-sectional view of the comparative header wall 100 at a location where the tube 104 contacts the wall of the shell 102. The header wall 100 typically has a thickness t ₄ if the tube 104 is not in contact with the header. To compensate for structural weakening due to the presence of the tube 104, the thickness of the header wall portion 100 are increased to t _5. This increase in thickness from t ₄ to t ₅ in conventional headers results in increased material costs and increased weight of the finished header.

FIG. 7B shows a cross-sectional view of the wall of the header 200 whose shape has been optimized. In the header 200 with an optimized shape, the wall thickness for the header, except that the wall thickness is increased to t ₅ in the appropriate region near the tube 204 is fixedly attached to the header , T ₄ . This local increase in thickness ensures stress uniformity in the header while actually reducing the weight when compared to the weight of the comparison header in FIG. 7A.

  The shell of the header 200 may be manufactured from an iron-based alloy, a nickel-based alloy, a tantalum-based alloy, and a titanium-based alloy.

In one embodiment, in one method of manufacturing a shape optimized header, a smaller diameter d ₁ (corresponding to a lower flow rate f ₁ ) and an end opposite the smaller diameter d _1. The shell in the form of a conical section with a larger diameter d ₂ (corresponding to a higher flow rate f ₂ ) in the part was sealed to prevent fluid from inside the shell from contacting the outside , Having opposite ends. The outlet (or inlet-inlet can also function as an outlet) is then perforated or cut in a portion of the shell. The outlet is used to drain its contents from the shell. A hole is drilled in the shell to accommodate a tube that drains fluid into the shell.

  In one embodiment, in one method of manufacturing a shape-optimized header having a smooth increase in cross-sectional area (from the portion of the header that produces low pressure to the portion of the header that produces higher pressure) A sheet metal roll (eg, a metal scroll) is held or fixed at one end, while the opposite end is extended from the fixed end. In addition to being extended in the longitudinal direction, the metal is extended radially outward from the center of the scroll, so that for each turn of the sheet metal, the header diameter increases with length. doing. When the length and diameter reach the desired limits, the overlapping sheets are seam welded or riveted together to form the header shell. The header end may be cut to form two parallel ends. The end of the header may be welded to the shell. One end may be sealed to the outside, while the other end has an opening through which the contents of the header are removed for recycling or Discharged for disposal.

  Since it is generally desirable to increase the wall thickness in the direction of increasing cross-sectional area, sheet metal scrolls of increasing thickness can be used to produce headers as described above. When manufacturing a header (shell) from such a thin plate, the thinnest part is held fixed, whereas the thickest part of the scroll has a smoothly increased cross-sectional area and wall thickness. In order to produce a growing shell, it is extended outward away from the thinnest part.

  Holes may be drilled in the surface of the shell to secure the tube to the header. The tube may be welded to the shell as shown in FIGS. 2-5 above. In another embodiment, the tube may be threaded into threads formed in the shell wall or welded to the shell. In one embodiment, the shell may be selectively thickened in a local area surrounding the tube by using techniques such as laser welding. Other techniques used to form the header and for local strengthening are conventional casting, spray molding, thermal spray molding, and powder metallurgy.

  In another embodiment, a header whose cross-sectional area is increased in a step function fashion as shown in FIG. 4 (from a portion of the header that produces lower pressure to a portion of the header that produces higher pressure). In another form of manufacture, tubes (spools) of varying desired diameter and thickness are first cut and then welded or riveted together to form a header. The header and tube ends are then welded together to form the header.

  In addition to achieving material savings from shape optimization, the use of thinner walls and shells reduces thermal stress and the life cycle and durability of headers or other equipment manufactured using these methods and principles To increase. Another advantage is that the reduced diameter and wall thickness results in smaller weldments (fewer passes) to join multiple spools to form a larger header.

  Although the invention has been described with reference to exemplary embodiments, various modifications can be made without departing from the scope of the invention, and equivalents may be substituted for the elements of the embodiments. It will be understood. In addition, many modifications may be made to adapt a particular situation or material to the disclosure of the invention without departing from the basic scope thereof. Accordingly, the invention is not limited to the specific embodiments disclosed as the best mode contemplated for carrying out the invention.

Claims (18)

In the header with optimized shape,
A shell including a plurality of cylinders and acting to collect fluid, wherein the inner diameter of the plurality of cylinders of the shell increases from a first end to a second end, the first end A shell that is sealed to the outside and wherein the second end is in fluid communication with the outlet port;
A plurality of tubes, each of said plurality of tubes, said in fluid shell and communicates, acts to transfer the fluid into said shell comprises a plurality of tubes, and
The plurality of tubes are disposed from a position close to the first end to a position close to the second end;
The fluid flowing in from the plurality of tubes is transferred to the outlet port through the shell,
The shape-optimized header, wherein the wall thickness of the plurality of cylinders of the shell increases from the first end to the second end.   The shape-optimized header of claim 1, wherein the shape-optimized header further comprises an outlet used to drain fluid collected in the header. The plurality of cylinders are
A first cylindrical portion disposed at the first end and having a first inner diameter and a first wall thickness;
A second cylindrical portion connected to the first cylindrical portion and having a second inner diameter that is longer than the first inner diameter and a second wall thickness that is greater than the first wall thickness;
A third cylindrical portion disposed at the second end and having a third inner diameter that is longer than the second inner diameter and a third wall thickness that is greater than the second wall thickness. Item 3. A header in which the shape according to item 1 or 2 is optimized. A first number of tubes of the plurality of tubes is connected to the first cylindrical portion;
A second number of tubes greater than the first number of the plurality of tubes is connected to the second cylindrical portion;
The shape-optimized header according to claim 3, wherein a third number of tubes greater than the second number of the plurality of tubes are connected to the third cylindrical portion. The shape-optimized header of claim 4, wherein the plurality of tubes extend through each of the first to third cylindrical portions and into the shell. The first cylindrical portion has a first length;
The second cylindrical portion has a second length that is longer than the first length;
6. The shape optimized header of claim 5, wherein the third cylindrical portion has a third length that is longer than the second length.   The shape-optimized header according to any of claims 1 to 6, wherein the fluid is steam.   The header having an optimized shape according to claim 1, wherein the shell includes any one of an iron-based alloy, a nickel-based alloy, a tantalum-based alloy, and a titanium-based alloy.   The shape-optimized header according to any of claims 1 to 7, wherein the shape-optimized header further comprises a plurality of outlets that act to drain fluid collected in the header. The shape-optimized header according to any of claims 1 to 9, wherein the wall thickness of the portion of the shell that contacts the plurality of tubes is increased. A method of manufacturing a header comprising:
Including fixing and attaching a plurality of tubes to the shell;
The shell includes a plurality of cylinders and serves to collect fluid, and the inner diameter of the plurality of cylinders of the shell increases from a first end to a second end, and the first end The second end is in fluid communication with the outlet port, the plurality of tubes are in communication with the shell, and transfers the fluid into the shell. Act to
The plurality of tubes are disposed from a position close to the first end to a position close to the second end;
The fluid flowing in from the plurality of tubes is transferred to the outlet port through the shell,
The wall thickness of the plurality of cylinders of the shell increases from the first end to the second end;
A method characterized by that.   The method of claim 11, wherein the shells are riveted together or welded together. The method of claim 11, wherein the plurality of tubes are welded to the shell. The plurality of cylinders are
A first cylindrical portion disposed at the first end and having a first inner diameter and a first wall thickness;
A second cylindrical portion connected to the first cylindrical portion and having a second inner diameter that is longer than the first inner diameter and a second wall thickness that is greater than the first wall thickness;
A third cylindrical portion disposed at the second end and having a third inner diameter longer than the second inner diameter and a third wall thickness greater than the second wall thickness;
The method
Connecting a first sealing member disposed at the first end to the first cylindrical portion;
Connecting the first cylindrical portion to a first flange;
Connecting the first flange to the second cylindrical portion;
Connecting the second cylindrical portion to a second flange;
Connecting the second flange to the third cylindrical portion;
The method according to claim 11, comprising: Connecting a first number of tubes of the plurality of tubes to the first cylindrical portion;
Connecting a second number of tubes greater than the first number of the plurality of tubes to the second cylindrical portion;
Connecting a third number of tubes greater than the second number of the plurality of tubes to the third cylindrical portion. The method of claim 15, wherein the plurality of tubes are attached to extend through each of the first to third cylindrical portions and into the shell. The first cylindrical portion has a first length;
The second cylindrical portion has a second length that is longer than the first length;
The method of claim 16, wherein the third cylindrical portion has a third length that is longer than the second length. 18. A method according to any of claims 11 to 17, wherein the wall thickness of the portion of the shell that contacts the plurality of tubes is increased.

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