heat exchanger

Abstract

The heat exchanger includes: a piping body forming a flow path for a first fluid; a pair of partition plates dividing a portion of the flow path into a closed space; a plurality of heat transfer tubes arranged at intervals; a supply section capable of supplying a second fluid from outside the piping body into the closed space; a discharge section capable of discharging the second fluid from the closed space to the outside; and a flow path forming section forming a plurality of small flow path sections between adjacent heat transfer tubes. The second fluid flows between the plurality of heat transfer tubes within the closed space in a direction opposite to the flow direction of the first fluid. When viewed from the position where the discharge section is arranged in the extending direction, the plurality of small flow path sections are arranged at different positions.

Description

Technical Field

[0001] This disclosure relates to heat exchangers.

[0002] This application claims priority to Japanese Patent Application No. 2022-016358, filed on February 4, 2022, the contents of which are incorporated herein by reference. Background Technology

[0003] As a heat exchanger, there is a structure having piping and multiple heat transfer tubes arranged within the piping. In such a heat exchanger, heat exchange occurs between a first fluid flowing within the multiple heat transfer tubes and a second fluid flowing outside the heat transfer tubes within the piping. For example, Patent Document 1 discloses a structure with fins on the heat transfer tubes. By providing fins on the heat transfer tubes, the heat exchange efficiency between the first fluid flowing within the heat transfer tubes and the second fluid flowing outside the heat transfer tubes can be improved.

[0004] Prior art literature

[0005] Patent documents

[0006] Patent Document 1: Japanese Patent Application Publication No. 2010-223520

[0007] However, miniaturization of heat exchangers is sometimes desirable. In such cases, narrowing the gaps between multiple heat transfer tubes arranged in the piping reduces the cross-sectional area of ​​the flow path of the second fluid flowing outside the heat transfer tubes. As a result, the heat exchange efficiency between the first fluid inside the heat transfer tubes and the second fluid outside the heat transfer tubes may decrease. Therefore, in structures where the gaps between the multiple heat transfer tubes are narrowed, it is also desirable to improve the heat exchange efficiency between the first fluid inside the heat transfer tubes and the second fluid outside the heat transfer tubes. Summary of the Invention

[0008] This disclosure provides a heat exchanger capable of improving the heat exchange efficiency between a first fluid inside a heat transfer tube and a second fluid outside the heat transfer tube.

[0009] The heat exchanger disclosed herein comprises: a piping body forming a flow path for a first fluid; a pair of partition plates spaced apart in the extending direction of the piping body, blocking a portion of the flow path in the extending direction and dividing a portion of the flow path to form a closed space; a plurality of heat transfer tubes, which are tubular with open ends, extending along the extending direction through the pair of partition plates and arranged spaced apart from each other; a supply section capable of supplying a second fluid from outside the piping body into the closed space; a discharge section spaced apart from the supply section in the extending direction, capable of discharging the second fluid in the closed space to outside the piping body; and a flow path forming section in which the heat transfer tubes adjacent to each other at the closest positions among the plurality of heat transfer tubes form a plurality of small flow path sections, the second fluid flowing between the plurality of heat transfer tubes in the closed space in a direction opposite to the flow direction of the first fluid, and the plurality of small flow path sections being arranged at different positions when viewed from the position where the discharge section is arranged in the extending direction.

[0010] Invention Effects

[0011] According to the heat exchanger disclosed herein, the heat exchange efficiency between the first fluid inside the heat transfer tube and the second fluid outside the heat transfer tube can be improved. Attached Figure Description

[0012] Figure 1 This is a diagram illustrating the schematic structure of a heat exchanger according to an embodiment of the present disclosure.

[0013] Figure 2 This is a cross-sectional view showing the internal structure of a heat exchanger according to a first embodiment of the present disclosure.

[0014] Figure 3 yes Figure 1 AA-direction sectional view.

[0015] Figure 4 yes Figure 1 BB-direction sectional view.

[0016] Figure 5 This is an enlarged cross-sectional view showing the flow path formation section of the heat exchanger described above.

[0017] Figure 6 This is a diagram showing the flow path forming section of a heat exchanger according to a modified example of the first embodiment of this disclosure.

[0018] Figure 7 This is a cross-sectional view orthogonal to the opposite direction showing the flow path forming portion of the heat exchanger according to the second embodiment of this disclosure.

[0019] Figure 8This is a cross-sectional view showing the internal structure of a heat exchanger according to a third embodiment of this disclosure.

[0020] Explanation of reference numerals in the attached figures:

[0021] 10...Piping;

[0022] 10c...bend;

[0023] 10r...Flow path;

[0024] 11...Piping body;

[0025] 12...bend your elbow;

[0026] 13...blades;

[0027] 20...partitions;

[0028] 20A...First partition plate;

[0029] 20B...Second partition plate;

[0030] 21...Supply Department;

[0031] 22...Discharge section;

[0032] 30A, 30D... core;

[0033] 30a...first end;

[0034] 30b...second end;

[0035] 30c...core middle section;

[0036] 31, 31A, 31B, 31D... heat transfer tubes;

[0037] 31b...top;

[0038] 31c... central axis;

[0039] 31t...top;

[0040] 32...outer surface;

[0041] 38a, 38b... gaps;

[0042] 40A~40D...Flow path forming part;

[0043] 41...The first convex part;

[0044] 41s...front-end;

[0045] 42...Second convex part;

[0046] 42s...front end;

[0047] 45, 45D... small flow path section;

[0048] 45A...First small flow path section;

[0049] 45B...Second small flow path section;

[0050] 48A...First flow path region;

[0051] 48B...Second flow path region;

[0052] 100A~100D... heat exchangers;

[0053] 211...The main body of the supply department;

[0054] 212...supply port;

[0055] 221...Discharge section main body;

[0056] 222...discharge outlet;

[0057] Da...Extended direction;

[0058] Da1...one side;

[0059] Da2...the other side;

[0060] Dc...circumferential;

[0061] Dh... Horizontal direction;

[0062] Ds...pipe diameter;

[0063] Dt...opposite direction;

[0064] Dv...vertical direction;

[0065] H...first fluid;

[0066] L...second fluid;

[0067] Sc... an enclosed space. Detailed Implementation

[0068] Hereinafter, a method for implementing the heat exchanger of the present disclosure will be described with reference to the accompanying drawings. However, the present disclosure is not limited to these embodiments.

[0069] (Structure of a heat exchanger)

[0070] like Figure 1As shown, the heat exchanger 100A is positioned midway through the piping 10. The piping 10 forms a flow path 10r for the flow of a first fluid H. In this embodiment, the first fluid H, such as hydrogen, flows through the flow path 10r within the piping 10. In this embodiment, the piping 10 has a straight pipe body 11 and elbows 12 respectively disposed at both ends of the pipe body 11. The elbows 12 form a bend 10c in the flow path 10r. The elbows 12 are connected to the pipe body 11. A plurality of blades 13 are disposed inside the elbows 12, which guide the flow direction of the first fluid H to align with the bend 10c. Each blade 13 bends along the curve of the elbow 12. A plurality of such blades 13 are arranged at intervals in the width direction of the flow path 10r within the elbows 12. It should be noted that the configuration of the piping body 11 is not limited to connecting to a bent portion of the piping 10, such as the elbow 12. The piping body 11 can be configured as part of the piping 10.

[0071] like Figure 1 and Figure 2 As shown, in this embodiment, the heat exchanger 100A is disposed at the location where the piping body 11 is arranged, in a manner that forms part of the piping 10. The heat exchanger 100A includes the piping body 11 forming the outer shell of the heat exchanger 100A, a pair of partition plates 20, a supply section 21, a discharge section 22, and a core section 30A.

[0072] A pair of partition plates 20 are spaced apart along the extension direction Da of the piping 10. The pair of partition plates 20 are located at both ends of the extension direction Da of the piping body 11. Each pair of partition plates 20 includes a first partition plate 20A disposed on one side (first side) Da1 of the piping body 11 along the extension direction Da, and a second partition plate 20B disposed on the other side (second side) Da2 of the piping body 11 along the extension direction Da. Here, one side Da1 of the extension direction Da is downstream of the flow direction of the first fluid H within the piping body 11. The other side Da2 of the extension direction Da is upstream of the flow direction of the first fluid H within the piping body 11. The pair of partition plates 20 (first partition plate 20A and second partition plate 20B) are each plate-shaped and extend along a surface orthogonal (intersecting) to the extension direction Da. Each pair of partition plates 20 blocks a portion of the flow path 10r along the extension direction Da. A portion of the flow path 10r within the piping 10 forms a closed space Sc, which is divided by a first partition plate 20A and a second partition plate 20B.

[0073] The supply unit 21 is disposed on one side Da1 in the extending direction Da relative to the piping body 11. The supply unit 21 is connected to the piping body 11 as an inlet-side manifold. The supply unit 21 is configured to supply a second fluid L introduced from the outside to the enclosed space Sc within the piping body 11. Figure 2 As shown, the supply section 21 has a cylindrical supply section body 211 with openings at both ends in the extending direction Da. The opening Da1 on one side of the supply section body 211 in the extending direction Da is blocked by a first partition plate 20A. The opening Da2 on the other side of the supply section body 211 in the extending direction Da is connected to the interior of the piping body 11. In the supply section body 211, a supply port 212 connecting the outside and the enclosed space Sc is formed on the other side Da2 in the extending direction Da, opposite to the first partition plate 20A. Figure 3 As shown, the supply port 212 can supply the second fluid L from the outside into the enclosed space Sc.

[0074] The discharge section 22 is disposed on the opposite side Da2 of the extension direction Da relative to the piping body 11. The discharge section 22 is connected to the piping body 11 as an outlet-side manifold. The discharge section 22 is configured to discharge the second fluid L from the enclosed space Sc inside the piping body 11 to the outside. The discharge section 22 has a cylindrical discharge section body 221 with openings at both ends in the extension direction Da. The opening Da2 on the opposite side of the extension direction Da of the discharge section body 221 is blocked by the second partition plate 20B. The opening Da1 on one side of the extension direction Da of the discharge section body 221 is connected to the interior of the piping body 11. In the discharge section body 221, a discharge port 222 connecting the interior and exterior of the enclosed space Sc is formed on the side Da1 of the extension direction Da relative to the second partition plate 20B. Figure 3 As shown, the outlet 222 can discharge the second fluid L from the closed space Sc to the outside.

[0075] like Figure 2 As shown, the core 30A is disposed inside the piping body 11. The first end 30a of the core 30A on one side (Da1) of its extension direction Da is covered from the outside by the supply body 211. The second end 30b of the core 30A on the other side (Da2) of its extension direction Da is covered from the outside by the discharge body 221. The core 30A includes a plurality of heat transfer tubes 31 and a flow path forming section 40A.

[0076] Multiple heat transfer tubes 31 are disposed inside the piping body 11. The multiple heat transfer tubes 31 extend along the extension direction Da (and...). Figure 4The heat transfer tubes 31 extend in a direction orthogonal to the plane of the paper. One end of the extension direction Da1 of each heat transfer tube 31 is disposed in the supply section 21. The other end of the extension direction Da2 of each heat transfer tube 31 is disposed in the discharge section 22. Both ends of the extension direction Da of each heat transfer tube 31 are open. Both ends of the extension direction Da of each heat transfer tube 31 are disposed on the outside of a pair of partition plates 20 in the extension direction Da, passing through a pair of partition plates 20. Both ends of each heat transfer tube 31 are open at a position facing the elbow section 12.

[0077] Multiple heat transfer tubes 31 are arranged at intervals within the piping body 11 in a direction orthogonal (crossing) to the extension direction Da. For example... Figure 3 and Figure 4 As shown, when viewed from the extension direction Da, multiple heat transfer tubes 31 are arranged in multiple stages in the vertical direction Dv, which is orthogonal to the extension direction Da. In each stage of the vertical direction Dv, multiple heat transfer tubes 31 are arranged in multiple horizontal directions Dh, which are orthogonal to both the extension direction Da and the vertical direction Dv. The vertical direction Dv and the horizontal direction Dh are both radial directions of the piping body 11. The heat transfer tubes 31 in the stage located on the upper Dvu side of the vertical direction Dv and the heat transfer tubes 31 in the stage located on the lower Dvd side of the vertical direction Dv are staggered in position in the horizontal direction Dh. When viewed from the extension direction Da, the multiple heat transfer tubes 31 are arranged in a honeycomb pattern. When viewed from the extension direction Da, the multiple heat transfer tubes 31 are arranged in a hexagonal shape around their central position (central axis 31c).

[0078] The cross-sectional shape of each heat transfer tube 31 along a plane orthogonal to the extension direction Da is, for example, hexagonal. That is, each heat transfer tube 31 has six outer surfaces 32 extending circumferentially Dc along the extension direction Da. Each heat transfer tube 31 is configured such that one top 31t faces upward Dvu of the vertical direction Dv, and another top 31b faces downward Dvd of the vertical direction Dv. The plurality of heat transfer tubes 31 are arranged in such a manner that the outer surfaces 32 of adjacent heat transfer tubes 31 are parallel to each other. Figure 5 As shown, the outer surfaces 32 of adjacent heat transfer tubes 31 in the horizontal direction Dh are spaced apart from each other in the horizontal direction Dh. The outer surfaces 32 of adjacent heat transfer tubes 31 in an inclined direction relative to the vertical direction Dv are also spaced apart from each other in an inclined direction intersecting both the vertical direction Dv and the horizontal direction Dh. When viewed from the extension direction Da, the spacing between the outer surfaces 32 of two adjacent heat transfer tubes 31 is constant. In the following description, the direction of the central axes 31c of two heat transfer tubes 31 connected at the closest position is referred to as the opposing direction Dt.

[0079] In the plurality of heat transfer tubes 31, in an imaginary plane orthogonal to the extension direction Da, the flow path forming portion 40A forms a plurality of small flow path portions 45 between the heat transfer tubes 31 that are closest to each other at the closest position. The flow path forming portion 40A has a plurality of first protrusions 41 and a plurality of second protrusions 42.

[0080] Multiple first protrusions 41 are formed on the outer surfaces 32 of one of the two heat transfer tubes 31A and 31B that are adjacent to each other at the closest positions. Each first protrusion 41 protrudes from the outer surface 32 of one heat transfer tube 31A toward the other heat transfer tube 31B along the opposing direction Dt. When viewed from the extension direction Da, the multiple first protrusions 41 are spaced apart along the outer surface 32 of one heat transfer tube 31A in the circumferential direction Dc of each heat transfer tube 31. That is, multiple first protrusions 41 are formed relative to one outer surface 32. When viewed from the extension direction Da, each first protrusion 41 has a rectangular cross-sectional shape and extends along the extension direction Da.

[0081] Multiple second protrusions 42 are formed on the outer surface 32 of one of the two heat transfer tubes 31A and 31B that are adjacent to each other at the closest position. Each second protrusion 42 protrudes from the outer surface 32 of the other heat transfer tube 31B toward the heat transfer tube 31A along the opposing direction Dt. When viewed from the extension direction Da, the multiple second protrusions 42 are spaced apart along the outer surface 32 of the other heat transfer tube 31B on the circumferential direction Dc of each heat transfer tube 31. That is, multiple second protrusions 42 are formed relative to one outer surface 32. When viewed from the extension direction Da, each second protrusion 42 has a rectangular cross-sectional shape and extends along the extension direction Da.

[0082] Viewed from the extending direction Da, the first protrusion 41 and the second protrusion 42 are staggered in the circumferential direction Dc. For the first protrusion 41 and the second protrusion 42, when viewed from the extending direction Da, a portion of the front end 41s of the first protrusion 41 adjacent in the circumferential direction Dc is connected to a portion of the front end 42s of the second protrusion 42. Specifically, for the first protrusion 41 and the second protrusion 42 having a rectangular cross-sectional shape, when viewed from the extending direction Da, the corner of the front end 41s of the first protrusion 41 is connected to the corner of the front end 42s of the second protrusion 42.

[0083] The flow path forming section 40A forms a plurality of small flow path sections 45 through a plurality of first protrusions 41 and a plurality of second protrusions 42. The plurality of small flow path sections 45 are formed between the outer surfaces 32 of one heat transfer tube 31A and the other heat transfer tube 31B. The plurality of small flow path sections 45 include a first small flow path section 45A and a second small flow path section 45B.

[0084] The first small flow path 45A is a space in which adjacent first protrusions 41 on the circumferential direction Dc are surrounded by the outer surfaces 32 of one heat transfer tube 31A and the front ends 42s of the second protrusions 42 formed on the other heat transfer tube 31B. The first small flow path 45A is disposed in the opposing direction Dt at a position close to one of the two heat transfer tubes 31A and 31B that are closest to each other at the closest position.

[0085] The second small flow path 45B is a space in which the second protrusions 42 adjacent to each other in the circumferential direction Dc are surrounded by the outer surfaces 32 of the other heat transfer tube 31B and the front ends 41s of the first protrusions 41 formed on the side of one heat transfer tube 31A. The second small flow path 45B is disposed in the opposing direction Dt at a position close to the other heat transfer tube 31B of the two heat transfer tubes 31A and 31B that are adjacent to each other at the closest position.

[0086] When viewed from the position where the discharge section 22 is arranged in the extending direction Da, multiple first small flow paths 45A and second small flow paths 45B are arranged in different positions. The first small flow paths 45A and second small flow paths 45B are arranged in different positions in both the opposing direction Dt and the circumferential direction Dc. Thus, when viewed from the extending direction Da, the first small flow paths 45A and second small flow paths 45B are arranged in an alternating pattern.

[0087] like Figure 2 As shown, such a flow path forming portion 40A is formed in a part of the core portion 30A in the extension direction Da. The flow path forming portion 40A is formed only in the core intermediate portion 30c between the first end 30a on one side Da1 of the extension direction Da and the second end 30b on the other side Da2 of the extension direction Da. The flow path forming portion 40A is formed between a pair of partition plates 20 in the portion other than the supply portion 21 and the discharge portion 22. That is, for the core portion 30A, at the first end 30a corresponding to the supply portion 21 and the second end 30b corresponding to the discharge portion 22 in the extension direction Da, multiple small flow path portions 45 are not formed between the multiple heat transfer tubes 31, but gaps 38a and 38b are formed.

[0088] The components of the heat exchanger 100A having the above structure are preferably formed using 3D printing technology, such as AM (Additive Modeling). Furthermore, titanium alloys and stainless steel alloys (SUS) are preferably used as materials for forming the heat exchanger 100A.

[0089] In such a heat exchanger 100A, such as Figure 1As shown, the first fluid H flows from the other side Da2 of the extension direction Da toward one side Da1 in the flow path 10r within the piping 10. The first fluid H flows into the heat transfer tube 31 through the elbow 12, which is located on the other side Da2 of the extension direction Da relative to the piping body 11. The first fluid H flows into each heat transfer tube 31 from one end of the heat transfer tube 31 that is open on the other side Da2 of the extension direction Da relative to the second partition plate 20B. That is, the first fluid H does not flow into the closed space Sc on one side Da1 of the extension direction Da relative to the second partition plate 20B, but only into the heat transfer tube 31. The first fluid H flows from the other side Da2 of the extension direction Da toward one side Da1 within the plurality of heat transfer tubes 31. The first fluid H flowing within the heat transfer tube 31 flows out toward the elbow 12, which is located on one side Da1 of the extension direction Da relative to the piping body 11. The first fluid H, after flowing through the heat transfer tube 31, flows out from one end of the heat transfer tube 31, which opens on the side Da1 of the extension direction relative to the first partition plate 20A, into the elbow 12.

[0090] like Figure 2 As shown, a second fluid L, supplied from outside the heat exchanger 100A, flows into the enclosed space Sc of the piping body 11 through the supply port 212 of the supply section 21. The second fluid L is a liquid used to cool the first fluid H, which is the object of cooling. The second fluid L is, for example, liquid oxygen. The second fluid L flows from the gap 38a formed between the multiple heat transfer tubes 31 disposed in the enclosed space Sc at the first end 30a of the core 30A disposed in the supply section 21. Specifically, the second fluid L flows into multiple small flow paths 45 from the gap 38a. The second fluid L flows from one side Da1 in the extension direction Da to the other side Da2 in the multiple small flow paths 45. That is, the second fluid L flows in the direction opposite to the first fluid H in the extension direction Da. As the second fluid L flows through the small flow paths 45, it exchanges heat with the first fluid H flowing in the heat transfer tubes 31, thereby cooling the first fluid H. The second fluid L reaches the gap 38b of the second end 30b of the core 30A disposed in the discharge section 22 from the plurality of small flow paths 45. Then, the second fluid L is discharged to the outside from the discharge port 222 of the discharge section 22 and flows out from the enclosed space Sc.

[0091] (Effects)

[0092] In the heat exchanger 100A with the above-described structure, multiple small flow path sections 45 are formed between the heat transfer tubes 31 that are closest to each other at the nearest position, through flow path forming sections 40A. Furthermore, when viewed from the position where the discharge section 22 is arranged in the extending direction Da, the multiple small flow path sections 45 are arranged at different positions. Therefore, when the second fluid L flows through the multiple small flow path sections 45, the second fluid L flows in contact with the flow path forming sections 40A forming the inner surface of each small flow path section 45. Thus, the contact surface area between the heat transfer tubes 31 that are closest to each other at the nearest position and the flow path forming sections 40A can be ensured to be large. In addition, the cross-sectional area of ​​each small flow path section 45, when viewed from the extending direction Da, is smaller than the gap between the heat transfer tubes 31 that are closest to each other at the nearest position. Therefore, the flow velocity of the second fluid L flowing into the small flow path section 45 is increased. As a result, the second fluid L flows through multiple small flow paths 45, thereby increasing the heat transfer efficiency compared to the case where it flows through the gaps between heat transfer tubes 31 that do not have small flow paths 45. This improves the heat exchange efficiency between the first fluid H inside the heat transfer tube 31 and the second fluid L outside the heat transfer tube 31.

[0093] Furthermore, a first small flow path 45A is formed by the flow path forming section 40A, positioned close to one of the heat transfer tubes 31A, and a second small flow path 45B is formed close to the other heat transfer tube 31B. Specifically, in this embodiment, the first small flow path 45A and the second small flow path 45B are arranged such that the positions of two adjacent heat transfer tubes 31 are staggered in the opposing direction Dt and the circumferential direction Dc. Thus, when viewed from the extending direction Da, the first small flow path 45A and the second small flow path 45B are arranged in a staggered pattern. As a result, compared to the case where a small flow path 45 is formed between adjacent heat transfer tubes 31 at the closest position, the cross-sectional area of ​​each of the first small flow path 45A and the second small flow path 45B when viewed from the extending direction Da is smaller. Therefore, the flow velocity of the second fluid L flowing into the first small flow path 45A and the second small flow path 45B is further increased. Therefore, the second fluid L flows in the staggered first small flow path section 45A and the second small flow path section 45B, thereby further increasing the heat transfer efficiency of the second fluid L via the flow path forming section 40A. As a result, the heat exchange efficiency between the first fluid H inside the heat transfer tube 31 and the second fluid L outside the heat transfer tube 31 can be further improved.

[0094] Furthermore, the flow path forming section 40A includes a plurality of first protrusions 41 formed on the outer surface 32 of one heat transfer tube 31A and a plurality of second protrusions 42 formed on the outer surface 32 of the other heat transfer tube 31B. Moreover, when viewed from the extending direction Da, the first protrusions 41 and the second protrusions 42 are staggered in the circumferential direction Dc. As a result, compared to the case where only one of the first protrusions 41 and the second protrusions 42 is formed, the contact surface area between the second fluid L and the flow path forming section 40A can be ensured to be larger by using both the first protrusions 41 and the second protrusions 42. Consequently, the heat exchange efficiency between the first fluid H inside the heat transfer tube 31 and the second fluid L outside the heat transfer tube 31 can be further improved.

[0095] Furthermore, when viewed from the extending direction Da, a portion of the front end 41s of the first protrusion 41 adjacent to the second protrusion 42 on the circumferential direction Dc is connected to a portion of the front end 42s of the second protrusion 42. This allows the first small flow path 45A and the second small flow path 45B to be formed independently. Therefore, compared to the case where the first small flow path 45A and the second small flow path 45B are connected, the cross-sectional area when viewed from the extending direction Da can be further reduced. This allows for a further increase in the flow velocity of the second fluid L flowing into the first small flow path 45A and the second small flow path 45B.

[0096] (A variation of the first embodiment)

[0097] It should be noted that in the first embodiment described above, when viewed from the extension direction Da, a portion of the front end 41s of the first protrusion 41 adjacent to the second protrusion 42 on the circumferential direction Dc is connected to a portion of the front end 42s of the second protrusion 42, but the structure of the flow path forming portion 40A is not limited to such a structure.

[0098] For example, it can also be like Figure 6 As shown, when viewed from the extension direction Da, the first protrusion 41 and the second protrusion 42 adjacent to each other on the circumferential direction Dc are arranged at intervals on the circumferential direction Dc in the flow path forming part 40B of the heat exchanger 100B.

[0099] According to this structure, the first small flow path 45A formed between adjacent first protrusions 41 on the circumferential Dc is connected to the second small flow path 45B formed between adjacent first protrusions 41 on the circumferential Dc. Similarly, in this structure, the second fluid L passes through multiple first small flow path sections 45A and second small flow path sections 45B, thereby improving the heat exchange efficiency of the second fluid L via the flow path forming section 40A. Furthermore, by making the first protrusions 41 and second protrusions 42 independent, it is easy to form the first protrusions 41 and second protrusions 42.

[0100] (Second Implementation)

[0101] Next, a second embodiment of the heat exchanger of this disclosure will be described. It should be noted that in the second embodiment described below, structures common to the first embodiment described above are labeled with the same reference numerals in the figures, and their descriptions are omitted. In the second embodiment, the structure of a portion of the flow path forming section 40C differs from that in the first embodiment.

[0102] like Figure 7 As shown, the flow path forming section 40C of the heat exchanger 100C is configured such that, in the extension direction Da, the cross-sectional area of ​​the small flow path section 45 is larger when viewed from the extension direction Da than when it is near the discharge section 22 near the supply section 21. The flow path forming section 40C includes a first flow path region 48A and a second flow path region 48B. The first flow path region 48A is a region in the flow path forming section 40C formed on one side Da1 of the extension direction Da. The second flow path region 48B is a region in the flow path forming section 40C formed on the other side Da2 of the extension direction Da, opposite to the first flow path region 48A. The second flow path region 48B is configured such that its cross-sectional area when viewed from the extension direction Da is larger than that of the first flow path region 48A.

[0103] In the first flow path region 48A, similarly to the flow path forming section 40A of the first embodiment described above, such as Figure 5 As shown, the heat transfer tubes 31 that are closest to each other have multiple small flow paths 45 formed between them. That is, multiple first protrusions 41 and multiple second protrusions 42 are arranged in the first flow path region 48A. Thus, the multiple small flow paths 45 have first small flow path 45A and second small flow path 45B.

[0104] Furthermore, at least a portion of the plurality of first protrusions 41 and the plurality of second protrusions 42 terminates at a position Da1 on one side of the extending direction Da relative to the second flow path region 48B. That is, at least a portion of the plurality of first protrusions 41 and the plurality of second protrusions 42 is not formed in the second flow path region 48B. It should be noted that it is also possible that not all of the plurality of first protrusions 41 and the plurality of second protrusions 42 are formed in the second flow path region 48B. As a result, at least a portion of the plurality of small flow path portions 45 (first small flow path portion 45A and second small flow path portion 45B) formed in the first flow path region 48A merges in the second flow path region 48B. Therefore, the flow path forming portion 40C is formed such that, in the extending direction Da, the flow path cross-sectional area is larger in the position near the discharge portion 22 than that of the small flow path portions 45 when viewed from the extending direction Da.

[0105] According to the heat exchanger 100C with the above structure, when the temperature of the first fluid H is higher than the temperature of the second fluid L, the second fluid L, which flows between the plurality of heat transfer tubes 31, experiences a temperature increase through heat exchange with the first fluid H flowing within the plurality of heat transfer tubes 31. As a result, the properties of the second fluid L change from liquid to gas. Consequently, in the extending direction Da, as it approaches the discharge section 22, the density of the second fluid L decreases, and its specific volume increases (expands). To address this, in the flow path forming section 40C of the second embodiment, the position near the discharge section 22 changes from the first flow path region 48A to the second flow path region 48B. As a result, the flow path cross-sectional area of ​​the small flow path section 45 in the second flow path region 48B, when viewed from the extending direction Da, can be increased. This allows for the volume expansion of the second fluid L flowing from the first flow path region 48A into the second flow path region 48B, and the flow rate of the second fluid L in the second flow path region 48B can be accelerated. As a result, the heat exchange efficiency between the first fluid H inside the heat transfer tube 31 and the second fluid L outside the heat transfer tube 31 can be improved.

[0106] Furthermore, the second flow path region 48B is formed by the merging of at least a portion of the multiple small flow path sections 45 formed in the first flow path region 48A. This allows for the easy formation of a structure that increases the flow path cross-sectional area midway along the extending direction Da.

[0107] (Third Implementation)

[0108] Next, a third embodiment of the heat exchanger of this disclosure will be described. It should be noted that in the third embodiment described below, structures common to the first and second embodiments described above are marked with the same reference numerals in the figures, and their descriptions are omitted. In the third embodiment, the structure of the flow path forming section 40D differs from that of the first and second embodiments.

[0109] like Figure 8 As shown, the core 30D of the heat exchanger 100D has multiple heat transfer tubes 31D and a flow path forming section 40D.

[0110] The cross-sectional area of ​​the flow path within each heat transfer tube 31D is formed to gradually increase from the other side Da2 of the extension direction Da toward one side. Therefore, the tube diameter (inner and outer diameter) Ds of each heat transfer tube 31D is formed to gradually increase from the other side Da2 of the extension direction Da toward one side Da1. That is, the heat transfer tube 31D becomes a trapezoidal tube member with a cross-sectional area where one side Da1 of the extension direction Da is wider than the other side Da2. Consequently, the cross-sectional area of ​​the gap between adjacent heat transfer tubes 31D at their closest positions in an imaginary plane orthogonal to the extension direction Da (the portion where the flow path forming portion 40D is formed) gradually increases from one side Da1 of the extension direction Da toward the other side Da2. In the third embodiment, this gap becomes a small flow path portion 45D. That is, the flow path forming portion 40D in the third embodiment serves as a wall surface for the heat transfer tube 31D. As a result, the cross-sectional area of ​​the multiple small flow paths 45D gradually increases when viewed from the extension direction Da as the discharge section 22 approaches the supply section 21.

[0111] According to this structure, the cross-sectional area of ​​the small flow path portion 45D, which forms the flow path of the second fluid L, gradually increases from one side Da1 in the extension direction Da towards the other side Da2. Therefore, the volume of the second fluid L can be increased, and the flow rate of the second fluid L can be gradually increased. As a result, the heat exchange efficiency between the first fluid H inside the heat transfer tube 31 and the second fluid L outside the heat transfer tube 31 can be improved.

[0112] (Other implementation methods)

[0113] The embodiments of this disclosure have been described in detail above with reference to the accompanying drawings. However, the specific structure is not limited to these embodiments and may include design changes that do not depart from the scope of this disclosure.

[0114] It should be noted that in the above embodiments, the first small flow path portion 45A and the second small flow path portion 45B are arranged alternately at different positions in the opposing direction Dt and the circumferential direction Dc, but the small flow path portion 45 is not limited to such a structure. There are no limitations on the arrangement of the small flow path portion 45, and by having multiple small flow path portions 45 with narrower flow path cross-sectional areas, the same effect as in the above embodiments can be obtained.

[0115] <Postscript>

[0116] The heat exchangers 100A to 100D described in each embodiment are as follows, for example.

[0117] (1) The heat exchangers 100A-100D of the first embodiment include: a piping body 11 forming a flow path 10r to which a first fluid H is supplied; a pair of partition plates 20 spaced apart in the extension direction Da of the piping body 11, blocking a portion of the flow path 10r in the extension direction Da, and dividing a portion of the flow path 10r to form a closed space Sc; a plurality of heat transfer tubes 31, 31D, which are tubular with open ends, extending along the extension direction Da in a manner that penetrates the pair of partition plates 20, and arranged spaced apart from each other; a supply unit 21 capable of supplying a second fluid L from outside the piping body 11 into the closed space Sc; and a discharge unit 22, which... The supply section 21 is arranged at intervals along the extension direction Da, which can discharge the second fluid L in the enclosed space Sc to the outside of the piping body 11; and the flow path forming sections 40A to 40D form a plurality of small flow path sections 45 between the heat transfer tubes 31 and 31D that are adjacent to each other at the closest position among the plurality of heat transfer tubes 31 and 31D, in which the second fluid L flows in the enclosed space Sc in a direction opposite to the flow direction of the first fluid H among the plurality of heat transfer tubes 31 and 31D, and when viewed from the position where the discharge section 22 is arranged along the extension direction Da, the plurality of small flow path sections 45 are arranged in different positions.

[0118] According to such heat exchangers 100A to 100D, when the second fluid L flows through the plurality of small flow path sections 45, the second fluid L flows in contact with the flow path forming section 40A that forms the inner surface of each small flow path section 45. Therefore, the contact surface area between the second fluid L and the flow path forming section 40A between the heat transfer tubes 31 that are closest to each other can be ensured to be large. Furthermore, the cross-sectional area of ​​each small flow path section 45 when viewed from the extending direction Da is smaller than the gap between the heat transfer tubes 31 that are closest to each other. Therefore, the flow velocity of the second fluid L flowing into the small flow path section 45 increases. As a result, the second fluid L flows through the plurality of small flow path sections 45, thereby increasing the heat transfer efficiency compared to the case where it flows in the gap between the heat transfer tubes 31 where small flow path sections 45 are not formed. Therefore, the heat exchange efficiency between the first fluid H inside the heat transfer tube 31 and the second fluid L outside the heat transfer tube 31 can be improved.

[0119] (2) The heat exchangers 100A to 100D of the second scheme are based on the heat exchangers 100A to 100D of (1). The flow path forming parts 40A to 40D form a first small flow path part 45A and a second small flow path part 45B as the small flow path part 45. The first small flow path part 45A is arranged at a position close to one of the two heat transfer tubes 31 and 31D that are adjacent to each other at the closest position. The second small flow path part 45B is arranged at a position close to the other of the two heat transfer tubes 31 and 31D that are adjacent to each other at the closest position. When viewed from the extension direction Da, the second small flow path part 45B is arranged at a position offset from the first small flow path part 45A in the circumferential direction Dc of the heat transfer tubes 31 and 31D.

[0120] Therefore, compared to the case where heat transfer tubes 31 adjacent to each other at the closest position have a small flow path 45 between them, the cross-sectional area of ​​the first small flow path 45A and the second small flow path 45B, when viewed in their respective extending directions Da, becomes smaller. Consequently, the flow velocity of the second fluid L flowing into the first small flow path 45A and the second small flow path 45B further increases. Therefore, the heat transfer efficiency of the second fluid L flowing through the first small flow path 45A and the second small flow path 45B, via the flow path forming section 40A, further increases. As a result, the heat exchange efficiency between the first fluid H inside the heat transfer tube 31 and the second fluid L outside the heat transfer tube 31 can be further improved.

[0121] (3) The heat exchanger 100A-100D of the third embodiment is based on the heat exchanger 100A-100D of (1) or (2), wherein the flow path forming part 40A-40D includes: a plurality of first protrusions 41 that protrude from the outer surface 32 of one of the two heat transfer tubes 31 that are adjacent to each other at the closest position toward the other heat transfer tube 31 and extend along the extension direction Da, and are arranged at intervals on the circumferential direction Dc of the heat transfer tubes 31; and a plurality of second protrusions 42 that protrude from the outer surface 32 of the other heat transfer tube 31 toward the one heat transfer tube 31 and extend along the extension direction Da, and are arranged at intervals on the circumferential direction Dc, wherein when viewed from the extension direction Da, the first protrusions 41 and the second protrusions 42 are staggered on the circumferential direction Dc.

[0122] Therefore, compared to the case where only one of the first protrusion 41 and the second protrusion 42 is formed, the contact surface area between the second fluid L and the flow path forming portion 40A can be ensured to be larger by forming both the first protrusion 41 and the second protrusion 42. As a result, the heat exchange efficiency between the first fluid H inside the heat transfer tube 31 and the second fluid L outside the heat transfer tube 31 can be further improved.

[0123] (4) The heat exchanger 100A of the fourth embodiment is based on the heat exchanger 100A of (3), when viewed from the extension direction Da, a portion of the front end 41s of the first protrusion 41 adjacent to the second protrusion 42 on the circumferential direction Dc is connected to a portion of the front end 42s of the second protrusion 42.

[0124] Therefore, compared to the case where the first small flow path section 45A and the second small flow path section 45B are connected, the cross-sectional area when viewed from the extending direction Da can be further reduced. Consequently, the flow velocity of the second fluid L flowing into the first small flow path section 45A and the second small flow path section 45B can be further increased.

[0125] (5) The heat exchanger 100B of the fifth embodiment is based on the heat exchanger 100B of (3), wherein when viewed from the extension direction Da, the first protrusion 41 and the second protrusion 42 adjacent to each other on the circumferential direction Dc are arranged at intervals on the circumferential direction Dc.

[0126] Thus, by making the first protrusion 41 and the second protrusion 42 independent, it is easy to form the first protrusion 41 and the second protrusion 42.

[0127] (6) In the sixth embodiment, the heat exchangers 100C and 100D are based on any one of the heat exchangers 100C and 100D in (1) to (5), wherein the flow path forming portions 40C and 40D are formed such that, in the extension direction Da, the flow path cross-sectional area is larger than that of the small flow path portion 45 when viewed from the extension direction Da than when viewed from the extension direction Da, compared to the position near the supply portion 21.

[0128] This increases the cross-sectional area of ​​the small flow path 45 when viewed from the extending direction Da near the discharge section 22. Consequently, the volume expansion of the second fluid L flowing from the supply section 21 towards the discharge section 22 is allowed, and the flow rate of the second fluid L can be increased near the discharge section 22. As a result, the heat exchange efficiency between the first fluid H inside the heat transfer tube 31 and the second fluid L outside the heat transfer tube 31 can be improved.

[0129] (7) The heat exchanger 100C of the seventh embodiment is based on the heat exchanger 100C of (6), wherein at least a portion of the plurality of small flow path sections 45 merge with each other in the middle of the extension direction Da.

[0130] Therefore, it is easy to form a structure that increases the cross-sectional area of ​​the flow path midway along the extension direction Da.

[0131] (8) The heat exchanger 100D of the eighth embodiment is based on the heat exchanger 100D of (6), wherein the cross-sectional area of ​​the multiple small flow path sections 45D gradually increases when viewed from the extension direction Da as the supply section 21 approaches the discharge section 22.

[0132] Therefore, by allowing the volume of the second fluid L to increase, the flow rate of the second fluid L can be gradually increased. As a result, the heat exchange efficiency between the first fluid H inside the heat transfer tube 31 and the second fluid L outside the heat transfer tube 31 can be improved.

[0133] Industrial availability

[0134] According to the heat exchanger disclosed herein, the heat exchange efficiency between the first fluid inside the heat transfer tube and the second fluid outside the heat transfer tube can be improved.

Claims

1. A heat exchanger, wherein, The heat exchanger includes: The main piping unit forms the flow path for the first fluid to be supplied; A pair of partition plates are arranged at intervals in the extension direction of the piping body, blocking a portion of the flow path in the extension direction and dividing a portion of the flow path to form an enclosed space; Multiple heat transfer tubes, which are tubular with open ends, extend along the extension direction in a manner that penetrates the pair of partition plates and are arranged at intervals to each other. A supply unit capable of supplying a second fluid from outside the piping body into the enclosed space; The discharge section, which is arranged at intervals from the supply section in the extending direction, is capable of discharging the second fluid in the enclosed space to the outside of the piping body; as well as A flow path forming section, wherein the heat transfer tubes that are closest to each other in the plurality of heat transfer tubes form a plurality of small flow path sections between each other. The second fluid flows between the plurality of heat transfer tubes within the enclosed space in a direction opposite to that of the first fluid. When viewed from the position where the discharge portion is arranged in the extending direction, the plurality of small flow path portions are arranged in different positions. The flow path forming section forms a first small flow path section and a second small flow path section as the small flow path section. The first small flow path is positioned close to one of the two heat transfer tubes that are closest to each other in the closest position. The second small flow path is positioned close to the other of the two heat transfer tubes that are closest to each other at the closest position, and when viewed from the extension direction, the second small flow path is positioned circumferentially offset from the first small flow path in the heat transfer tube. When viewed from the extending direction, the first small flow path and the second small flow path are arranged in an alternating pattern.

2. The heat exchanger according to claim 1, wherein, The flow path forming section includes: A plurality of first protrusions protrude from the outer surface of one of the two heat transfer tubes that are adjacent to each other at the closest position toward the other heat transfer tube and extend in the extending direction, and are arranged at intervals in the circumferential direction of the heat transfer tubes. as well as A plurality of second protrusions, which protrude from the outer surface of one of the heat transfer tubes toward the other heat transfer tube and extend along the extending direction, are arranged at intervals in the circumferential direction. When viewed from the extending direction, the first protrusion and the second protrusion are offset in the circumferential direction.

3. The heat exchanger according to claim 2, wherein, When viewed from the extending direction, a portion of the front end of the first protrusion adjacent in the circumferential direction is connected to a portion of the front end of the second protrusion.

4. The heat exchanger according to claim 2, wherein, When viewed from the extending direction, the first protrusion and the second protrusion, which are adjacent in the circumferential direction, are arranged at a distance from each other in the circumferential direction.

5. A heat exchanger, wherein, The heat exchanger includes: The main piping unit forms the flow path for the first fluid to be supplied; A pair of partition plates are arranged at intervals in the extension direction of the piping body, blocking a portion of the flow path in the extension direction and dividing a portion of the flow path to form an enclosed space; Multiple heat transfer tubes, which are tubular with open ends, extend along the extension direction in a manner that penetrates the pair of partition plates and are arranged at intervals to each other. A supply unit capable of supplying a second fluid from outside the piping body into the enclosed space; The discharge section, which is arranged at intervals from the supply section in the extending direction, is capable of discharging the second fluid in the enclosed space to the outside of the piping body; as well as A flow path forming section, wherein the heat transfer tubes that are closest to each other in the plurality of heat transfer tubes form a plurality of small flow path sections between each other. The second fluid flows between the plurality of heat transfer tubes within the enclosed space in a direction opposite to that of the first fluid. When viewed from the position where the discharge portion is arranged in the extending direction, the plurality of small flow path portions are arranged in different positions. The flow path forming section includes: A plurality of first protrusions protrude from the outer surface of one of the two heat transfer tubes that are adjacent to each other at the closest position toward the other heat transfer tube and extend in the extending direction, and are arranged at intervals in the circumferential direction of the heat transfer tubes. as well as A plurality of second protrusions, which protrude from the outer surface of one of the heat transfer tubes toward the other heat transfer tube and extend along the extending direction, are arranged at intervals in the circumferential direction. When viewed from the extending direction, the first protrusion and the second protrusion are offset in the circumferential direction. When viewed from the extending direction, a portion of the front end of the first protrusion adjacent in the circumferential direction is connected to a portion of the front end of the second protrusion.

6. The heat exchanger according to claim 5, wherein, The flow path forming section forms a first small flow path section and a second small flow path section as the small flow path section. The first small flow path is positioned close to one of the two heat transfer tubes that are closest to each other in the closest position. The second small flow path is positioned close to the other of the two heat transfer tubes that are adjacent to each other at the closest position, and when viewed from the extension direction, the second small flow path is positioned offset from the first small flow path in the circumferential direction of the heat transfer tube.

7. The heat exchanger according to claim 5, wherein, When viewed from the extending direction, the first protrusion and the second protrusion, which are adjacent in the circumferential direction, are arranged at a distance from each other in the circumferential direction.

8. The heat exchanger according to any one of claims 1 to 7, wherein, The flow path forming section is configured such that, in the extending direction, the cross-sectional area of ​​the small flow path section is larger when viewed from the extending direction than when it is near the discharge section.

9. The heat exchanger according to claim 8, wherein, At least a portion of the multiple small flow paths merge with each other midway along the extension direction.

10. The heat exchanger according to claim 8, wherein, The cross-sectional area of ​​the multiple small flow paths gradually increases as the supply section approaches the discharge section when viewed from the extension direction.

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