WO2016072100A1

WO2016072100A1 - Heat exchanger

Info

Publication number: WO2016072100A1
Application number: PCT/JP2015/054289
Authority: WO
Inventors: 高橋　優
Original assignee: 住友精密工業株式会社
Priority date: 2014-11-06
Filing date: 2015-02-17
Publication date: 2016-05-12
Also published as: EP3217119B1; EP3217119A4; US20170328644A1; JP2016090157A; JP5847913B1; EP3217119A1

Abstract

This heat exchanger is provided with heat transfer members (10 and 20), each comprising: flow ports (11, 12, 21, and 22) through which a fluid (6 and 7) is introduced or discharged; a plurality of heat exchange passages (13 and 23); and connection channel parts (14 and 24) configured such that both ends thereof are connected to the flow port and the plurality of heat exchange passages (13 and 23). The connection channel parts are shaped like a tournament tree branching in two toward the heat exchange passages.

Description

Heat exchanger

The present invention relates to a heat exchanger, and more particularly to a heat exchanger including a heat transfer member in which a heat exchange passage and a connection passage portion are formed.

Conventionally, a heat exchanger including a heat transfer member in which a heat exchange passage and a connection passage portion are formed is known. Such a heat exchanger is disclosed in, for example, Japanese Patent Application Laid-Open No. 4-227482.

The above Japanese Patent Laid-Open No. 4-227481 includes a metal plate in which a fluid inlet portion, a plurality of heat exchange passages, and a connection passage portion for distributing fluid from the inlet portion to each heat exchange passage are provided. A plate fin heat exchanger is disclosed. Japanese Patent Laid-Open No. 4-227481 discloses a structure in which a large number of dot-shaped convex portions called dot cores are distributed in a distribution region connected in parallel with a large number of heat exchange passages as a connection passage portion. Has been. In the above-mentioned Japanese Patent Application Laid-Open No. 4-227481, the fluid dispersed in each dot core in the distribution area is distributed to each heat exchange passage.

Japanese Patent Laid-Open No. 4-227481

However, in the connection passage part of the above-mentioned Japanese Patent Application Laid-Open No. 4-227481, since the fluid dispersed by a large number of dot cores is distributed to each heat exchange passage, the flow rate of the fluid distributed to each heat exchange passage can be controlled. Without being random. Therefore, there is a problem that it is difficult to accurately suppress the flow rate variation in each heat exchange passage. If the flow rate of each heat exchange passage varies, the heat exchange performance varies from flow path to flow path, making it difficult to design a heat exchanger for obtaining the desired performance.

The present invention has been made to solve the above-described problems, and one object of the present invention is to provide a heat exchanger capable of accurately suppressing flow rate variations in a plurality of heat exchange passages. It is to be.

In order to achieve the above object, a heat exchanger according to the present invention includes a circulation port for introducing or deriving a fluid, a plurality of heat exchange passages for causing the fluid to exchange heat, and a plurality of heat exchanges at both ends and the circulation port. A heat transfer member including a connection passage portion connected to each of the passages is provided, and the connection passage portion has a tournament shape that branches two by two toward the heat exchange passage. The “tournament shape” of the present invention is a broad concept showing a branch shape that repeats two branches, and the shape and length of the branch portion and the number of branches are not limited. For this reason, the flow path that constitutes the connection passage section is not only a flow path that branches into two at right angles as in the so-called tournament table, but also branches in a curved shape such as an arc shape or in an oblique direction such as a Y shape. It may be a flow path.

In the heat exchanger according to the present invention, as described above, the connection passage portion is formed in a tournament shape that branches two by two toward the heat exchange passage. Thereby, when providing a connection channel | path part in the introduction side of a fluid, the fluid which goes in and out of a heat exchange channel can be divided | segmented 2 each, and it can distribute to each of several heat exchange channel | paths. Here, when branching (dividing) one flow path into three or more flow paths, the flow rate of each flow path is likely to vary due to uneven flow, etc. The distribution amount to each flow path can be easily equalized. Therefore, by repeating the two branches as many times as the number of heat exchange passages, it is possible to accurately control the flow rate variation of multiple heat exchange passages compared to a structure that distributes fluid to many heat exchange passages at once. can do.

In the heat exchanger according to the invention described above, preferably, the connection passage portion includes a pair of branch passages that branch into two from the branch source portion, and the branch source portion has a pair of branch passages with respect to the pair of branch passages. The connection is made in the direction in which the bisector of the angle formed extends. If comprised in this way, since a fluid can be made to flow toward the middle direction (direction where a bisector extends) of a pair of branch paths from a branch source part to each branch path, more evenly, Fluid can be distributed to each of the pair of branches. As a result, it is possible to more effectively suppress the flow rate variation of the plurality of heat exchange passages.

In this case, preferably, the branch path is a first part branched from the branch source part, and a second linear part as a branch source part extending from the first part and connected to the pair of branch paths on the heat exchange passage side. Part. According to this structure, when the fluid is allowed to flow from the upstream branch path to the downstream branch path, the fluid is supplied to the downstream branch path in a state where the flow direction is aligned by the linear second portion. Can flow in. As a result, since the fluid can flow into each of the downstream branch passages in a state where the flow direction is aligned toward the middle of the pair of branch passages, the fluid can be more evenly distributed.

In the heat exchanger according to the invention described above, preferably, the connection passage portion includes a pair of branch passages that branch into two from the branch source portion, and the pair of branch passages have the same passage length. If comprised in this way, since it can aim at equalization of channel resistance of a pair of bifurcated paths which branch into two, the amount of distribution of the fluid to a pair of branched paths can be made more equal. Then, by repeating the two branches with the same flow path length as many times as the number of heat exchange passages, it is possible to more effectively suppress the flow rate variation of each heat exchange passage.

In this case, preferably, the pair of branch paths are formed in a symmetrical shape with the branch source portion interposed therebetween. If comprised in this way, since the same branch path can be branched symmetrically, the flow-path resistance of a pair of branch path can be equalized more reliably. As a result, it is possible to further suppress flow rate variations in the plurality of heat exchange passages.

In the configuration in which the pair of branch paths are formed in a symmetrical shape, preferably, the pair of branch paths are branched from the branch source portion so as to form a semi-elliptical shape. With this configuration, the flow of the semi-elliptical channel is in the tangential direction of the elliptic curve. Therefore, after the pair of branch paths are branched from the branching source portion in the lateral direction with respect to the flow from the upstream side. The fluid flow can be gradually directed downstream along the semi-ellipse. As a result, the fluid flow can be made closer to the downstream direction so that the fluid can be evenly distributed.

In this case, it is preferable that the pair of branch paths are branched in an arc shape from the branch source portion so as to form a semicircular shape. If comprised in this way, after making a branch path branch from a branch origin part to a horizontal direction, the flow of a fluid can be gradually directed to a downstream direction along a circular arc. Further, since the branch path does not bend sharply after branching at the branch source part, the channel resistance is unlikely to increase. As a result, the flow of the fluid can be made closer to the downstream direction so that the fluid can be evenly distributed while suppressing an increase in the channel resistance.

According to the present invention, as described above, flow rate variations in a plurality of heat exchange passages can be accurately suppressed.

It is the schematic diagram which looked at the heat exchanger by 1st Embodiment of this invention from the upper surface side. It is the schematic diagram which looked at the heat exchanger by 1st Embodiment of this invention from the side surface side. FIG. 3A is a plan view showing a first heat transfer member of the heat exchanger according to the first embodiment of the present invention. FIG. 3B is a plan view showing a second heat transfer member of the heat exchanger according to the first embodiment of the present invention. It is the enlarged plan view which showed the connection channel | path part of the 1st heat-transfer member. It is the schematic diagram which showed the connection channel | path part by a comparative example. It is the figure which showed the flow volume simulation result of the connection channel | path part by a comparative example. It is the figure which showed the flow simulation result of the connection channel | path part in the heat exchanger by 1st Embodiment. It is the schematic diagram which showed the flow velocity vector in the connection channel | path part of the heat exchanger by 1st Embodiment. It is the schematic diagram which showed the flow velocity vector of the connection channel | path part by a comparative example. It is the top view which showed the connection channel | path part of the heat exchanger by 2nd Embodiment of this invention. It is the enlarged plan view which showed the detailed structure of the connection channel | path part of the heat exchanger by 2nd Embodiment of this invention. It is the figure which showed the flow rate simulation result of the connection channel | path part in the heat exchanger by 2nd Embodiment. It is the schematic diagram which showed the 1st modification of the connection channel | path part of the heat exchanger by 1st Embodiment. It is the schematic diagram which showed the flow velocity vector at the time of lengthening the 2nd part of the connection channel | path part of 1st Embodiment. It is the schematic diagram which showed the 2nd modification of the connection channel | path part of the heat exchanger by 1st Embodiment.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(First embodiment)
First, the configuration of the heat exchanger 100 according to the first embodiment will be described with reference to FIGS.

The heat exchanger 100 is a plate heat exchanger. As shown in FIGS. 1 and 2, the heat exchanger 100 includes a core 1 and header portions 2 to 5 (see FIG. 2). The core 1 includes a plurality of first heat transfer members 10 through which the first fluid 6 flows and a plurality of second heat transfer members 20 through which the second fluid 7 flows. The core 1 is a heat exchange unit that performs heat exchange between the first fluid 6 flowing through the first heat transfer member 10 and the second fluid 7 flowing through the second heat transfer member 20. Both the first fluid 6 and the second fluid 7 are examples of the “fluid” of the present invention. The first heat transfer member 10 and the second heat transfer member 20 are both examples of the “heat transfer member” of the present invention.

In the first embodiment, the first fluid 6 is a gas on the high temperature side, and the second fluid 7 is a liquid on the low temperature side. Note that the first fluid 6 and the second fluid 7 may be either on the high temperature side, or may be either gas or liquid. In FIGS. 1 and 2, white arrows indicate the flow direction of the first fluid 6, and hatched arrows indicate the flow direction of the second fluid 7.

The core 1 is configured by alternately laminating a plurality of plate-like first heat transfer members 10 and a plurality of plate-like second heat transfer members 20. Further, side plates 8 are respectively provided at both ends of the core 1 in the stacking direction (Z direction). The core 1 is formed by sandwiching alternately laminated first heat transfer members 10 and second heat transfer members 20 by a pair of side plates 8 and joining them by fastening, diffusion bonding, brazing, or the like using fastening members. The whole is formed in a rectangular box shape (cuboid shape). The first heat transfer member 10 and the second heat transfer member 20 are made of a metal material having high heat conductivity. The first heat transfer member 10 and the second heat transfer member 20 are formed with flow paths for allowing the first fluid 6 and the second fluid 7 to circulate, respectively. Detailed configurations of the first heat transfer member 10 and the second heat transfer member 20 will be described later. In FIG. 1, the side plate 8 on the upper surface, the first heat transfer member 10, and the second heat transfer member 20 are illustrated by being separated by a broken line. Below, let the lamination direction of the 1st heat-transfer member 10 and the 2nd heat-transfer member 20 shown in FIG. 2 be a Z direction. Further, as shown in FIG. 1, the longitudinal direction of the core 1 when viewed from the Z direction is the X direction, and the short direction of the core 1 is the Y direction.

The header part 2 is an inlet flow path of the second fluid 7 for allowing the second fluid 7 to flow into the core 1 (second heat transfer member 20). The header part 3 is an outlet channel for the second fluid 7 that causes the second fluid 7 to flow out of the core 1 (second heat transfer member 20). The

header parts

2 and 3 are attached to the surface of one side (Z1 side) of the core 1, the header part 2 is arranged in the vicinity of the X1 side end part, and the header part 3 is arranged in the vicinity of the X2 side end part. . The

header portions

2 and 3 are both cylindrical tube members. The

header portions

2 and 3 are connected to the introduction path 91 and the outlet path 92 for the second fluid 7 with respect to the plurality of second heat transfer members 20, respectively. The header part 2 causes the second fluid 7 to flow into the plurality of second heat transfer members 20 in a lump, and the header part 3 causes the second fluid 7 to flow out from the plurality of second heat transfer members 20 at a time. Let

The header part 4 is an inlet flow path of the first fluid 6 for allowing the first fluid 6 to flow into the core 1 (first heat transfer member 10). The header portion 5 is an outlet flow path for the first fluid 6 that causes the first fluid 6 to flow out of the core 1 (the first heat transfer member 10). The

header portions

4 and 5 are attached to the other surface (Z2 side) of the core 1, the header portion 4 is disposed in the vicinity of the X2 side end portion, and the header portion 5 is disposed in the vicinity of the X1 side end portion. . The

header parts

4 and 5 are both cylindrical tube members. The

header parts

4 and 5 are respectively connected to an introduction path 93 and an outlet path 94 for the first fluid 6 with respect to the plurality of first heat transfer members 10. The header portion 4 causes the first fluid 6 to flow into the plurality of first heat transfer members 10 at once, and the header portion 5 causes the first fluid 6 to flow out from the plurality of first heat transfer members 10 at once. Let

The first fluid 6 is introduced into each first heat transfer member 10 from the header portion 4 on the X2 side, flows in the flow path of the first heat transfer member 10 in the X1 direction, and from the header portion 5 on the X1 side. leak. The second fluid 7 is introduced into each second heat transfer member 20 from the header portion 2 on the X1 side, flows in the flow path of the second heat transfer member 20 in the X2 direction, and from the header portion 3 on the X2 side. leak. As a result, the first heat transfer member 10 and the second heat transfer between the first fluid 6 flowing in the first heat transfer member 10 in the X1 direction and the second fluid 7 flowing in the second heat transfer member 20 in the X2 direction. Heat exchange via the heat member 20 is performed. Thus, the heat exchanger 100 of 1st Embodiment is comprised as a counterflow type heat exchanger. In the first embodiment, the first fluid 6 on the high temperature side is cooled by the second fluid 7 on the low temperature side, and is taken out from the header portion 5 in a state where the temperature has dropped. The second fluid 7 functions as a coolant for the first fluid 6.

Next, detailed configurations of the first heat transfer member 10 and the second heat transfer member 20 will be described.

As shown in FIG. 3A, the first heat transfer member 10 is a metal plate-like member including an inlet port 11 and an outlet port 12, a plurality of heat exchange passages 13, and a connection passage portion 14. . The introduction port 11 and the outlet 12 are examples of the “distribution port” in the present invention. The plurality of heat exchange passages 13 and the connection passage portions 14 are groove-like passages that are integrally formed with the first heat transfer member 10. The heat exchange passage 13 is a linear flow path provided for exchanging heat with the fluid, and is provided so as to extend in the X direction and to be arranged in parallel to the Y direction. In the first embodiment, 32 heat exchange passages 13 are formed. The number of heat exchange passages 13 may be an even number and may be other than 32.

Both the inlet 11 and the outlet 12 are circular through holes that penetrate the first heat transfer member 10 in the thickness direction. The introduction port 11 is disposed in the vicinity of the end portion of the first heat transfer member 10 on the X2 direction side, and the outlet port 12 is disposed in the vicinity of the end portion of the first heat transfer member 10 on the X1 direction side. The introduction port 11 and the outlet port 12 are each connected to the connection passage portion 14 via a plurality (four) of communication passages 15. The inlet 11 is provided to introduce the first fluid 6 into the flow path, and the outlet 12 is provided to lead out the first fluid 6 from the flow path. Note that through holes 9b (see FIG. 3B) similar to the inlet port 11 and the outlet port 12 are also provided at corresponding positions of the second heat transfer member 20, respectively. Therefore, the respective inlets 11 and through holes 9b of the stacked first heat transfer member 10 and second heat transfer member 20 are connected in the thickness direction (Z direction), and penetrate the core 1 in the Z direction as a whole. An introduction path 93 (see FIG. 2) is configured. Similarly, each lead-out port 12 and the through-hole 9b are connected to constitute a lead-out path 94 (see FIG. 2) that penetrates the core 1 in the Z direction as a whole. The Z2 side plate 8 (see FIG. 2) is also provided with a through hole to connect the

header portions

4 and 5 to the introduction path 93 and the lead-out path 94.

A plurality of connection passage portions 14 are provided between the inlet 11 and the plurality of heat exchange passages 13 and between the outlet 12 and the plurality of heat exchange passages 13, respectively. The number of connection passage portions 14 corresponds to the number of heat exchange passages 13, and in the first embodiment, four connection passage portions 14 are provided on the introduction port 11 side and the discharge port 12 side, respectively. Since the structure of the connection passage portion 14 is common to the introduction port 11 side and the outlet port 12 side, only the connection passage portion 14 of the introduction port 11 will be described. The four connection passage portions 14 have the same structure.

Both ends of the connection passage portion 14 are connected to the introduction port 11 (communication passage 15) and the plurality of heat exchange passages 13, respectively, and the function of distributing the first fluid 6 from the introduction port 11 to each heat exchange passage 13 is provided. Have In the first embodiment, the connection passage portion 14 has a tournament shape that branches two by two toward the heat exchange passage 13.

Specifically, as shown in FIG. 4, the connection passage portion 14 is branched into three stages of a first stage 31, a second stage 32, and a third stage 33, and one flow path (communication path 15). ) Is finally branched into eight channels. Then, the four connection passage portions 14 are branched into eight pieces and connected to the 32 heat exchange passages 13 respectively. In the first embodiment, the connection passage portion 14 includes a pair of branch passages 34 that branch from the branch source portion 35 (second portion 37 or communication passage 15 described later) into two. Therefore, one pair of the branch paths 34 is provided in the first stage 31, two sets in the second stage 32, and four sets in the third stage 33. The branch path 34 of the first stage 31 is bifurcated with the end of the communication path 15 as the branch source portion 35. The branch path 34 after the second stage 32 is bifurcated with a later-described second portion 37 as a branch source portion 35. In the entire connection passage portion 14, the dimension in the X direction is L1.

The pair of branch paths 34 branch from the branch source portion 35 to both sides in the Y direction. The pair of branch paths 34 have the same channel length. More specifically, the pair of branch paths 34 are formed in a symmetrical shape with the branch source portion 35 interposed therebetween. That is, the pair of branch paths 34 is symmetrical in the Y direction with the branch source portion 35 as the center. Further, the flow path widths W1 of the pair of branch paths 34 are the same, and although not shown, the pair of branch paths 34 have the same channel cross-sectional area. 4 shows an example in which the connection passage portion 14 has a constant flow path width W1 and a constant flow path cross-sectional area throughout.

Here, it is preferable that the pair of branch paths 34 are branched from the branch source portion 35 so as to form a semi-elliptical shape. In the first embodiment, the pair of branch paths 34 are branched from the branch source portion 35 in an arc shape so as to form a semicircular shape which is a kind of semi-elliptical shape. Therefore, the pair of branch paths 34 branch from the branch source part 35 in the Y1 direction and the Y2 direction, which are tangential directions, extend so as to form a ¼ arc, and are along the X1 direction at the end of the arc. More specifically, each branch path 34 includes a first portion 36 and a second portion 37 that is continuous with the first portion 36.

The first part 36 of the pair of branch paths 34 is a flow path branched from the branch source part 35, and is a 1/4 arc-shaped part. In each of the first stage 31, the second stage 32, and the third stage 33, the radius of the first portion 36 is a radius R1, a radius R2, and a radius R3, respectively. The radius R1 is larger than (R2 + R3). The radius R2 is larger than the radius R3.

The second portion 37 of the pair of branch paths 34 extends from the first portion 36 and is connected to the pair of branch paths 34 on the heat exchange passage 13 side (X1 side in FIG. 4) as a straight flow as a branch source portion. Road. That is, the second portion 37 of the branch path 34 of the first stage 31 is connected to the branch path 34 of the second stage 32 as the branch source part 35, and the second portion 37 of the branch path 34 of the second stage 32 is the third stage. A branch source portion 35 is connected to 33 branch paths 34. Note that the branch passage 34 of the third stage 33 is connected to the linear heat exchange passage 13 at the end on the heat exchange passage 13 side, and does not include the second portion 37. The second portion 37 is an example of the “branch source portion” in the present invention.

The second portion 37 of each branch path 34 extends linearly along the X direction. In other words, the second portion 37 extends in parallel with the heat exchange passage 13. The length of the second portion 37 is substantially equal between the first step 31 and the second step 32, and any second portion 37 has a length L2. The X direction dimension (length) L2 of the second portion 37 is smaller than the X direction dimension (R1, R2 or R3) of the first portion 36. In the example of FIG. 4, the length L2 is about 1/9 of R1 and about 1/5 of R2. The length of the second part 37 may be different between the first stage 31 and the second stage 32, but the length of the plurality of second parts 37 included in the same stage is preferably the same.

Here, in the first embodiment, the branching source portion 35 is connected to the pair of branch paths 34 in the direction in which the bisector BS of the angle θ formed by the pair of branch paths 34 extends. That is, in FIG. 4, the first portion 36 of the pair of branch paths 34 branches in the Y1 direction and the Y2 direction, which are tangential directions, so the angle θ formed by the pair of branch paths 34 is 180 degrees. On the other hand, the branch source portion 35 (second portion 37, communication path 15) extends linearly in the X1 direction and is connected to the pair of branch paths 34 from the upstream side. Therefore, the branching source portion 35 is connected to the pair of branch paths 34 at 90 degrees perpendicular to the tangential direction of the first portion 36, and the angle θ (180 degrees) formed by the pair of branch paths 34 is 2 etc. The branch line 34 is connected in the direction (X1 direction) in which the branch line BS extends. Further, the tangent line of the inner wall portion (inner wall point) 34 a facing the branch source portion 35 is a vertical line orthogonal to the branch source portion 35.

With the above configuration, in the first heat transfer member 10, as shown in FIG. 3A, the first fluid 6 that has flowed from the introduction port 11 flows into the connection passage portions 14 through the communication passages 15. . In each connection passage portion 14, the first fluid 6 is divided into eight parts in three stages and flows into eight corresponding heat exchange passages 13. The first fluid 6 cooled by passing through the heat exchange passage 13 flows into the respective connection passage portions 14 on the downstream side and merges from eight to one, and then is led out via the communication passage 15 on the downstream side. 12 flows out.

As shown in FIG. 3B, the second heat transfer member 20 is a metal plate-like member including an inlet port 21 and an outlet port 22, a plurality of heat exchange passages 23, and a plurality of connection passage portions 24. It is. The introduction port 21 and the outlet port 22 are examples of the “distribution port” in the present invention.

The introduction port 21 is disposed in the vicinity of the end portion of the second heat transfer member 20 on the X1 direction side, and the outlet port 22 is disposed in the vicinity of the end portion of the second heat transfer member 20 on the X2 direction side. The introduction port 21 and the lead-out port 22 are respectively arranged at positions shifted from the through hole 9b to the outside in the X direction. And the through-hole 9a (refer FIG. 3 (A)) similar to the inlet 21 and the outlet 22 is also provided in the corresponding position of the 1st heat-transfer member 10, respectively. Thereby, each through-hole 9a and the introduction port 21 of the 1st heat-transfer member 10 and the 2nd heat-transfer member 20 are connected to the thickness direction (Z direction), and the introduction path 91 which penetrates the core 1 to the Z direction as a whole. (See FIG. 2). Similarly, each lead-out port 22 and the through-hole 9a are connected to constitute a lead-out path 92 (see FIG. 2) that penetrates the core 1 in the Z direction as a whole.

In the first embodiment, the configuration of the second heat transfer member 20 is basically the same as the configuration of the first heat transfer member 10 except for the positions of the inlet port 21 and the outlet port 22 (and the position of the through

hole

9a or 9b). The same. Therefore, the configuration of each connection passage portion 24 of the second heat transfer member 20 is the same as the configuration of the connection passage portion 14 of the first heat transfer member 10. Therefore, the detailed description about the structure of the 2nd heat-transfer member 20 is abbreviate | omitted.

In the second heat transfer member 20 having such a configuration, the second fluid 7 that has flowed from the introduction port 21 flows into the corresponding heat exchange passages 23 through the respective connection passage portions 24. The second fluid 7 that has been heated through the heat exchange passage 23 (has deprived of heat) flows into the respective connection passage portions 24 on the downstream side and flows out from the outlet port 22.

The first heat transfer member 10 and the second heat transfer member 20 are configured as described above.

In the first embodiment, the following effects can be obtained.

In the first embodiment, as described above, the connection passage portion 14 (24) is formed in a tournament shape that branches two by two toward the heat exchange passage 13 (23). Accordingly, in the connection passage portion 14 (24), the first fluid 6 (second fluid 7) entering and exiting the heat exchange passage 13 (23) is divided into two parts, and each of the plurality of heat exchange passages 13 (23). Can be distributed. Here, when branching (dividing) one flow path into three or more flow paths, the flow rate of each flow path is likely to vary due to uneven flow, etc. The distribution flow rate to each flow path can be easily equalized. Therefore, a structure in which the first fluid 6 (second fluid 7) is distributed to many heat exchange passages 13 (23) at a time by repeating two branches as many times as the number of heat exchange passages 13 (23). Compared with, the flow rate variation of the plurality of heat exchange passages 13 (23) can be suppressed with high accuracy.

Further, in the first embodiment, as described above, the connection passage portion 14 (24) is provided with a pair of branch paths 34 that branch from the branch source portion 35 into two. The branching source portion 35 is configured to be connected to the pair of branch paths 34 in the direction in which the bisector BS of the angle θ formed by the pair of branch paths 34 extends. Accordingly, the first fluid 6 (second fluid 7) is caused to flow from the branching source portion 35 to the respective branch paths 34 toward the middle direction of the pair of branch paths 34 (the direction in which the bisector BS extends). Therefore, the first fluid 6 (second fluid 7) can be distributed to each of the pair of branch paths 34 more evenly. As a result, flow rate variations in the plurality of heat exchange passages 13 (23) can be more effectively suppressed.

In the first embodiment, as described above, the first portion 36 branched from the branching source portion 35 and the pair of branch passages 34 extending from the first portion 36 and connected to the heat exchange passage 13 (23) side are connected. A straight second portion 37 as a branch source portion is provided in the branch path 34. Thus, when the first fluid 6 (second fluid 7) flows from the upstream branch path 34 to the downstream branch path 34, the flow direction is aligned by the linear second portion 37. The first fluid 6 (second fluid 7) can flow into the downstream branch path 34. As a result, the first fluid 6 (second fluid 7) can be caused to flow into each of the downstream branch passages 34 in a state where the flow direction is aligned toward the middle of the pair of branch passages 34. The first fluid 6 (second fluid 7) can be evenly distributed.

In the first embodiment, as described above, the pair of branch paths 34 are formed so as to have the same flow path length. As a result, the flow resistance of the pair of branch paths 34 branched into two can be made uniform, so that the distribution amount of the first fluid 6 (second fluid 7) to the pair of branch paths 34 is further equalized. be able to. Then, by repeating the two branches with the same flow path length as many times as the number of heat exchange passages 13 (23), it is possible to more effectively suppress the flow rate variation of each heat exchange passage 13 (23). .

In the first embodiment, as described above, the pair of branch paths 34 are formed in a symmetrical shape with the branch source portion 35 interposed therebetween. Thereby, since the same branch path 34 can be branched symmetrically, the channel resistance of a pair of branch paths 34 can be equalized more reliably. As a result, the flow rate variation of the plurality of heat exchange passages 13 (23) can be further suppressed.

In the first embodiment, as described above, the pair of branch paths 34 are branched from the branch source portion 35 so as to form a semi-elliptical shape. As a result, the flow of the first fluid 6 (second fluid 7) gradually flows along the semi-ellipse after the pair of branch paths 34 are branched from the branch source portion 35 in the lateral direction with respect to the flow from the upstream side. Can be directed downstream. As a result, the flow of the first fluid 6 (second fluid 7) can be made closer to the downstream direction so that the first fluid 6 (second fluid 7) can be evenly distributed.

Further, in the first embodiment, as described above, the pair of branch paths 34 are respectively branched from the branch source portion 35 in an arc shape so as to form a semicircular shape. As a result, the flow of the arc-shaped flow path is in the tangential direction of the arc, and therefore the flow of the first fluid 6 (second fluid 7) is arced after the branch path 34 is branched laterally from the branch source portion 35. Can be gradually directed downstream. Further, since the branch path 34 does not bend sharply after branching at the branch source part 35, the flow path resistance is unlikely to increase. As a result, the flow of the first fluid 6 (second fluid 7) is made closer to the downstream direction so that the first fluid 6 (second fluid 7) can be evenly distributed while suppressing an increase in flow path resistance. be able to.

(Explanation of simulation results)
Next, referring to FIGS. 5 to 9, the effect of the connection passage portion 14 of the first heat transfer member 10 (the connection passage portion 24 of the second heat transfer member 20) in the heat exchanger 100 according to the first embodiment. A simulation result performed for confirming the above will be described. In the simulation, the flow rate of the first fluid 6 for each of 32 flow paths (channels) flowing out from the connection passage portion 14 was calculated by flowing the first fluid 6 at a predetermined flow rate into the connection passage portion 14. Moreover, the same calculation was performed also about the connection channel | path part 50 by the comparative example shown in FIG. 5, and the flow volume dispersion | variation in each connection channel | path part was compared.

First, the structure of the connection passage portion 50 according to the comparative example shown in FIG. 5 will be described. The connection passage part 50 of the comparative example branches the first fluid 6 from the communication passage 15 six at a time. In the comparative example, five sets of the six-branch connection passage portions 50 are provided to constitute 30 flow paths (channels). Each connection passage portion 50 includes a branch portion 52 that extends linearly on both sides in the Y direction from the connection portion 51 with the communication passage 15 and an individual portion 53 that extends linearly from the branch portion 52 in the X1 direction. In the branch portion 52, the connection portion 51 of the communication path 15 is disposed at the center in the Y direction. The individual portions 53 are arranged at equal intervals in the Y direction.

FIG. 6 shows a simulation result of the connection passage portion 50 according to the comparative example, and FIG. 7 shows a simulation result of the connection passage portion 14 according to the first embodiment. In each figure, the horizontal axis indicates the flow path number (channel number), and the vertical axis indicates the flow rate of the first fluid 6. In the first embodiment, since the four connection passage portions 14 have a total of 32 flow paths, there are 1 to 32 channels in order from the Y1 direction side in FIG. The vertical axis represents the ratio when the average value of all channels is 100%. The simulation was performed under the condition that the first fluid 6 was supplied from the inlet 11 at a mass flow rate of 1.0 × 10 ⁻³ Kg / s.

In the connection passage portion 50 of the comparative example shown in FIG. 6, the flow rate for each channel varies greatly in the range VR1 of about 0% to about 180%. Further, in the connection passage portion 50 of the comparative example, a group having a relatively small flow rate (

channels

3, 4, 9, 10, 15, 16, etc.) and a group having a relatively large flow rate (

channels

1, 6, 7, 12, 13, 18, etc.).

On the other hand, as shown in FIG. 7, in the connection passage portion 14 of the first embodiment, the variation in the flow rate for each channel is remarkably reduced. The flow rate of each channel is within a range VR2 of about 20% above and below, centering on the average value of 100%.

FIG. 8 is a diagram showing a velocity vector of the first fluid 6 passing through the pair of branch paths 34 (first stage 31) in the connection passage portion 14 according to the first embodiment. FIG. 9 is a diagram showing a velocity vector of the first fluid 6 passing through the connection passage portion 50 according to the comparative example. In each figure, the velocity vector at an arbitrary position in the flow path is shown as a representative point, and the length of the vector indicates the magnitude of the velocity.

As shown in FIG. 8, in the connecting passage portion 14 of the first embodiment, it can be seen that the distribution of velocity vectors is symmetrical between the pair of branch paths 34 and there is little variation. In addition, it can be seen that the velocity vector extends approximately in the tangential direction in the first portion 36 of each branch path 34 and the direction of the velocity vector changes in the second portion 37 so as to approach the X direction. For this reason, the second stage 32 and the subsequent results are similar. As a result, as shown in FIG.

As shown in FIG. 9, in the connection passage portion 50 of the comparative example, the flow of the first fluid 6 proceeds to both ends in the Y direction at the branch portion 52, and concentrated on the individual portions 53 at both ends in the Y direction. It can be seen that the fluid 6 is flowing in. As a result, the first fluid 6 hardly flows into the central individual portion 53. For this reason, as shown in FIG. 6, in the connection passage portion 50, the flow rate increases in the channels (

channels

1, 6, etc.) at both ends in the Y direction, and the flow rate decreases in the center channels (

channels

3, 4, etc.). became.

From the above, the effect of equalizing the distribution flow rate to each flow path by the connection passage portion 14 (24) of the heat exchanger 100 according to the first embodiment was confirmed. Thereby, it was confirmed that the flow volume dispersion | variation of the several heat exchange channel | path 13 (23) distributed by the connection channel | path part 14 (24) can be suppressed accurately.

(Second Embodiment)
Next, a second embodiment will be described with reference to FIGS. 10 and 11. In the second embodiment, unlike the first embodiment in which the heat exchanger 100 is provided with the connection passage portion 14 having the arc-shaped branch passage 34, the connection passage portion 114 having the branch passage 134 that branches in a Y shape. An example of the heat exchanger 200 provided with the above will be described.

In addition, the heat exchanger 200 of 2nd Embodiment differs from the said 1st Embodiment only in the connection channel | path part 114, and the other structure of the heat exchanger 200 is the same as that of the said 1st Embodiment. For this reason, the same components as those in the first embodiment are denoted by the same reference numerals, description thereof is omitted, and only the connection passage portion 114 will be described. Moreover, only the example which provided the connection channel | path part 114 in the 1st heat transfer member is demonstrated here, and description is abbreviate | omitted about the 2nd heat transfer member.

As shown in FIG. 10, the connection passage portion 114 of the second embodiment has a tournament shape that branches two by two toward the heat exchange passage 13 as in the first embodiment. Also in the second embodiment, the connection passage portion 114 branches in three stages and is connected to the 32 heat exchange passages 13. In the second embodiment, the connection passage portion 114 includes a pair of branch paths 134 that are bifurcated into a Y shape.

As shown in FIG. 11, the pair of branch paths 134 branches from a common branch source portion 135 in a Y shape (reverse Y shape) on both sides in the Y direction. The pair of branch paths 134 have the same channel length, and are formed symmetrically with the branch source portion 135 interposed therebetween. Further, the channel width W2 of the pair of branch paths 134 is the same. In the second embodiment, the entire flow path of the connection passage portion 114 has a flow path width W2, and has the same flow path cross-sectional area.

Each of the pair of branch paths 134 includes a first portion 136 that branches obliquely from the branch source portion 135 in the Y direction and the X1 direction, and a linear second portion 137 that continues to the first portion 136. Yes. The second portion 137 is an example of the “branch source portion” in the present invention.

The first portion 136 of the pair of branch paths 134 extends linearly obliquely from the branch source portion 135. A Y-shaped branch is formed by the first portion 136 of each of the pair of branch paths 134 and the upstream second portion 137 which is the branching source portion 135. The angle θ formed by the pair of first portions 136 is about 120 degrees. In each of the first stage 31, the second stage 32, and the third stage 33, the X-direction dimensions of the first portions 136 are L3, L4, and L5, respectively. The Y direction dimensions of each first portion 136 are W3, W4, and W5, respectively. In each first portion 136, lengths L3, L4, and L5 in the X direction are smaller than lengths W3, W4, and W5 in the Y direction, respectively. Therefore, when W3, W4, and W5 are equal to R1, R2, and R3 (see FIG. 4), the branch path 134 of the second embodiment is dimensioned in the X direction compared to the branch path 34 of the first embodiment. Can be reduced. As a result, the connection passage portion 114 of the second embodiment can have a smaller X-direction dimension L6 than the connection passage portion 14 of the first embodiment.

The second portion 137 of the pair of branch paths 134 is a linear flow path and extends along the X direction. The second part 137 of the first stage 31 has a length L7, and the second part 137 of the second stage 32 has a length L8. The length L7 is larger than the length L8. The length L7 is about 1/8 of W3. The length L8 is about 1/5 of W4.

Further, the branching source portion 135 is connected to the pair of branch paths 134 in the direction in which the bisector BS of the angle θ formed by the pair of branch paths 134 extends. That is, with respect to the angle θ formed by the pair of branch paths 134 (first portion 136) = about 120 degrees, the branch source portion 135 (second portion 137, communication path 15) is divided into two equal parts of the pair of branch paths 134. The line BS is connected in the extending direction (X1 direction). For this reason, the inner wall part 134 a facing the branching source part 135 is a triangular wall of about 120 degrees with respect to the branching source part 135. For this reason, compared with the inner wall part 34a of the said 1st Embodiment which is a 180 degree | times wall, it is possible to reduce flow path resistance by the part which the inner wall part 134a has an angle.

Other configurations of the second embodiment are the same as those of the first embodiment.

Also in the second embodiment, similarly to the first embodiment, by forming the connection passage portion 114 in a tournament shape that branches two by two toward the heat exchange passage 13, the distribution flow rate to each flow path is easy. Can be equalized. Therefore, by repeating the two branches as many times as the number of heat exchange passages 13, the flow rate variation of the plurality of heat exchange passages 13 can be accurately suppressed.

(Explanation of simulation results)
Next, with reference to FIG. 12, the simulation result performed in order to confirm the effect of the connection channel | path part 114 in the heat exchanger 200 by 2nd Embodiment is demonstrated. The contents of the simulation are the same as in the first embodiment.

As shown in FIG. 12, in the connection passage portion 114 of the second embodiment, some of the 32 channels show values higher than 150%, but most of the others are from the average value of 100%. It is within the range of ± 50% (hatched part). That is, 26 out of 32 channels (about 72%) are within an average value ± 50%.

Compared with the connection passage portion 50 according to the comparative example of FIG. 6, in the comparative example, 10 out of 30 channels (about 33%) are only within the range of the average value ± 50%. Thereby, the effect which equalizes the distribution flow volume to each flow path by the connection passage part 114 of the heat exchanger 200 by 2nd Embodiment was confirmed. As a result, it was confirmed that the flow rate variation of the plurality of heat exchange passages 13 distributed by the connection passage portion 114 can be accurately suppressed.

Note that, in comparison with the connection passage portion 14 according to the first embodiment of FIG. 7, in the first embodiment, all 32 channels are within the range of the average value ± 50%. For this reason, in the second embodiment, the X-direction dimension L6 (see FIG. 11) of the connection passage portion 114 can be reduced as compared with the first embodiment. On the other hand, in terms of equalizing the distribution flow rate, It can be seen that the first embodiment is more effective.

In addition, it should be thought that embodiment disclosed this time is an illustration and restrictive at no points. The scope of the present invention is shown not by the above description of the embodiment but by the scope of claims for patent, and further includes all modifications (modifications) within the meaning and scope equivalent to the scope of claims for patent.

For example, in the first and second embodiments, the example of the counterflow type heat exchanger 100 (200) in which the first fluid 6 and the second fluid 7 flow in opposite directions to each other in the X direction has been described. The invention is not limited to this. In the present invention, the heat exchanger is a parallel flow type in which the first fluid 6 and the second fluid 7 flow in the same direction, or a cross flow in which the flow of the first fluid 6 and the flow of the second fluid 7 intersect. It may be a mold or the like.

Moreover, although the said 1st and 2nd embodiment showed the example which comprised the core 1 by laminating | stacking the some 1st heat-transfer member 10 and the some 2nd heat-transfer member 20 alternately, this invention was shown. Is not limited to this. In the present invention, the first heat transfer member and the second heat transfer member are not necessarily stacked alternately. For example, along the Z direction, the first heat transfer member, the second heat transfer member, the second heat transfer member, the first heat transfer member,... Alternatively, two (multiple) layers of the second heat transfer member may be laminated. Conversely, one layer of the second heat transfer member may be laminated on the two layers (multiple layers) of the first heat transfer member.

Moreover, in the said 1st and 2nd embodiment, although the example which provided the tournament-shaped connection channel | path part 14 (114) in both the 1st heat-transfer member 10 and the 2nd heat-transfer member 20 was shown, this invention is shown. It is not limited to this. In the present invention, a tournament-shaped connection passage portion may be provided in only one of the first heat transfer member and the second heat transfer member, and a tournament-shaped connection passage portion may not be provided in the other.

In the first and second embodiments, the first heat transfer member 10 and the second heat transfer member 20 are provided, and an example of a heat exchanger that performs heat exchange between two kinds of fluids is shown. Is not limited to this. In the present invention, the heat exchanger may perform heat exchange between three or more types of fluids. In that case, what is necessary is just to provide 3 or more types of heat-transfer members, such as a 3rd heat-transfer member. At that time, each of the three or more types of heat transfer members may include a tournament-shaped connection passage portion.

In the first and second embodiments, the tournament-shaped connecting passage portion 14 (114) is branched into three stages and finally branched into eight flow paths. It is not limited to this. The number of stages of the connection passage portion (that is, the number of branches) is not particularly limited. The connecting passage portion may be branched into two stages or four or more stages.

Moreover, in the said 1st and 2nd embodiment, the example which provided the four connection channel | path parts 14 (114) finally branched to eight flow paths corresponding to the 32 heat exchange paths 13 was shown. However, the present invention is not limited to this. It is only necessary to provide as many connection passage portions as the number of heat exchange passages. When the number of the heat exchange passages 13 is 32, instead of providing four connection passage portions 14 including eight flow paths, eight connection passage portions including four flow paths may be provided by branching in two stages. It is also possible to provide two connection passage portions that branch into four stages and include 16 flow paths, or to provide one connection passage section that branches into five stages and includes 32 flow paths. Good.

Moreover, in the said 1st Embodiment, the example which provided the pair of branch path 34 which branches in a semi-ellipse (semicircle) shape is shown, and in the said 2nd Embodiment, a pair of branch path 134 which branches in a Y shape is shown. Although the example provided is shown, the present invention is not limited to this. In the present invention, the pair of branch paths may branch into a shape other than the semicircular shape and the Y shape. For example, as shown in the first modification of FIG. 13, the connection passage portion 214 may have a pair of branch paths 234 that branch at right angles. The pair of branch paths 234 includes a first portion 236 that extends linearly along the Y direction and a second portion 237 that extends linearly along the X direction from the first portion 236. The second portion 237 is an example of the “branch source portion” in the present invention. If comprised in this way, the X direction dimension of the 1st part 236 can be suppressed to the minimum. Therefore, in the connection passage portion 214, the X-direction dimension L10 can be further reduced as compared with the connection passage portion 114 of the second embodiment. As a result, the overall size of the heat exchanger can be reduced while suppressing the size in the X direction. In addition, the pair of branch paths may be formed so that the pair of branch paths has a semi-elliptical shape having a major axis and a minor axis having different lengths.

In the first embodiment, the connection is made between the heat exchange passage 13 (23) and the inlet 11 (21) and between the heat exchange passage 13 (23) and the outlet 12 (22). Although the example which provided the channel | path part 14 (24) was shown, this invention is not limited to this. In the present invention, a tournament-shaped connection passage portion may be provided only between the heat exchange passage and the introduction port, or a tournament-shaped connection passage portion may be provided only between the heat exchange passage and the outlet port. .

In the first and second embodiments, the example in which the branch path 34 (134) includes the linear second portion 37 (137) is shown, but the present invention is not limited to this. In the present invention, the branch path may not include the second portion.

Moreover, in the said 1st Embodiment, the length L2 of the 2nd part 37 of the branched path 34 showed the example of the structure which is about 1/9 of radius R1 of the 1st part 36, and about 1/5 of R2. However, the present invention is not limited to this. In the present invention, the length of the second portion may be relatively increased with respect to the radius of the first portion.

FIG. 14 is a diagram showing changes in the velocity vector of the first fluid 6 when the length of the second portion 37 is increased in the branch path 34 of the first embodiment. As shown in FIG. 14, the flow (vector) of the first fluid 6 is biased radially outward when passing through the first portion 36 and enters the second portion 37 (end position of the ¼ arc). Is slightly inclined in the Y direction. Thereafter, the flow (vector) of the first fluid 6 is aligned in the X direction with the Y direction component gradually decreasing in the linear second portion 37. As a result of this simulation, if the length L2 of the second portion 37 is R / 2 with respect to the radius R of the first portion 36, the flow (vector) of the first fluid 6 can be practically sufficiently aligned in the X direction. I understood that. On the other hand, in the region where the length L2> R / 2 of the second portion 37, the merit of the rectifying effect obtained is relatively small with respect to the demerit that the dimension in the X direction of the connection passage portion 14 is large.

As can be seen from FIG. 14, the rectification effect increases toward the upstream side of the second portion 37, and in the range of 0 <L2 <R / 2, the rectification effect can be expected to be improved by the amount provided for the second portion 37. The length of the second portion 37 is preferably length L2 ≧ R / 4, and more preferably R / 4 <length L2 <R / 2. Although illustration is omitted, in the simulation in which the length L2 of the second portion 37 is sufficiently large, a result that can suppress the variation in the flow rate of each channel within a range of about ± 5% was obtained. .

Moreover, in the said 1st and 2nd embodiment, although the connection channel | path part 14 (114) showed the example which has a fixed flow-path cross-sectional area with the fixed flow-path width W1 (W2) over the whole, The present invention is not limited to this. In the present invention, the flow path width (flow path cross-sectional area) of the connection passage portion may change. For example, as in the second modification shown in FIG. 15, the connection passage portion 314 may have a branch path 334 having a different flow path width in each of the first stage 31 to the third stage 33. Preferably, the channel cross-sectional area (channel width) of the pair of branch paths 334 is approximately ½ of the channel cross-sectional area (channel width) before branching. That is, the sum of the channel cross-sectional area (channel width) of the bifurcated branch channel 334 matches the channel cross-sectional area (channel width) before branching. In the connection passage portion 314, the flow passage width (flow passage cross-sectional area) W12 = (W11 / 2) of the branch passage 334 of the first stage 31 with respect to the flow passage width (flow passage cross-sectional area) W11 of the communication passage 15. Yes, the channel width (channel cross-sectional area) W13 = (W12 / 2) of the branch path 334 of the second stage 32, and the channel width (channel cross-sectional area) W14 of the branch path 334 of the third stage 33 = (W13 / 2). Thereby, since the change of the flow-path cross-sectional area before and behind a branch can be suppressed, pressure loss can be suppressed. Here, the flow path depth is assumed to be constant, and the description has been made on the assumption that the flow path width corresponds to the flow path cross-sectional area. Replace with channel cross-sectional area.

In the first and second embodiments, the example in which the linear heat exchange passage 13 (23) is provided has been described, but the present invention is not limited to this. In the present invention, the heat exchange passage may have a curved shape other than a straight shape, for example, a shape that bends after extending from one end of the heat transfer member to the other end and is folded back in the opposite direction. Good.

6 First fluid (fluid)
7 Second fluid (fluid)
10 First heat transfer member (heat transfer member)
11, 21 Introduction port (distribution port)
12, 22 Outlet (distribution port)
13, 23

Heat exchange passage

14, 24, 114, 214, 314 Connection passage portion 20 Second heat transfer member (heat transfer member)
34, 134, 234, 334

Branch path

35, 135

Branch source part

36, 136, 236

First part

37, 137, 237 Second part (branch source part)
100, 200 heat exchanger θ angle formed by a pair of branch paths BS bisecting line

Claims

A circulation port for introducing or deriving a fluid; a plurality of heat exchange passages for causing the fluid to exchange heat; and a connection passage portion having both ends connected to the circulation port and the plurality of heat exchange passages, respectively. A heat transfer member,
The said connection channel | path part is a heat exchanger which has a tournament shape branched to two each toward the said heat exchange channel | path.
The connection passage portion includes a pair of branch paths that branch into two from a branch source portion,
2. The heat exchanger according to claim 1, wherein the branching source portion is connected to the pair of branch paths in a direction in which a bisector of an angle formed by the pair of branch paths extends.
The branch path includes a first part branched from the branch source part and a linear second part as the branch source part extending from the first part and connected to the pair of branch paths on the heat exchange passage side. The heat exchanger of Claim 2 containing these.
The connection passage portion includes a pair of branch paths that branch into two from a branch source portion,
The heat exchanger according to claim 1, wherein the pair of branch paths have equal channel lengths.
The heat exchanger according to claim 4, wherein the pair of branch paths are formed in a symmetrical shape with the branch source portion interposed therebetween.
The heat exchanger according to claim 5, wherein the pair of branch paths are branched from the branch source part so as to form a semi-elliptical shape.
The heat exchanger according to claim 6, wherein the pair of branch paths are each branched in an arc shape from the branch source portion so as to form a semicircular shape.