JP7173929B2 - Method for manufacturing heat exchange part of plate-fin heat exchanger and heat exchange system - Google Patents

Description

The present invention relates to a heat exchange section of a plate-fin heat exchanger and a method for manufacturing a heat exchange system comprising the heat exchange section.

A so-called plate-fin type heat exchanger is known for exchanging heat between different fluids. For example, the heat exchanger described in Patent Literature 1 includes a heat exchange section 100 as shown in FIGS. 5 and 6. FIG. The heat exchange section 100 has a plurality of partition plates 102 , a plurality of fin plates 104 and a plurality of closing members 106 . The plurality of partition plates 102 are arranged parallel to each other at intervals in the stacking direction corresponding to the vertical direction in FIGS. Each of the plurality of fin plates 104 is formed in a wavy shape and is disposed between adjacent partition plates 102 to form a plurality of fluid channels. The plurality of closing members 106 are arranged on both sides of the fin plate 104 in the width direction, and cover the space between the partition plates 102 adjacent to each other in the width direction perpendicular to the stacking direction (the left-right direction and the depth direction in FIG. 6). direction). Each of the plurality of fin plates 104 is, for example, brazed to the partition plate 102 so as to transfer the heat of the fluid flowing through the plurality of fluid channels to the pair of partition plates 102 adjacent to the fin plate 104. joined by

In the heat exchange section 100, the plurality of fin plates 104 are arranged such that the directions of the fluid flow paths formed by the fin plates 104 adjacent to each other in the stacking direction of the plurality of fin plates 104 are orthogonal to each other. ing. Specifically, the fin plates 104 arranged in an even number of stages counted from the top are arranged so as to form a plurality of first fluid flow passages r1 arranged in a first width direction (horizontal direction in FIG. 6). The closing members 106 are arranged on both outer sides of the plate 104 in the first width direction. Similarly, the fin plates 104 arranged in odd-numbered stages counted from the top form a plurality of second fluid flow passages r2 arranged in a second width direction (depth direction in FIG. 6) orthogonal to the first width direction. The closing members 106 are arranged on both outer sides of the fin plate 104 in the second width direction.

In this heat exchange section 100, the first fluid is caused to flow through the plurality of first fluid flow paths r1, and the second fluid is allowed to flow through the plurality of second fluid flow paths r2, so that each partition Heat exchange is performed between the first fluid and the second fluid flowing on both upper and lower sides (both sides in the stacking direction) of the plate 102 as a medium. For example, if the temperature of the second fluid is lower than the temperature of the first fluid, the first fluid is cooled by heat exchange with the second fluid.

JP-A-7-167580

In a plate-fin heat exchanger having a heat exchange section similar to the heat exchange section 100, the temperature or flow rate of a fluid (e.g., the first fluid or the second fluid) flowing through the heat exchange section suddenly fluctuates. In this case, a large difference in thermal displacement resulting from this causes a large thermal stress in the heat exchanging portion, which may cause damage.

An object of the present invention is to provide a method for manufacturing a heat exchange section of a plate-fin heat exchanger capable of reducing such thermal stress, and a method for manufacturing a heat exchange system including the heat exchange section. .

In order to solve the above problems, the present inventors have carefully examined the cause of the occurrence of the thermal stress, and as a result, have found that the following means are effective for solving the problems.

(A) Restriction on stacking height dimension In the heat exchange part as described above, there is a difference in the speed of following the temperature of the introduced fluid depending on the part of the heat exchange part, so the amount of thermal deformation temporarily A large difference occurs, which causes excessive thermal stress. For example, in the heat exchange section 100 shown in FIGS. 5 and 6, the mass of the blocking members 106 arranged on both sides in the width direction is generally larger than that of the thin fin plates 104. It thermally deforms at a higher rate than member 106 . Therefore, if the heat exchange section 100 is rapidly cooled or heated by the temperature of the fluid flowing through the heat exchange section 100, there will temporarily be a significant difference between the amount of thermal deformation of the fin plate 104 and the amount of thermal deformation of the closing member 106. there is a difference. Moreover, since the difference in the amount of thermal deformation is integrated in proportion to the number of stages, the difference in the amount of thermal deformation increases as the distance from the central position in the stacking direction (for example, the central position in the vertical direction in the structure shown in FIG. 6) increases. growing. Therefore, suppressing this distance, that is, suppressing the stacking height, which is the dimension of the entire heat exchanging portion in the stacking direction, makes it possible to reduce the thermal stress.

Normally, the heat exchange section of a plate-fin heat exchanger is heated in a dedicated furnace in a state in which partition plates, fin plates and closing members are alternately stacked as shown in FIG. The fin plate and the partition plate are brazed by. The stacking height (dimension in the stacking direction) of the heat exchange section at this time is usually the allowable height of the furnace (the maximum stacking height of the heat exchange section that can be inserted into the furnace). and this reduces the required number of plate-fin heat exchangers each containing said heat exchange section, enabling an economical design. However, it is possible to reduce the thermal stress by deliberately suppressing the stacking height of the heat exchange part to be significantly smaller than the allowable height of the furnace (specifically, making it less than half of the allowable height). .

(B) Uniformity of Density in Heat Exchange Section As described above, a plurality of fin plates and a plurality of partition plates are alternately arranged in the stacking direction, and each fin plate has a large thickness on both sides in the width direction. In the heat exchange section in which the blocking members having the dimensions are arranged, both widthwise outer portions of the heat exchanging section, that is, the portion where the plurality of blocking members are arranged in the stacking direction, and the inner portion sandwiched between the both outer portions, that is, the above-mentioned There is a difference in speed following the temperature of the introduced fluid between the portion where the plurality of fin plates are arranged in the stacking direction and the portion. This temperature follow-up speed difference can be reduced by reducing the difference between the density in the outer portions and the density in the inner portion.

In order to reduce the density difference, the thickness of the plurality of partition plates should be increased, in other words, the space occupied by the fin plates forming the gaps, which are the flow paths for the fluid, should be relatively reduced. is valid. That is, making the actual thickness of the partition plate significantly larger than the theoretically required thickness (specifically, making it 1.3 times or more the theoretically required thickness) also makes it possible to reduce the thermal stress. do. Here, the theoretical required plate thickness is a plate thickness calculated from the pressure of the fluid flowing through the flow paths formed by the fin plates.

The present invention has been made from such a viewpoint. Provided by the present invention is a method for manufacturing a heat exchange section of a plate-fin heat exchanger, said heat exchange section comprising a plurality of partition plates arranged in parallel and spaced apart in the stacking direction. and, among the plurality of partition plates, arranged between the partition plates that are adjacent to each other in the stacking direction and brazed to the partition plates so that a width direction parallel to the partition plates is formed between the partition plates. a plurality of fin plates forming a plurality of fluid flow paths arranged in parallel, and the plurality of fin plates so as to close a space formed between partition plates adjacent to each other in the stacking direction among the plurality of partition plates. and a plurality of closing members arranged on both outer sides in the width direction. The method comprises a preparing step of preparing the plurality of partition plates, the plurality of fin plates and the plurality of closing members, alternately stacking the plurality of partition plates and the plurality of fin plates in the stacking direction, and an assembling step of assembling a heat exchanging portion assembly by arranging the closing members respectively on both outer sides of the plurality of fin plates in the width direction; placing the assembly in a furnace and heating to join each of the plurality of fin plates to the partition plate adjacent to the fin plate by vacuum brazing.

As a feature of this method, in the assembling step, the stacking height of the heat exchanging section assembly is set to 1/2 or less of the allowable height of the furnace. The stacking height is the dimension of the heat exchange assembly in the stacking direction, and the allowable height of the furnace is the maximum stacking height of the heat exchange assembly that is allowed to be placed in the furnace. value. This feature occurs at both ends in the stacking direction due to rapid changes in the temperature or flow rate of the fluid that flows through the fluid flow path, due to intentionally reducing the stacking height of the heat exchange assembly. It makes it possible to relieve large thermal stresses.

In the method, the thickness of the plurality of partition plates prepared in the preparing step is set to 1.3 times or more of the theoretically required plate thickness calculated based on the pressure of the fluid flowing through the fluid channel. is preferred. By increasing the thickness of the partition plate and intentionally reducing the occupied area ratio of the fluid flow channel formed by the fin plate, the density of both outer portions where the plurality of blocking members are arranged in the stacking direction is increased. and the density of the inner portion between the outer portions where the fin plates are arranged in the stacking direction. This reduces the difference between the speed at which the outer portions follow the temperature of the fluid when the fluid is caused to flow through the fluid channel and the speed at which the inner portion follows the temperature, thereby reducing the speed difference. It is possible to reduce the large thermal stress generated due to.

The invention also provides a method for manufacturing a heat exchange system with a plurality of heat exchange sections. This method comprises steps of manufacturing a plurality of heat exchange parts for constituting the heat exchange system by the method for manufacturing the heat exchange part of the plate fin heat exchanger, and setting a throughput of the entire heat exchange system in advance. determining the number of the heat exchange units constituting the heat exchange system so as to satisfy the required throughput, and connecting the heat exchange units of the determined number in parallel.

As described above, according to the present invention, the heat exchange portion of a plate-fin heat exchanger that can reduce the large thermal stress caused by rapid fluctuations in the temperature or flow rate of the fluid flowing through the fluid flow path. and a method for manufacturing a heat exchange system comprising the heat exchange section.

1 is a perspective view of a plate-fin heat exchanger according to an embodiment of the invention; FIG. FIG. 4 is a partially cross-sectional perspective view showing a lower portion of a heat exchange portion included in the plate-fin heat exchanger; It is a top view which shows the cross section along the horizontal surface of the said heat exchange part. 1 is a flowsheet showing an example of a heat exchange system comprising multiple plate-fin heat exchangers connected in parallel. FIG. 3 is an exploded perspective view of a heat exchanging portion in a conventional heat exchanger; FIG. 6 is a front view of the heat exchange section shown in FIG. 5;

Preferred embodiments of the present invention will be described below with reference to FIGS. 1 to 4. FIG.

1 to 3 show a heat exchanger HE which is an example of a plate-fin heat exchanger that can be manufactured by the manufacturing method according to the invention. The heat exchanger HE has a structure that allows the first fluid F1 and the second fluid F2 to flow inside the heat exchanger HE and exchange heat with each other. Specifically, the heat exchanger HE includes a heat exchange section 3, a first inlet header 21, a first outlet header 22, a second inlet header 23, a second inlet header 24, and an upper flow path forming section. 25 and a lower channel forming portion 26 , the heat exchange portion 3 forms a plurality of fluid channels 30 . The plurality of fluid flow paths 30 include a plurality of first fluid flow paths 30a through which the first fluid F1 flows, and a plurality of second fluid flow paths 30b through which the second fluid F2 flows.

The first inlet header 21 is joined to the lower end of the lower flow path forming portion 26, and receives the supply of the first fluid F1 through the first fluid supply pipe 41 to the plurality of first fluid flow paths 30a. Defining a space for dispensing. The first outlet header 22 is joined to the upper end of the upper flow path forming portion 25, receives the first fluid F1 discharged from the plurality of first fluid flow paths 30a, and guides it to the first fluid discharge pipe 42. define a space for The second inlet header 23 is joined to the upper portion of the side surface of the upper flow path forming portion 25, receives the supply of the second fluid F2 through the second fluid supply pipe 43, and feeds the plurality of second fluid flow paths 30b. Defining a space for dispensing. The second outlet header 24 is joined to a lower portion of a side of the upper flow path forming portion 26 opposite to the second inlet header 23, and is discharged from the plurality of second fluid flow paths 30b. A space is defined for receiving the second fluid F2 and leading it to the second fluid discharge line 44 .

The heat exchanging portion 3 is housed in the central portion of the casing 2 in the vertical direction, and the upper flow passage forming portion 25 and the lower flow passage forming portion 26 are housed in the upper and lower portions of the casing 2, respectively. The upper flow channel forming part 25 forms a plurality of upper flow channels. The plurality of upper flow paths are a plurality of second distribution paths that respectively distribute the second fluid F2 introduced from the second fluid supply pipe 43 to the second inlet header 23 to the plurality of second fluid flow paths 30b. and a first outlet channel for guiding the first fluid F1 discharged from the plurality of first fluid channels 30a to the first outlet header 22, respectively. The lower flow channel forming portion 26 forms a plurality of lower flow channels. The plurality of lower flow passages are arranged in a plurality of first flow passages for distributing the first fluid F1 introduced from the first fluid supply pipe 41 to the first inlet header 21 to the plurality of first fluid flow passages 30a. A distribution channel and a second outlet channel for guiding the second fluid F2 discharged from the plurality of second fluid channels 30b to the second outlet header 24, respectively.

In the heat exchanger HE configured as described above, the first fluid F1 supplied to the first inlet header 21 through the first fluid supply pipe 41 passes through the lower flow path forming portion 26 to the heat exchanging portion 3. are respectively introduced into the plurality of first fluid flow channels 30a. The first fluid F1 that has passed through the plurality of first fluid flow paths 30a joins the first outlet header 22 through the upper flow path forming portion 25 and is discharged through the first fluid discharge pipe 42. . On the other hand, the second fluid F2 supplied to the second inlet header 23 through the second fluid supply pipe 43 flows through the upper flow path forming portion 25 into the plurality of second fluid flow paths 30b of the heat exchanging portion 3. introduced respectively. The second fluid F2 that has passed through each of the plurality of second fluid flow paths 30b joins the second outlet header 24 through the lower flow path forming portion 26 and is discharged through the second fluid discharge pipe 44. be.

The heat exchange section 3 is configured such that the plurality of first fluid flow passages 30a and the plurality of second fluid flow passages 30b are arranged alternately along a predetermined stacking direction. 30b, thereby enabling heat exchange between the first fluid F1 flowing through the first fluid flow path 30a and the second fluid F2 flowing through the second fluid flow path 30b. Specifically, the heat exchange section 3 includes a plurality of fin plates 32 , a plurality of partition plates 33 and a plurality of side bars 34 . The stacking direction coincides with the horizontal direction indicated by the double-headed arrow AL in FIGS. 3 coincides with the vertical direction.

The plurality of partition plates 33 are made of rectangular plate materials, and are arranged in parallel with each other at intervals in the stacking direction. Each of the plurality of partition plates 33 has a flat plate shape having a first surface and a second surface opposite to the first surface, and enables heat conduction between the first surface and the second surface.

The plurality of fin plates 32 are arranged between the partition plates 33 that are adjacent to each other in the stacking direction among the plurality of partition plates 33 and are joined to the partition plates 33 . A plurality of first fluid channels 30a or a plurality of second fluid channels 30b are formed therebetween. The plurality of first fluid flow paths 30a or the plurality of second fluid flow paths 30b are arranged in the width direction (horizontal direction indicated by arrow α in FIG. 2, horizontal direction in FIG. 3) orthogonal to the stacking direction. Specifically, the plurality of fin plates 32 are thin plates made of a material with good thermal conductivity, such as the aluminum alloy, and are formed in a wavy shape in the lamination direction. is brazed to the first surface of a predetermined partition plate 33, and the vertex on the other side is brazed to the second surface of the partition plate 33 facing the first surface of the partition plate 33. As shown in FIG.

The side bars 34 are provided on both outer sides of the plurality of fin plates 32 in the width direction so as to close the space formed between the partition plates 33 adjacent to each other in the stacking direction among the plurality of partition plates 33 . placed. The side bar 34 functions as a closing member that closes the space, and also functions as a connection member that connects the partition plates 33 adjacent to each other in the stacking direction (vertical direction in FIG. 3). The side bar 34 is made of a bar material extending in a direction (depth direction in FIG. 3) parallel to the longitudinal direction of the first and second fluid flow paths 30a and 30b, and has a rectangular cross section.

Each of the plurality of fin plates 32, the plurality of partition plates 33, and the plurality of side bars 34 is made of a metal material with high thermal conductivity. The metal material is, for example, an aluminum alloy such as A3003, titanium, copper, or stainless steel.

The heat exchange section 3 according to this embodiment further includes a pair of outer sheets 37 . The pair of outer sheets 37 respectively constitute both outer portions of the heat exchange section 3 in the stacking direction, and the plurality of fin plates 32 and the plurality of partition plates 33 positioned inside the pair of outer sheets 37. and protect the plurality of side bars 34 from external force.

As shown in FIG. 3, the heat exchanging portion 3 includes both outer portions 3a in which the plurality of side bars 34 are arranged in the stacking direction, and a portion between the outer portions 3a and the plurality of fins. The plate 32 has an inner portion 3b arranged in the stacking direction, and the first and second fluid flow paths 30a and 30b are adjacent partition plates among the plurality of partition plates 33 in the inner portion 3b. The fin plates 32 are formed in the spaces between the fin plates 33 and are separated from each other in the width direction by the fin plates 32 having a wavy shape in the spaces. The first and second fluid flow paths 30a and 30b are arranged alternately in the stacking direction, and the first fluid F1 flowing through the first fluid flow path 30a and the second fluid flow flowing through the second fluid flow path 30b are arranged alternately. It enables heat exchange including heat conduction in the fin plate 32 and the partition plate 33 between two fluids F2.

Next, a method for manufacturing the heat exchanging part 3 in this embodiment will be described. This method includes the following preparation, assembly and joining steps.

(1) Preparing step In this preparing step, a plurality of constituent members forming the heat exchange section 3 are prepared. The plurality of components includes, in this embodiment, the plurality of partition plates 33, the plurality of fin plates 32, the plurality of side bars 34, and (in this embodiment) a pair of outer sheets 37. Each of the plurality of constituent members is configured to be capable of vacuum brazing in the joining step. Specifically, each of the plurality of constituent members includes a base material having a higher melting point than the brazing temperature for vacuum brazing in the joining step, and a base material laminated on the surface of the base material for the brazing. and a surface material having a melting point lower than the temperature.

The total number of the plurality of partition plates 33 and the plate thickness t33 of each of the partition plates 33 directly affect the stacking height (dimension in the stacking direction) h3 of the entire heat exchange section 3 . In addition, the plate thickness t33 of the partition plate 33 directly affects the ratio of the members excluding the spaces (that is, the first and second fluid flow paths 30a and 30b) in the inner portion 3b, that is, the density of the inner portion 3b. do. The lamination height h3 and plate thickness t33 will be described in detail later.

(2) Assembling Process In this assembling process, the heat exchanging portion assembly is assembled in the posture shown in FIG. 3, that is, the posture in which the stacking direction coincides with the vertical direction. Specifically, the plurality of partition plates 33 and the plurality of fin plates 32 are alternately laminated in the lamination direction, and both the width direction (horizontal direction in FIG. 3) of the plurality of fin plates 32 are stacked. The side bars 34 are arranged on the outside respectively. Preferably, a weight is placed on the heat exchanging assembly to hold the assembled state of the heat exchanging assembly.

(3) Joining step In this joining step, the heat exchange assembly is placed in a furnace for vacuum brazing in the posture shown in FIG. The parts that are heated so that they contact each other are joined together by vacuum brazing. The joining includes joining the top of each of the plurality of fin plates 32 to the adjacent partition plate 33 . By this bonding step, the plurality of constituent members are integrated with each other, and the heat exchange section 3 is completed.

The manufacturing method according to this embodiment further has the following features (A) and (B).

Feature (A): In the assembling process, the stacking height h3 of the heat exchange assembly is set to 1/2 or less of the allowable height of the furnace. The stacking height h3 is the dimension in the stacking direction of the heat exchange unit assembly (vertical dimension in FIG. 3), and the allowable height of the furnace is the heat that is allowed to enter the furnace. This is the maximum value of the stacking height h3 of the replacement part assembly.

Feature (B): The plate thickness t33 of the plurality of partition plates 33 prepared in the preparation step is set to 1.3 times or more the theoretical required plate thickness to (t33≧1.3to). The theoretically required plate thickness to is the minimum plate thickness that can be obtained based on the pressure of the fluid applied from the inside to each of the side bars 34, and the pressure is equal to the first and second fluid flow paths 30a. , 30b on the basis of the respective pressures P1, P2 of said first and second fluids F1, F2 flowing through said fluids F1, F2.

Both of the features (A) and (B) are caused by sudden changes in temperature or flow rate of the first and second fluids F1 and F2 flowing through the first and second fluid flow paths 30a and 30b. This makes it possible to reduce the large thermal stress generated at both ends of the heat exchange section 3 in the stacking direction (hereinafter referred to as "stacking direction both ends"). The reason is as follows.

When the first fluid F1 and the second fluid F2 are introduced into the heat exchanger HE, depending on the temperatures of these fluids F1 and F2, the plurality of constituent members (the partition plate 33, the fin plate 32, the side plates 33, Significant thermal deformation (thermal contraction or thermal expansion) can occur in the bar 34). At this time, there is a large difference in the speed of thermal deformation in the stacking direction between the outer portions 3a in which the plurality of side bars 34 are arranged in the stacking direction and the inner portion 3b positioned between the outer portions 3a. , which causes a large thermal stress. Specifically, the inner portion 3b is occupied by a large proportion of the first and second fluid flow paths 30a and 30b, which are spaces in which no constituent members exist, and the plurality of fin plates 32 forming these are thin and easily deformable. Therefore, compared to the outer portion 3a in which a plurality of side bars 34 each having a high rigidity are densely arranged in the stacking direction, the inner portion 3b is thermally deformed in the stacking direction at a higher speed following temperature changes. Therefore, there is a significant difference in the amount of thermal deformation in the stacking direction between the inner portion 3b and the outer portions 3a on both sides thereof. The difference in the amount of thermal deformation causes the partition plate 33 to be distorted (bent) in the stacking direction. That is, bending stress (thermal stress) is generated in the partition plate 33 .

Since the amount of thermal deformation is accumulated as the number of steps increases from the central position in the stacking direction (central position in the vertical direction in FIG. 3), the difference in the amount of thermal deformation increases with increasing distance from the central position. That is, the difference in the amount of thermal deformation becomes maximum at both ends of the heat exchanging portion 3 in the stacking direction (upper and lower ends in FIG. 3; hereinafter referred to as "stacking direction both ends"). Therefore, suppressing the stacking height h3 of the heat exchanging portion 3 as in the feature (A) reduces the difference in the amount of thermal deformation that is maximum at both ends in the stacking direction, thereby reducing the stacking direction. It makes it possible to prevent the occurrence of excessive thermal stress at both ends.

Normally, the stacking height h3 of the heat exchanging part 3 is set as large as possible within a range not exceeding the allowable height of the furnace. For example, if the permissible height is 1400 mm, the lamination height h3 is set to 1400 mm or slightly smaller. This makes it possible to maximize the throughput of one heat exchange section 3 and reduce the required number of heat exchangers HE. However, the feature (A) is caused by repeatedly generating a large thermal stress by setting the lamination height h3 to 1/2 or less of the allowable height (for example, 700 mm) contrary to conventional wisdom. It is possible to suppress shortening of the life of the heat exchanger HE.

Moreover, the difference between the amount of thermal deformation of the both outer portions 3a and the amount of thermal deformation of the inner portion 3b largely depends on the temperature followability of both, and the temperature followability also depends on the density difference between the two. Therefore, the density difference should be reduced, specifically, the thickness t33 of each partition plate 33 should be increased to increase the ratio of the partition plate 33 in the inner portion 3b as in the feature (B). , is also effective in suppressing thermal stress.

Normally, the plate thickness t33 of the partition plate 33 is set as small as possible within a range not less than the theoretically required plate thickness to. For example, when the theoretical required plate thickness to is 1.55 mm, the plate thickness t33 of the partition plate 33 is set to a dimension slightly larger than 1.55 mm (for example, 1.6 mm). This makes it possible to increase the ratio of the first and second fluid flow paths 30a, 30b in the inner portion 3b to increase the throughput of one heat exchanging section 3, thus increasing the need for the heat exchanger HE. It makes it possible to reduce the number of units. However, in the feature (B), the thickness t33 of the partition plate 33 is intentionally set to 1.3 times or more (for example, 2.4 mm) the theoretically required thickness to without prioritizing the economy of the heat exchanger itself. By doing so, it is possible to suppress shortening of the life of the heat exchanger HE due to repeated occurrence of large thermal stress.

As described above, the features (A) and (B) both reduce the processing capacity of one heat exchange unit 3 and increase the required number of heat exchangers HE. By supplying the first and second fluids F1 and F2 in parallel to the heat exchangers HE, it is possible to increase the number of heat exchangers HE and ensure the required throughput. For example, when the allowable height of the furnace is 1400 mm and the required number of heat exchangers H1 is three when the stacking height h3 of the heat exchange section 3 is set to be substantially equal to the allowable height, the If the stacking height h3 is intentionally suppressed to 700 mm, the required number of heat exchangers HE each including the heat exchange section 3 is doubled to six. By arranging them in parallel, it is possible to obtain a heat exchange system capable of ensuring the required throughput. That is, a step of manufacturing a plurality of heat exchange units 3 by the above-described manufacturing method, and determining the number of the heat exchange units 3 so that the processing amount of the entire heat exchange system satisfies a preset required processing amount. connecting a number of said heat exchanging sections 3 in parallel with each other, it is possible to produce a heat exchanging system capable of meeting said required throughput as a whole.

FIG. 4 shows an example of a heat exchange system manufactured in this way. This heat exchange system includes a plurality of (six in this example) heat exchangers HE each including the heat exchange section 3, the first fluid supply pipe 41, the first fluid discharge pipe 42, the first A two-fluid supply pipe 43 and the second fluid discharge pipe 44 are provided. The first fluid supply pipe 41 includes a first main supply pipe 41a connected to a supply source of the first fluid F1, and a first main supply pipe 41a branched from the first main supply pipe 41a to supply the heat exchangers HE. and a plurality of first sub-supply pipes 41b connected to the inlet header 21, and the first fluid discharge pipes 42 are connected to the respective first outlet headers 22 of the heat exchanger HE. It has one sub-discharge pipe 42b and a first main discharge pipe 42a connected to each of the plurality of first sub-discharge pipes 42b and guiding the first fluid F1 out of the system. Similarly, the second fluid supply pipe 43 includes a second main supply pipe 43a connected to the supply source of the second fluid F2, and a second main supply pipe 43a branched from the second main supply pipe 43a to supply the heat exchanger HE to each of the heat exchangers HE. and a plurality of second sub-supply pipes 43b connected to the second inlet headers 23 of the heat exchangers HE, and the second fluid discharge pipes 44 are connected to the respective second outlet headers 24 of the heat exchangers HE. It has a plurality of second sub-discharge pipes 44b, and a second main discharge pipe 44a connected to each of the plurality of second sub-discharge pipes 44b and guiding the second fluid F2 out of the system.

In addition, the fluids to be treated in the present invention are not limited to the first and second fluids F1 and F2. The present invention can also be applied to manufacture a heat exchange section of a heat exchanger that enables heat exchange between three or more types of fluids.

3 heat exchange part 3a outer part 3b inner part 30 fluid channel 30a first fluid channel 30b second fluid channel 32 fin plate 33 partition plate 34 side bar (closure member)
37 Outer sheet HE Heat exchanger h3 Lamination height t33 Partition plate thickness

Claims (2)

A heat exchange part of a plate-fin heat exchanger, comprising: a plurality of partition plates arranged in parallel with each other in a stacking direction; a plurality of fin plates arranged in the partition plate and brazed to the partition plate to form a plurality of fluid flow passages arranged in a width direction parallel to the partition plate between the partition plates; and the plurality of partition plates. and a plurality of blocking members arranged on both outer sides in the width direction of the plurality of fin plates so as to block the space formed between the partition plates adjacent to each other in the stacking direction. A method for manufacturing a
a preparing step of preparing the plurality of partition plates, the plurality of fin plates and the plurality of closing members;
The plurality of partition plates and the plurality of fin plates are alternately laminated in the lamination direction, and the blocking members are arranged on both outer sides of the plurality of fin plates in the width direction, thereby forming a heat exchange assembly. An assembly process for assembling a solid,
Each of the plurality of fin plates is vacuum brazed to the partition plate adjacent to the fin plate by heating the heat exchange unit assembly in a furnace with the stacking direction aligned with the vertical direction. a joining step of joining,
In the assembling step, the stacking height of the heat exchange unit assembly is set to 1/2 or less of the allowable height of the furnace ,
The plate fins , wherein the thickness of the plurality of partition plates prepared in the preparation step is set to 1.3 times or more of the theoretical required plate thickness calculated based on the pressure of the fluid flowing through the fluid flow channel. A method for manufacturing a heat exchange section of a heat exchanger. A method for manufacturing a heat exchange system comprising a plurality of heat exchange sections, wherein the heat exchange system comprises a plurality of heat exchange sections according to the method for manufacturing a heat exchange section of a plate-fin heat exchanger according to claim 1 . and determining the number of the heat exchange units constituting the heat exchange system so that the throughput of the entire heat exchange system satisfies a preset required throughput, and determining the number of the heat exchange units. connecting the sections in parallel with each other.

Images