heat exchanger

Abstract

The inner fin of the heat exchanger has a corrugated shape in which one side top (361) and the other side top (362) are alternately arranged in one direction (Df) via an intermediate portion (363) in a cross section perpendicular to the thickness direction (Dt) of the flat cross section of the flow path tube (3). The intermediate portion has a connecting portion (364) having a connecting port (364a) that connects two adjacent thin flow paths across the inner fin. The intermediate portion has a side wall portion (365) that extends from the one side top adjacent to the connecting portion in the one direction to the connecting portion and separates the two thin flow paths. The intermediate portion has another side wall portion (366) that extends from the other side top adjacent to the connecting portion in the one direction to the connecting portion and separates the two thin flow paths. The peripheral edge of the communication port includes an end edge (365a) of one side wall portion and an end edge (366a) of the other side wall portion, and the end edge of one side wall portion is formed in a manner that allows the end edge of the other side wall portion to move parallel to the long side direction (Dw) of the above-mentioned flat cross-sectional shape.

Description

[0001] Cross-reference to related applications

[0002] This application is based on Japanese Patent Application No. 2020-25292 filed on February 18, 2020, the contents of which are incorporated herein by reference. Technical Field

[0003] The present invention relates to a heat exchanger that exchanges heat between a heat exchange object and a heat medium. Background Art

[0004] As such a heat exchanger, for example, the heat exchanger described in Patent Document 1 is known in the past. The heat exchanger described in Patent Document 1 includes a plurality of flow tubes that sandwich a heat exchange object, such as a heat generating element such as a semiconductor module having a built-in semiconductor element, from both sides. The plurality of flow tubes each have a flat cross-sectional shape and are stacked with the heat exchange object sandwiched between them. The heat exchanger in Patent Document 1 exchanges heat between a heat medium flowing through the plurality of flow tubes and the heat exchange object.

[0005] The heat exchanger of Patent Document 1 includes inner fins arranged inside the flow tube and configured as corrugated fins. The inner fins divide the internal space of the flow tube 3 into a plurality of narrow flow paths, thereby increasing the heat transfer area between the heat exchange object and the heat medium.

[0006] Furthermore, an opening is partially formed in the inner fin, and the opening connects two adjacent thin flow paths across the inner fin among the plurality of thin flow paths.

[0007] Prior art literature

[0008] Patent Literature

[0009] Patent Document 1: Japanese Patent No. 6327271

[0010] In the heat exchanger disclosed in Patent Document 1, for example, when a compressive force acting on the flow tube acts in the thickness direction of the flat cross-section of the flow tube, the inner fins within the flow tube serve to overcome this compressive force. However, since the inner fins have openings, there is a concern that the strength of the inner fins required to overcome this compressive force will be reduced.

[0011] Specifically, in the heat exchanger disclosed in Patent Document 1, the shape of the opening, as viewed from a direction opposite to the opening, is a triangular shape that tapers toward one or the other side in the thickness direction of the flat cross-section of the flow tube. Furthermore, the length of one of the two sides of the opening extending in the thickness direction that define this triangular shape is different from the length of the other side.

[0012] Therefore, for example, if a compressive external force acts on the flow tube in the thickness direction, causing the peripheral edge of the opening to deform, the peripheral edge of the opening bends in such a way that the difference in length between the long side portion (corresponding to the longer side) and the short side portion (corresponding to the shorter side) of the one side and the other side is shortened. Therefore, in this case, the long side portion of the peripheral edge of the opening bends before the short side portion. That is, in the heat exchanger of Patent Document 1, when the long side portion and the short side portion of the peripheral edge of the opening bend due to a compressive external force, they bend at different times. Therefore, in the heat exchanger of Patent Document 1, the strength of the long side portion and the short side portion cannot be fully utilized, which is one of the reasons for the reduced strength of the inner fins.

[0013] Furthermore, while forming inner fins to miniaturize the numerous fine flow paths within the flow tubes can improve the strength of the inner fins, the smaller the fine flow paths, the greater the pressure loss of the heat medium flowing within the flow tubes. The inventors have discovered this through detailed research. Summary of the Invention

[0014] In view of the above, the present invention aims to provide a heat exchanger disclosed in Patent Document 1, which, compared to the heat exchanger disclosed in Patent Document 1, does not require miniaturization of the multiple narrow flow paths within the flow path tube, while suppressing the reduction in strength of the inner fins caused by the provision of a communication portion. Furthermore, the communication portion corresponds to the opening of the heat exchanger disclosed in Patent Document 1.

[0015] In order to achieve the above object, according to one aspect of the present invention, a heat exchanger,

[0016] A heat exchanger that exchanges heat between an object and a heat medium and has:

[0017] a flow pipe having a flat cross-sectional shape in a first cross-section perpendicular to one direction, wherein a heat medium flows through the flow pipe with one side in the one direction being an upstream side of the flow of the heat medium and the other side in the one direction being a downstream side of the flow of the heat medium; and

[0018] The inner fin is arranged inside the flow tube and divides the internal space of the flow tube into a plurality of thin flow paths arranged in the long side direction of the flat cross-sectional shape. The inner fin has a cross-sectional wave shape in a first cross-section, wherein a convex shape on one side and a convex shape on the other side are alternately connected and extend in the long side direction. The convex shape on one side bulges toward one side in the thickness direction of the flat cross-sectional shape, and the convex shape on the other side bulges toward the other side in the thickness direction. The inner fin extends in the one direction.

[0019] The inner fin has a corrugated shape in which one side top and the other side top are alternately arranged in one direction via a middle portion in a second cross-section perpendicular to the thickness direction, the one side top is arranged between the plurality of fine flow paths and is curved so as to bulge toward one side in the longitudinal direction, and the other side top is arranged between the plurality of fine flow paths and is curved so as to bulge toward the other side in the longitudinal direction.

[0020] The middle portion includes a connecting portion, a side wall portion, and another side wall portion. The connecting portion is formed with a connecting port that connects two adjacent thin flow paths across the inner fin among the plurality of thin flow paths. The one side wall portion extends from a top portion of a side adjacent to the connecting portion in the one direction to the connecting portion and separates the two adjacent thin flow paths. The other side wall portion extends from a top portion of the other side adjacent to the connecting portion in the one direction to the connecting portion and separates the two adjacent thin flow paths.

[0021] The inner fin is provided with one or more connecting parts.

[0022] The communication port is arranged in the middle portion away from each of the top portion on one side and the top portion on the other side.

[0023] The peripheral edge of the communication port includes an end edge of one side wall portion and an end edge of the other side wall portion. The end edge of the one side wall portion is formed so as to be parallel to the end edge of the other side wall portion in the longitudinal direction.

[0024] As a result, the end edges of one side wall and the other side wall are approximately the same length. Therefore, when the end edges of one side wall and the other side wall bend due to the compressive external force acting on the flow tube in the thickness direction, the respective bending times coincide. Therefore, compared to the heat exchanger disclosed in Patent Document 1, for example, it is possible to suppress the reduction in inner fin strength caused by the provision of the connecting portion without miniaturizing the multiple fine flow paths within the flow tube.

[0025] In addition, according to another aspect of the present invention, the heat exchanger,

[0026] A heat exchanger that exchanges heat between an object and a heat medium and has:

[0027] a flow pipe having a flat cross-sectional shape in a first cross-section perpendicular to one direction, wherein a heat medium flows through the flow pipe with one side in the one direction being an upstream side of the flow of the heat medium and the other side in the one direction being a downstream side of the flow of the heat medium; and

[0028] The inner fin is arranged inside the flow tube and divides the internal space of the flow tube into a plurality of thin flow paths arranged in the long side direction of the flat cross-sectional shape. The inner fin has a cross-sectional wave shape in a first cross-section, wherein a convex shape on one side and a convex shape on the other side are alternately connected and extend in the long side direction. The convex shape on one side bulges toward one side in the thickness direction of the flat cross-sectional shape, and the convex shape on the other side bulges toward the other side in the thickness direction. The inner fin extends in the one direction.

[0029] The inner fin has a corrugated shape in which one side top and the other side top are alternately arranged in the above-mentioned one direction via an intermediate portion in a second cross-section perpendicular to the thickness direction, the one side top is arranged between the plurality of fine flow paths and is curved so as to bulge toward one side in the longitudinal direction, and the other side top is arranged between the plurality of fine flow paths and is curved so as to bulge toward the other side in the longitudinal direction.

[0030] The middle portion is configured as a wall that separates two adjacent thin flow paths across the inner fins among the plurality of thin flow paths, and has a cut-and-raised portion.

[0031] The cut and raised portion is in a cut and folded shape, so that the through hole penetrating the cut and raised wall portion is formed on one side or the other side of the cut and raised portion in the above-mentioned direction.

[0032] The inner fin is provided with one or more through holes and one or more cut-and-raised portions.

[0033] This allows the cut-and-raised portion to overcome the compressive external forces acting on the flow tube in the thickness direction. Therefore, compared to, for example, the case of providing openings in the inner fins as in Patent Document 1, the inner fins can be formed so that the central portion is less susceptible to buckling in the thickness direction. Consequently, compared to, for example, the heat exchanger in Patent Document 1, the reduction in inner fin strength caused by providing through-holes in the central portion can be suppressed without miniaturizing the multiple narrow flow paths within the flow tubes. Furthermore, these through-holes in the central portion can replace the openings in the heat exchanger in Patent Document 1, thereby improving heat exchange performance.

[0034] In addition, the reference symbols in parentheses attached to each component etc. represent an example of the correspondence relationship between the component etc. and the specific components etc. described in the embodiment described later. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] Figure 1 This is a front view schematically showing the structure of the heat exchanger in the first embodiment.

[0036] Figure 2 In the first embodiment, Figure 1 Cross-sectional view of section II-II.

[0037] Figure 3 In the first embodiment, Figure 2A cross-sectional view of section III-III (ie, the first cross-sectional view).

[0038] Figure 4 yes Figure 2 It is a view taken in the IV direction and is a diagram showing a flow channel tube of a single body.

[0039] Figure 5 This is a diagram showing a first embodiment, partially illustrating the intermediate plate and the first inner fins when viewed from one side toward the other direction in the flat thickness direction, and showing a state in which the first inner fins are mounted on the intermediate plate.

[0040] Figure 6 This is a perspective view partially showing a region where a corrugated shape is formed in the first inner fin in the first embodiment.

[0041] Figure 7 This is a diagram partially showing the first inner fin of the first embodiment, and is in accordance with Figure 5 The same direction of observation indicates that in the second section perpendicular to the flat thickness direction, Figure 5 A cross-sectional view of part VII.

[0042] Figure 8 This is an enlarged representation of the first embodiment. Figure 7 An enlarged cross-sectional view of part VIII.

[0043] Figure 9 is Figure 6 Section IX is a perspective view of the first inner fin in cross section.

[0044] Figure 10 In the first embodiment, Figure 8 Cross-sectional view of section XX.

[0045] Figure 11 This is a diagram partially showing the first inner fin of the first embodiment, and is in accordance with Figure 5 Observe in the same direction and indicate Figure 5 Top view of part VII.

[0046] Figure 12 is schematically represented by Figure 10 The cross section taken along the same direction shows a cross-sectional view of a portion of the inner fin in the first comparative example.

[0047] Figure 13 This is a perspective view showing a portion of an inner fin in the first comparative example, schematically showing the area of ​​a pressure-receiving surface between two communication ports adjacent to each other in the flow direction in the tube in the inner fin, which receives a compressive external force.

[0048] Figure 14is an enlarged cross-sectional view showing a portion of the inner fin in the second comparative example, and is equivalent to Figure 8 Picture.

[0049] Figure 15 In the second comparative example Figure 14 The sectional view of the XV-XV section is equivalent to Figure 10 Picture.

[0050] Figure 16 This is a perspective view showing a portion of the first inner fin in cross section in the first embodiment, and is a view showing a state in which a compressive external force acts on the flow tube accommodating the first inner fin in the flat thickness direction.

[0051] Figure 17 This is a cross-sectional view partially showing a portion of the first inner fin of the second embodiment in the second cross section.

[0052] Figure 18 This is a perspective view partially showing a portion of a first inner fin according to the third embodiment.

[0053] Figure 19 yes Figure 18 XIX direction view.

[0054] Figure 20 Yes Figure 18 Cross-sectional view of section XX-XX.

[0055] Figure 21 This is a perspective view partially showing a portion of the first inner fin of the fourth embodiment, and is equivalent to Figure 18 Picture.

[0056] Figure 22 yes Figure 21 The XXII direction view is equivalent to Figure 19 Picture.

[0057] Figure 23 Yes Figure 21 The sectional view of section XXIII-XXIII is equivalent to Figure 20 Picture.

[0058] Figure 24 It means that Figure 5 The top view of the first inner fin of the fifth embodiment is viewed from the same direction and is equivalent to Figure 11 Picture.

[0059] Figure 25 This is a cross-sectional view partially showing a portion of the first inner fin of the fifth embodiment in the second cross section, and is equivalent to Figure 8 Picture.

[0060] Figure 26 This is a cross-sectional view partially showing a portion of the first inner fin of the sixth embodiment in the second cross section, and is equivalent to Figure 8 Picture.

[0061] Figure 27 This is a cross-sectional view partially showing a portion of the first inner fin of the seventh embodiment in the second cross section, and is equivalent to Figure 8 Picture.

[0062] Figure 28 This is a cross-sectional view partially showing a portion of the first inner fin of the eighth embodiment in the second cross section, and is equivalent to Figure 8 Picture.

[0063] Figure 29 This is a cross-sectional view partially showing a portion of the first inner fin of the ninth embodiment in the second cross section, and is equivalent to Figure 8 Picture.

[0064] Figure 30 This represents the equivalent of the tenth embodiment Figure 2 The cross-sectional view of the cross section of III-III is equivalent to Figure 3 Picture. DETAILED DESCRIPTION

[0065] Hereinafter, each embodiment will be described with reference to the accompanying drawings. In addition, the same or equivalent parts in each of the following embodiments are denoted by the same reference numerals in the drawings.

[0066] (First embodiment)

[0067] like Figure 1 As shown, in this embodiment, a heat exchanger 1 is used as a cooler for cooling a plurality of electronic components 2. This heat exchanger 1 is a stacked-type heat exchanger having a plurality of flow tubes 3 arranged in a stacked arrangement. Heat exchanger 1 exchanges heat between a heat medium flowing through the flow tubes 3 and the electronic components 2, thereby cooling the electronic components 2, which are the objects of heat exchange. The electronic components 2 are components that form part of a power conversion device, such as an inverter circuit, mounted on a vehicle and converting direct current into alternating current.

[0068] like Figures 1 to 3 As shown, the heat exchanger 1 includes a plurality of flow tubes 3 , a plurality of first inner fins 34 , and a plurality of second inner fins 35 .

[0069] The heat medium for heat exchange with the electronic components 2 flows through the flow tubes 3. Specifically, in each of the plurality of flow tubes 3, the heat medium flows through the flow tubes 3 with one side of the flow direction Df in the tube being the upstream side of the heat medium flow and the other side of the flow direction Df being the downstream side of the heat medium flow. For example, the flow direction Df in the tube is consistent with the longitudinal direction of the flow tube 3. For example, Figure 2 As shown in FIG. 1 , a pair of peripheral portions in the short side direction of the flow tube 3 extend in parallel along the long side direction, and the shape of the peripheral end portion in the long side direction of the flow tube 3 is semicircular. Figure 2 The direction perpendicular to the flow direction Df in the pipe.

[0070] In this embodiment, the heat medium for exchanging heat with the electronic component 2 is liquid. For example, water mixed with an ethylene glycol-based antifreeze solution, water, a natural refrigerant such as ammonia, etc. can be used as the heat medium.

[0071] The flow tube 3 is in the first cross section perpendicular to the flow direction Df in the tube (ie, Figure 3 The cross section of the ) is flat. Figures 1 to 3 As shown, the flow tube 3 has the flat cross-sectional shape and extends in the flow direction Df in the tube. Figure 3 The long side direction Dw of the flat cross-sectional shape of the flow tube 3 represented by the cross section is referred to as the flat long side direction Dw, and the thickness direction Dt of the flat cross-sectional shape (in other words, the short side direction Dt of the flat cross-sectional shape) is referred to as the flat thickness direction Dt. The flat long side direction Dw, the flat thickness direction Dt, and the in-tube flow direction Df are directions intersecting with each other, or more precisely, directions perpendicular to each other.

[0072] In the heat exchanger 1, a plurality of flow tubes 3 are stacked in the flat thickness direction Dt, sandwiching the electronic components 2 therebetween. In other words, the flow tubes 3 and the electronic components 2 are stacked alternately in the flat thickness direction Dt. Therefore, the flat thickness direction Dt also serves as the stacking direction for the plurality of flow tubes 3.

[0073] Furthermore, in order to improve heat transfer between the flow tube 3 and the electronic component 2 in contact with the flow tube 3 , the electronic component 2 is pressed in the flat thickness direction Dt by the pair of flow tubes 3 interposing the electronic component 2 and is held in this pressed state.

[0074] In addition, although Figure 2 Yes Figure 1 The sectional view of section II-II is shown, but Figure 2 In order to clarify the shape of the flow tube 3, the electronic component 2 is omitted. Figure 2In FIG, the first inner fin 34 disposed inside the flow tube 3 is indicated by a dotted line. Figure 2 、 Figure 3 、 Figure 5 、 Figure 6 、 Figure 16 In the figures corresponding thereto, the communication portion 364 described later is omitted for simplification of the illustration.

[0075] The flow tube 3 is formed by laminating and joining metal plate members having high thermal conductivity such as aluminum alloy and copper alloy. Figure 3 and Figure 4 As shown, the flow tube 3 includes a pair of outer plates 31, 32 and an intermediate plate 33. For example, at portions where the pair of outer plates 31, 32, the intermediate plate 33, the first inner fins 34, and the second inner fins 35 contact each other, the contacting parts are joined by brazing.

[0076] The outer shell plates 31 and 32 are plate members that form the outer shell of the flow tube 3. Heat exchange between the electronic components 2 and the heat medium occurs via these plates. Specifically, the first outer shell plate 31, one of the pair of outer shell plates 31 and 32, is positioned on one side of the second outer shell plate 32, the other, in the flat thickness direction Dt. Furthermore, the first outer shell plate 31 is stacked on the second outer shell plate 32 in the flat thickness direction Dt, such that the in-tube flow paths 3a and 3b, which constitute the internal space of the flow tube 3, are formed between the first and second outer shell plates 31 and 32.

[0077] The intermediate plate 33 is composed of a flat plate member. The intermediate plate 33 is disposed between the pair of outer shell plates 31 and 32, and divides the internal space of the flow tube 3 in the flat thickness direction Dt, and extends in the flow direction Df in the tube. Figure 5 As shown, through-holes 33a and 33b are formed at one end and the other end of the intermediate plate 33, respectively corresponding to the openings of the protruding tube portions 411 and 412, which will be described later. The first inner fin 34 and the second inner fin 35 are arranged inside the flow tube 3 and are positioned between the two through-holes 33a and 33b in the flow direction Df within the tube.

[0078] like Figure 2 and Figure 3 As shown, each flow tube 3 is provided with one first inner fin 34 and one second inner fin 35. Both the first inner fin 34 and the second inner fin 35 increase the heat transfer area between the electronic component 2 and the heat medium within the flow tube 3, thereby promoting heat exchange between the electronic component 2 and the heat medium. For example, the first inner fin 34 and the second inner fin 35 are formed by stamping a metal plate having high thermal conductivity, such as an aluminum alloy.

[0079] The first inner fins 34 and second inner fins 35 are identical components, but their placement differs. Specifically, the first inner fins 34 are located in the in-tube flow path 3a formed between the first outer shell plate 31 and the intermediate plate 33, while the second inner fins 35 are located in the in-tube flow path 3b formed between the second outer shell plate 32 and the intermediate plate 33. In other words, within the flow tube 3, the first inner fins 34 are located on one side of the intermediate plate 33 in the flat thickness direction Dt, while the second inner fins 35 are located on the other side of the intermediate plate 33 in the flat thickness direction Dt.

[0080] Therefore, the first inner fins 34 divide the inner flow path 3a, which is the internal space of the flow tube 3, into a plurality of narrow flow paths 30a arranged in the flat longitudinal direction Dw. Similarly, the second inner fins 35 divide the inner flow path 3b, which is the internal space of the flow tube 3, into a plurality of narrow flow paths 30b arranged in the flat longitudinal direction Dw.

[0081] Furthermore, the second inner fins 35 are arranged in a direction that reverses the first inner fins 34 in the flat thickness direction Dt. The second inner fins 35 are identical to the first inner fins 34 except for their arrangement direction and position. For example, the communication portions 364, described later, provided on the first inner fins 34 are also provided on the second inner fins 35 with the same structure as the first inner fins 34. Therefore, in the description of this embodiment, the first inner fins 34 will be primarily described, and the description of the second inner fins 35 will be omitted.

[0082] like Figure 3 As shown, the first inner fin 34 has a cross-sectional wave shape in the first cross section, wherein a convex shape 341 protruding toward one side of the flat thickness direction Dt and a convex shape 342 protruding toward the other side of the flat thickness direction Dt are alternately connected and extend toward the flat longitudinal direction Dw. Figure 2 and Figure 6 As shown, the first inner fins 34 extend in the tube flow direction Df within the tube flow path 3a.

[0083] For example, the shape of the plurality of fine flow paths 30a in the first cross section of the first inner fin 34 is as follows: Figure 3 That is, the first inner fin 34 divides the in-tube flow path 3a in such a manner that the narrow flow paths 30a that widen toward the flat longitudinal direction Dw as they move toward one side of the flat thickness direction Dt and the narrow flow paths 30a that widen toward the flat longitudinal direction Dw as they move toward the other side of the flat thickness direction Dt are alternately arranged in the flat longitudinal direction Dw.

[0084] In other words, in the first cross-section, one of the two adjacent thin flow paths 30a in the flat longitudinal direction Dw has a trapezoidal cross-sectional shape, with the other side in the flat thickness direction Dt being wider than the one side in the flat thickness direction Dt. Furthermore, the other of the two adjacent thin flow paths 30a has a trapezoidal cross-sectional shape, with the one side in the flat thickness direction Dt being wider than the other side in the flat thickness direction Dt.

[0085] like Figure 1 、 Figure 2 、 Figure 4 As shown, the heat exchanger 1 includes a plurality of protruding tube portions 411 and 412. These protruding tube portions 411 and 412 are provided at one end and the other end of the flow tube 3 in the tube flow direction Df, respectively, and are formed to protrude from the flow tube 3 in the flat thickness direction Dt. For example, the one-side protruding tube portion 411 protruding in the one-side flat thickness direction Dt is formed as a single component with the first outer shell plate 31, and the other-side protruding tube portion 412 protruding in the other-side flat thickness direction Dt is formed as a single component with the second outer shell plate 32.

[0086] The multiple protruding tube sections 411 and 412 are pipes that connect adjacent flow tubes 3 in the flat thickness direction Dt, and are formed, for example, into a cylindrical shape. For example, the protruding tube section 411 and the protruding tube section 412 provided at one end of the flow tube 3 in the pipe flow direction Df are coaxially aligned. Similarly, the protruding tube section 411 and the protruding tube section 412 provided at the other end of the flow tube 3 in the pipe flow direction Df are coaxially aligned.

[0087] Specifically, in the arrangement of the plurality of flow tubes 3 constituting the heat exchanger 1 , the flow tubes 3 excluding the pair of flow tubes 3 located outermost in the flat thickness direction Dt are provided with a pair of one-side protruding tube portions 411 and a pair of other-side protruding tube portions 412 .

[0088] On the other hand, the flow tube 3 at the end on one side in the flat thickness direction Dt of the arrangement of the plurality of flow tubes 3 is provided with a pair of other-side protruding tube portions 412, but is not provided with a one-side protruding tube portion 411. Furthermore, the flow tube 3 at the end on the other side in the flat thickness direction Dt of the arrangement of the plurality of flow tubes 3 is provided with a pair of one-side protruding tube portions 411, but is not provided with a other-side protruding tube portion 412.

[0089] The plurality of flow tubes 3 are connected by fitting the protruding tube portions 411 and 412 facing each other and joining the side walls of the protruding tube portions 411 and 412. As a result, the inner flow paths 3a and 3b of one of the flow tubes 3 adjacent to each other in the flat thickness direction Dt are connected to the inner flow paths 3a and 3b of the other of the flow tubes 3 adjacent to each other (see Figure 3 For example, the side walls of the protruding tube portions 411 and 412 are joined to each other by brazing.

[0090] like Figure 1 As shown, the medium introduction portion 4 is a pipe for introducing the heat medium into the heat exchanger 1, and the medium discharge portion 5 is a pipe for discharging the heat medium from the heat exchanger 1. The heat exchanger 1 includes the medium introduction portion and the medium discharge portion 5.

[0091] The medium inlet portion 4 and the medium outlet portion 5 are connected to the flow tube 3 located at one end of the arrangement of the plurality of flow tubes 3 in the flat thickness direction Dt. Specifically, the medium inlet portion 4 is connected to the end of the flow tube 3 on one side in the tube flow direction Df and is coaxially aligned with the other protruding tube portion 412 provided at the one end. Furthermore, the medium outlet portion 5 is connected to the end of the flow tube 3 on the other side in the tube flow direction Df and is coaxially aligned with the other protruding tube portion 412 provided at the other end. For example, the medium inlet portion 4 and the medium outlet portion 5 are each brazed to the flow tube 3.

[0092] Since the medium inlet 4 and the medium outlet 5 are connected to the flow tube 3, the protruding tube portions 411 and 412 provided at one end of the flow tube 3 in the flow direction Df constitute the supply header 11. Furthermore, the protruding tube portions 411 and 412 provided at the other end of the flow tube 3 in the flow direction Df constitute the discharge header 12. The supply header 11 is a header for supplying the medium to the flow channels 3a and 3b in the flow tube 3 (see FIG. Figure 3 ) is a pipe for supplying heat medium, and the discharge header portion 12 is a pipe for discharging heat medium from the in-tube flow paths 3a and 3b of the flow path pipe 3.

[0093] The heat medium is supplied from a pump (not shown) to the heat exchanger 1 through the medium introduction portion 4 , and is returned from the heat exchanger 1 to the pump through the medium discharge portion 5 .

[0094] As described above, the first inner fin 34 has a cross-sectional wave shape in the first cross section. Figure 7 and Figure 8 As shown, the first inner fin 34 is in a second cross section perpendicular to the flat thickness direction Dt (ie, Figure 7 The first inner fin 34 has a corrugated shape 36 in the cross section thereof. In short, the first inner fin 34 is configured as a corrugated fin.

[0095] The corrugated shape 36 of the first inner fin 34 is a shape in which one side top 361 and the other side top 362 are alternately arranged in the flow direction Df of the tube via the middle portion 363 in the second cross section. Figure 3 ) between each other, and in the second cross section, it is a convex shape that is curved and raised toward one side of the flat long side direction Dw. The other side top 362 is a partition wall portion arranged between the plurality of thin flow paths 30a, and in the second cross section, it is a convex shape that is curved and raised toward the other side of the flat long side direction Dw.

[0096] Furthermore, in the first inner fin 34, a plurality of corrugated shapes 36 are arranged in parallel in the flat longitudinal direction Dw, and the tops 361 on one side and the tops 362 on the other side of the corrugated shapes 36 are connected in the flow direction Df in the tube via the intermediate portion 363. Thus, the first inner fin 34 has the plurality of tops 361 on one side, the plurality of tops 362 on the other side, and the plurality of intermediate portions 363 forming the corrugated shapes 36. Figure 7 express Figure 3 Section VII-VII.

[0097] In addition, if Figure 8 and Figure 9 As shown, the middle portion 363 of the first inner fin 34 is not a partition structure that continuously connects the top portion 361 on one side and the top portion 362 on the other side. Specifically, the middle portion 363 includes a connecting portion 364 with a connecting opening 364a, a side wall portion 365, and a side wall portion 366. The connecting opening 364a is formed as a hole that opens in the flow direction Df within the tube and connects two adjacent thin flow paths 30a across the first inner fin 34 among the plurality of thin flow paths 30a.

[0098] exist Figure 8 In the corrugated shape 36, when described with reference to the top portion 361 on one side, a communication portion 364 and a side wall portion 365 are provided on one side of the top portion 361 in the pipe flow direction Df, and a communication portion 364 and a side wall portion 365 are also provided on the other side. Furthermore, the side wall portion 365 extends from the top portion 361 adjacent to the communication portion 364 in the pipe flow direction Df to the communication portion 364, and separates two adjacent thin flow paths 30a.

[0099] In addition, Figure 8In the corrugated shape 36, when described with reference to the other-side top 362, a communication portion 364 and a second side wall portion 366 are provided on one side of the other-side top 362 in the tube flow direction Df, and a communication portion 364 and a second side wall portion 366 are also provided on the other side. Furthermore, the second side wall portion 366 extends from the other-side top 362 adjacent to the communication portion 364 in the tube flow direction Df to the communication portion 364, and separates two adjacent thin flow paths 30a.

[0100] In addition, if Figure 8 and Figure 9 As shown, the plurality of communication openings 364a are arranged in the middle portion 363 away from the one side top 361 and the other side top 362. In other words, the plurality of communication openings 364a are not provided at either the one side top 361 or the other side top 362, but are provided between the one side top 361 and the other side top 362 in the flow direction Df within the tube.

[0101] For example, in this embodiment, the communication openings 364a are not provided in any of the one side tops 361 and the other side tops 362 of the first inner fins 34. Instead, the communication openings 364a are formed in each of the intermediate portions 363 aligned in the tube flow direction Df.

[0102] In addition, when explaining the opening shape of the communication port 364a, Figure 8 and Figure 10 As shown, the communication portion 364 has a peripheral edge 364b of a communication opening 364a. The peripheral edge 364b of the communication opening 364a includes an end edge 365a of a side wall portion 365 and an end edge 366a of a side wall portion 366. The end edge 365a of the pair of side walls 365 is located on the side of the side wall portion 365 opposite to the side top 361, and the end edge 366a of the side wall portion 366 is located on the side of the side wall portion 366 opposite to the side top 362.

[0103] Furthermore, the end edge 365a of the side wall portion 365 is formed so as to be parallel to the end edge 366a of the other side wall portion 366 in the flat longitudinal direction Dw. In short, the end edge 365a of the side wall portion 365 is formed by paralleling the end edge 366a of the other side wall portion 366 in the flat longitudinal direction Dw. More specifically, as indicated by arrow Aof, the end edge 365a of the side wall portion 365 is formed by paralleling the end edge 366a of the other side wall portion 366 in the other side of the flat longitudinal direction Dw. Focusing on each of the connecting portions 364, in each of the multiple connecting portions 364, the end edge 365a of the side wall portion 365 is positioned on the other side of the flat longitudinal direction Dw relative to the end edge 366a of the other side wall portion 366.

[0104] In addition, the shape of the first inner fin 34 is as follows: Figure 10 and Figure 11 As shown, the first inner fin 34 is configured as an offset fin having a predetermined offset shape. This offset shape is formed by parallel displacement of the first convex portion 371 relative to the second convex portion 372 so as to widen the communication opening 364a in the flat longitudinal direction Dw. Specifically, this offset shape is formed by parallel displacement of the first convex portion 371 relative to the second convex portion 372 toward the other side in the flat longitudinal direction Dw so as to widen the communication opening 364a in the flat longitudinal direction Dw.

[0105] The first convex portion 371 includes a top portion 361 on one side and a pair of side walls 365 arranged in the pipe flow direction Df across the top portion 361. Meanwhile, the second convex portion 372 includes a top portion 362 on the other side and a pair of side walls 366 arranged in the pipe flow direction Df across the top portion 362 on the other side. The first convex portions 371 and the second convex portions 372 are arranged alternately in the pipe flow direction Df.

[0106] In the second section Figure 8 In the cross-section of FIG, the one-side top portion 361 disposed between two adjacent communication openings 364a in the pipe flow direction Df is disposed between the two adjacent communication openings 364a, offset to one side in the pipe flow direction Df. The configuration of the other-side top portion 362 is similar. That is, in the second cross-section, the other-side top portion 362 disposed between two adjacent communication openings 364a in the pipe flow direction Df is disposed between the two adjacent communication openings 364a, offset to one side in the pipe flow direction Df.

[0107] in short, Figure 8 The first distance C1 shown in the flow direction Df in the tube is greater than the second distance C2. Here, the position of the vertex of the top 361 on one side or the top 362 on the other side arranged between two adjacent communication ports 364a in the flow direction Df in the tube is referred to as the vertex position Pf. The first distance C1 refers to the distance in the flow direction Df in the tube between the vertex position Pf and the other communication port 364a of the two adjacent communication ports 364a, which is located on the other side of the flow direction Df in the tube relative to the vertex position Pf. In addition, the second distance C2 refers to the distance in the flow direction Df in the tube between the vertex position Pf and the communication port 364a of the two adjacent communication ports 364a, which is located on the side of the flow direction Df in the tube relative to the vertex position Pf.

[0108] Next, in order to compare with the heat exchanger 1 of this embodiment, the heat exchanger of Patent Document 1 is described as a first comparative example. In this first comparative example, Figure 12 As shown in the first cross section, the opening shape of the communication port 71a is a triangular shape that tapers toward one side or the other side in the flat thickness direction Dt. The communication port 71a of the first comparative example corresponds to the communication port 364a of this embodiment.

[0109] Furthermore, in the communication port 71a of the first comparative example, the length of one of the two sides 711a and 711b forming the triangular shape and extending in the flat thickness direction Dt is different from the length of the other side 711b. In this respect, the heat exchanger of the first comparative example differs significantly from the heat exchanger 1 of the present embodiment.

[0110] For example, Figure 12 As shown, in the heat exchanger of the first comparative example, a compressive external force Fa acts in the flat thickness direction Dt on the flow tube housing the inner fin 70 having the communication port 71a. This causes a portion of the inner fin 70 to buckle around the communication port 71a. In this case, the periphery of the communication port 71a deforms to reduce the difference between the length of the long side portion corresponding to the longer side 711a and the short side portion corresponding to the shorter side 711b. Therefore, as indicated by the dashed line Lfa and arrow Afa, the long side portion corresponding to the longer side 711a of the communication port 71a buckles before the short side portion corresponding to the shorter side 711b.

[0111] Specifically, in the heat exchanger of the first comparative example, when the long and short sides of the periphery of the communication port 71a buckle due to the compressive external force Fa, the buckling occurs at different times. This is because the length of one side 711a around the communication port 71a differs from the length of the other side 711b. Therefore, this difference in length between the one side 711a and the other side 711b is believed to be one factor contributing to the reduced strength of the inner fin 70.

[0112] In contrast, according to this embodiment, Figure 8 and Figure 10 As shown, the peripheral edge 364b of the communication port 364a in the first inner fin 34 includes an end edge 365a of a side wall portion 365 and an end edge 366a of the other side wall portion 366. Furthermore, the end edge 365a of the side wall portion 365 is formed so as to be parallel to the end edge 366a of the other side wall portion 366 in the flat longitudinal direction Dw.

[0113] Therefore, the communication port 364a is formed so that the length of the end edge 365a of the one side wall portion 365 is the same or substantially the same as the length of the end edge 366a of the other side wall portion 366. Figure 12 ) When the end edge 365a of the one side wall portion 365 and the end edge 366a of the other side wall portion 366 bend, the timing of their respective bending coincides. Therefore, when compared with the heat exchanger of the first comparative example described above, the reduction in strength of the first inner fin 34 caused by the provision of the communication portion 364 can be suppressed without miniaturizing the plurality of narrow flow paths 30a within the flow tube 3.

[0114] If the strength reduction of the first inner fins 34 is suppressed in this manner, the flow tube 3 can be pressed against the electronic component 2 more strongly, thereby reducing the thermal resistance between the flow tube 3 and the electronic component 2 .

[0115] Furthermore, since the first inner fins 34 of this embodiment are formed with a plurality of communication openings 364a, the heat transfer performance between the first inner fins 34 and the heat medium can be improved compared to a case without the communication openings 364a. Furthermore, stagnation of the heat medium flow in the plurality of narrow flow paths 30a can be reduced.

[0116] Here, in order to explain the first comparative example again, Figure 13 As shown, it is assumed that in the first comparative example, a compressive external force Fa in the flat thickness direction Dt acts on the inner fin 70. In this case, between two adjacent communication ports 71a in the flow direction Df in the tube, the compressive external force Fa is received by the pressure-bearing surface FC1 facing the direction opposite to the compressive external force Fa. In the first comparative example, since the communication port 71a is formed in the above-mentioned triangular shape, the width of the pressure-bearing surface FC1 on one side in the flow direction Df in the tube is narrower than that on the opposite side. Therefore, compared with the case where there is no communication port, for example, where the communication port 71a is not formed and the wave shape of the inner fin 70 is maintained in the cross-section Sx, the pressure-bearing area, which is the area of ​​the pressure-bearing surface FC1, is reduced. Figure 13 Therefore, in the first comparative example, it is considered that the strength of the inner fin 70 against the compressive external force Fa is reduced.

[0117] In contrast, according to this embodiment, Figure 8 and Figure 10As shown, in each of the plurality of communicating portions 364, the end edge 365a of the side wall portion 365 is formed so as to be parallel to the end edge 366a of the other side wall portion 366 in the flat longitudinal direction Dw. Therefore, the pressure-bearing surface FC1 of the first inner fin 34 of this embodiment has the same width on one side or the other side of the tube flow direction Df, thereby obtaining a pressure-bearing area equivalent to that of the case without the communicating port. For example, in this embodiment, it is possible to obtain Figure 13 The pressure receiving area is the sum of the area of ​​the pressure receiving surface FC1 of the first comparative example and the area of ​​the double-dashed line region FCa. Therefore, compared with the first comparative example, in this embodiment, the compressive external force Fa (see Figure 13 ) the strength of the first inner fin 34 is improved.

[0118] In addition, if the purpose is only to improve the strength of the first inner fin 34, although it is conceivable to increase the thickness of the first inner fin 34, Figure 3 While increasing the number of pitches of the cross-sectional corrugated shape shown above presents significant disadvantages, such as increasing the thickness of the first inner fins 34, the cross-sectional area of ​​each of the plurality of narrow flow paths 30a decreases, leading to an increase in the pressure loss of the heat medium flowing through the narrow flow paths 30a. Furthermore, the workability of the first inner fins 34 deteriorates.

[0119] Furthermore, even if the number of pitches of the cross-sectional corrugation in the first inner fin 34 is increased, there is a disadvantage that the pressure loss of the heat medium flowing in the narrow flow path 30a increases. In addition, increasing the number of pitches of the cross-sectional corrugation inherently has a dimensional limitation.

[0120] In addition, according to this embodiment, Figure 10 and Figure 11 As shown, the first inner fin 34 is configured as an offset fin having a predetermined offset shape. Furthermore, this offset shape is formed by the first convex portion 371 being parallel-shifted relative to the second convex portion 372 toward the other side in the flat-long direction Dw, so as to widen the communication opening 364a in the flat-long direction Dw. This offset shape is referred to as a positive offset shape. In this positively offset first inner fin 34, in each of the multiple communication portions 364, the end edge 365a of the one side wall portion 365 is positioned toward the other side in the flat-long direction Dw relative to the end edge 366a of the other side wall portion 366.

[0121] Therefore, the first inner fin 34 having the positive offset shape can reduce pressure loss in the heat medium flowing through the plurality of narrow flow paths 30 a compared to the inner fin having the negative offset shape offset in the opposite direction of the positive offset shape.

[0122] To illustrate this effect, Figure 14 and Figure 15 In the second comparative example, as shown in FIG. Figure 14 and Figure 15 As shown, the inner fin 76 is configured as an offset fin with a negative offset shape. Furthermore, this negative offset shape is the result of the first convex portion 371 being parallel-shifted relative to the second convex portion 372 toward one side in the planar-longitudinal direction Dw, thereby widening the communication opening 364a in the planar-longitudinal direction Dw. In short, this negative offset shape is the result of the first convex portion 371 being parallel-shifted relative to the second convex portion 372, as indicated by the arrow Bof, from a state without the communication opening 364a.

[0123] Here, in the second comparative example, the heat medium in the narrow flow path 30a flows as follows: Figure 14 As shown by arrows FLa and FLb, the position where the communication port 364a is provided is divided into two by the end edges 365a and 366a of the side wall portion 365 or the other side wall portion 366 opposite to the heat medium flow. Figure 8 Same as shown. Figure 8 and Figure 14 Specifically, arrows FLa and FLb indicate the heat medium flow divided into two by the end edge 365 a of the one side wall portion 365 .

[0124] In the second comparative example, when the heat medium flow is divided into two as described above, after the division into two, Figure 14 The heat medium flow indicated by arrow FLa immediately tilts relative to the pipe flow direction Df and collides with the opposing wall surface 365b facing upstream. At this point, the heat medium flow does not pass through the communication port 364a but instead passes through the adjacent port 301a adjacent to the communication port 364a before colliding with the opposing wall surface 365b. While the opposing wall surface 365b can also be the surface of the other side wall portion 366 depending on its location, it is the surface of the one side wall portion 365 in this description.

[0125] Furthermore, the adjacent interface 301a has a shape with a different width (ie, the width in the flat longitudinal direction Dw) depending on the position in the flat thickness direction Dt. Figure 15 The adjacent interface 301a shown is shaped such that the width of the narrow region R1 in the adjacent interface 301a, which is located on the other side of the flat thickness direction Dt, is smaller than the width of the other regions. Therefore, the heat medium flow passing through the narrow region R1 in the adjacent interface 301a strongly collides with the opposite wall surface 365b near the narrow region R1. Figure 15 The same applies to other locations other than the illustrated locations. As a result, in the second comparative example, the pressure loss generated in the heat medium flowing through the plurality of narrow flow paths 30a increases.

[0126] On the other hand, in this embodiment, when the heat medium flow is divided into two, after the division into two, Figure 8 The heat medium flow on one side indicated by the arrow FLa immediately collides with the opposite wall surface 365b. This is the same as the second comparative example, but in this embodiment, the heat medium flow on one side does not pass through the adjacent port 301a but collides with the opposite wall surface 365b after passing through the communication port 364a. In addition, the communication port 364a is not limited to the position in the flat thickness direction Dt, but is as shown by the arrow Wa (see FIG. Figure 10 ) is formed in a shape with the same width. Therefore, in this embodiment, the heat medium flow colliding with the opposite wall surface 365b does not collide strongly with the opposite wall surface 365b as the heat medium in the second comparative example. Figure 10 The same applies to other locations other than the illustrated locations. Therefore, in this embodiment, the pressure loss generated in the heat medium flowing through the plurality of narrow flow paths 30a can be reduced compared to the second comparative example.

[0127] In addition, although in this embodiment Figure 8 The other heat medium flow, indicated by arrow FLb, passes through adjacent port 301a, but there is no opposing wall 365b or equivalent wall surface with which the other heat medium flow would collide immediately after passing through it. Therefore, even if the other heat medium flow passes through connection port 364a instead of adjacent port 301a, the heat medium pressure loss caused by the other heat medium flow passing through adjacent port 301a remains virtually unchanged. In other words, regardless of whether the adjacent port 301a or the connecting port 364a, which serves as the passage opening through which the heat medium flow passes, is the passage opening on the side that does not collide with the opposing wall 365b or equivalent wall surface, there is no difference in the heat medium pressure loss.

[0128] In addition, according to this embodiment, Figure 8 and Figure 9 As shown, the communication port 364a of the first inner fin 34 is arranged in the middle portion 363 away from each of the top portion 361 on one side and the top portion 362 on the other side. Therefore, compared with the case where the communication port 364a is arranged at the top portion 361 on one side or the top portion 362 on the other side, the compressive external force Fa in the flat thickness direction Dt (see FIG. Figure 16 ) the strength of the first inner fin 34 is improved.

[0129] To illustrate this, for example Figure 16As shown in the figure, it is assumed that a compressive external force Fa acts in the flat thickness direction Dt on the flow tube 3 that accommodates the first inner fin 34. In this case, since the pair of side walls 365 arranged across the side top 361 are inclined with respect to the flat thickness direction Dt, the compressive external force Fa also acts on the side wall 365, causing it to tilt.

[0130] That is, the compressive external force Fa has a component force Fb directed in the flow direction Df within the tube at one side wall portion 365. These components Fb are mutually opposed at the pair of side wall portions 365. In this embodiment, as described above, the communication port 364 is positioned away from the one side top portion 361, and since the one side top portion 361 is connected to the pair of side wall portions 365, the components Fb in the mutually opposed directions cancel each other out.

[0131] That is, the pair of side walls 365 disposed across the one-side top 361 are structured to support each other and overcome the compressive external force Fa. Since the communication opening 364a is also disposed away from the other-side top 362, the same applies to the pair of other-side wall portions 366 disposed across the other-side top 362. Therefore, as described above, the strength of the first inner fin 34 against the compressive external force Fa in the flat thickness direction Dt can be improved compared to a case where the communication opening 364a is disposed at either the one-side top 361 or the other-side top 362.

[0132] In addition, according to this embodiment, Figure 3 In the first cross-section shown above, one of the two adjacent thin channels 30a in the planar longitudinal direction Dw has a trapezoidal cross-sectional shape, with the other side in the planar thickness direction Dt being wider than the one side in the planar thickness direction Dt. Furthermore, the other of the two adjacent thin channels 30a has a trapezoidal cross-sectional shape, with one side in the planar thickness direction Dt being wider than the other side in the planar thickness direction Dt. Therefore, the sidewall surface facing the thin channel 30a in the planar longitudinal direction Dw is an inclined surface that is tilted relative to the planar thickness direction Dt.

[0133] Therefore, compared with a case where the side wall surface facing the narrow flow channel 30a is parallel to the flat thickness direction Dt, for example, the effect of stirring the heat medium flowing in the narrow flow channel 30a in the flat thickness direction Dt can be enhanced.

[0134] In addition, according to this embodiment, Figure 8 In the second cross section shown above, the top portion 361 disposed between two adjacent communication openings 364a in the pipe flow direction Df is disposed between the two adjacent communication openings 364a to be offset toward one side in the pipe flow direction Df.

[0135] Here, of the pair of side walls 365 disposed across the top portion 361, the downstream side wall 365, extending from the top portion 361 toward the other side of the pipe flow direction Df, has a diverting function for diverting the heat medium flow after passing through the communication port 364a or the adjacent port 301a. In contrast, the upstream side wall 365, extending from the top portion 361 toward the one side of the pipe flow direction Df, does not have this diverting function. The upstream side wall 365 only needs to have a length sufficient to distribute the heat medium flow toward the communication port 364a and the adjacent port 301a.

[0136] In this embodiment, since the top portion 361 is positioned offset toward one side of the tube flow direction Df between two adjacent communication openings 364a in the longitudinal direction Dw, the downstream side wall portion 365, which provides the aforementioned diverting function, can be formed longer. This enhanced diverting function promotes the ripple flow of the heat medium flowing within the narrow flow path 30a, thereby enhancing the heat exchange performance between the electronic component 2 and the heat medium.

[0137] In addition, Figure 8 In the second cross-section shown above, the other-side top portion 362, located between two adjacent communication openings 364a in the tube flow direction Df, is also located between these two adjacent communication openings 364a, offset toward one side in the tube flow direction Df. Consequently, as described above, the deflection function is enhanced around the other-side top portion 362 of the first inner fin 34, thereby promoting the ripple flow of the heat medium flowing within the narrow flow path 30a, thereby improving the heat exchange performance between the electronic component 2 and the heat medium.

[0138] In addition, according to this embodiment, Figure 8 As shown, one of the edge 365a of one side wall portion 365 and the edge 366a of the other side wall portion 366, included in the peripheral edge 364b of the communication opening 364a, forms the leading edge of the wall portion facing the heat medium flow in the narrow flow path 30a. This leading edge is located in a portion of the narrow flow path 30a where the heat medium flows rapidly. Therefore, the leading edge effect of this wall portion can be enhanced, which improves the heat exchange performance between the first inner fin 34 and the heat medium.

[0139] (Second embodiment)

[0140] Next, the second embodiment will be described. In this embodiment, the differences from the first embodiment will be mainly described. In addition, the same or equivalent parts as those in the above embodiment will be omitted or simplified. This also applies to the description of the following embodiments.

[0141] In this embodiment, if Figure 17As shown, the angles formed by each of the pair of side wall portions 365 disposed across the one side top portion 361 relative to the flow direction Df in the tube are different from each other. Furthermore, the angles formed by each of the pair of other side wall portions 366 disposed across the other side top portion 362 relative to the flow direction Df in the tube are also different from each other. In this respect, this embodiment differs from the first embodiment.

[0142] In the description of this embodiment, among the plurality of one side tops 361 and the plurality of other side tops 362, the one side tops 361 and the other side tops 362 located on the other side of the communicating portion 364 in the tube flow direction Df and adjacent thereto are referred to as side wall tops 36a. The first inner fin 34 includes a pair of extended wall portions 36b and 36c extending from the side wall top 36a and arranged across the side wall top 36a. The pair of extended wall portions 36b and 36c separate two adjacent thin flow paths 30a in the flat longitudinal direction Dw.

[0143] The pair of side wall portions 365 disposed across the top 361 of the side wall top 36a, and the pair of other side wall portions 366 disposed across the top 362 of the side wall top 36a, respectively correspond to the pair of extended wall portions 36b and 36c. Therefore, one of the pair of extended wall portions 36b and 36c, the extended wall portion 36b, extends from the side wall top 36a toward one side in the flow direction Df within the tube. Furthermore, the other of the pair of extended wall portions 36b and 36c, the extended wall portion 36c, extends from the side wall top 36a toward the other side in the flow direction Df within the tube.

[0144] And, in Figure 17 In the second cross-section shown above, the other side elevation angle θc, which is the elevation angle θc formed between the other extended wall portion 36c and the flow direction Df within the tube, is larger than the one side elevation angle θb, which is the elevation angle θb formed between the one extended wall portion 36b and the flow direction Df within the tube. The one side elevation angle θb is the smaller of the two angles formed between the one extended wall portion 36b and the flow direction Df within the tube. Furthermore, the other side elevation angle θc is the smaller of the two angles formed between the other extended wall portion 36c and the flow direction Df within the tube.

[0145] Here, when the other extended wall portion 36c corresponds to, for example, the one side wall portion 365 of the one side wall portion 365 and the other side wall portion 366, in detail, the other extended wall portion 36c corresponds to the aforementioned downstream side wall portion 365. Therefore, the other extended wall portion 36c has the aforementioned diverting function of diverting the flow of the heat medium after passing through the communication port 364a or the adjacent port 301a.

[0146] In this embodiment, since the one-side elevation angle θb and the other-side elevation angle θc are in the relationship of "θc>θb" as described above, the above-mentioned diversion function can be improved compared to the case where the relationship is reversed, "θc<θb". Therefore, the ripple flow of the heat medium flowing in the narrow flow path 30a is promoted, thereby improving the heat exchange performance between the electronic component 2 and the heat medium. In addition, in the first embodiment described above, Figure 8 It can be seen that the one-side elevation angle θb and the other-side elevation angle θc are equal in magnitude.

[0147] Except for the above-described contents, this embodiment is the same as the first embodiment. Also, in this embodiment, similarly to the first embodiment, the effects obtained by the configuration common to the first embodiment can be obtained.

[0148] (Third embodiment)

[0149] Next, a third embodiment will be described. In this embodiment, differences from the first embodiment described above will be mainly described.

[0150] like Figures 18 to 20 As shown, any one or all of the plurality of intermediate plates 363 include a cut-and-raised wall portion 38 having a cut-and-raised portion 381, and this cut-and-raised wall portion 38 is provided as one side wall portion 365 or the other side wall portion 366. In other words, any one or all of the plurality of side walls 365 and the plurality of other side walls 366 include a cut-and-raised portion 381. In this embodiment, a portion of the plurality of side walls 365 and a portion of the plurality of other side walls 366 each include a cut-and-raised portion 381. This aspect differs from the first embodiment.

[0151] Specifically, the cut-and-raised portion 381 is louver-shaped, protruding toward the narrow flow path 30a. Furthermore, the cut-and-raised portion 381 is cut and folded so that the through-hole 381a extending through the cut-and-raised wall portion 38 is formed on one side or the other side of the cut-and-raised portion 381 in the flow direction Df within the tube. That is, the cut-and-raised portion 381 is positioned on one side or the other side of the flow direction Df within the tube relative to the through-hole 381a formed by the cut-and-folded portion 381. In this embodiment, the through-hole 381a is formed on one side of the cut-and-raised portion 381 in the flow direction Df within the tube, and the through-hole 381a is also formed on the other side of the cut-and-raised portion 381 in the flow direction Df within the tube.

[0152] Furthermore, the cut-and-raised portion 381 and the through-hole 381 a extend in the flat thickness direction Dt. Therefore, both the top and base ends of the cut-and-raised portion 381 extend in the flat thickness direction Dt.

[0153] Thus, according to this embodiment, the cut-and-raised portions 381 of the first inner fins 34 are cut and folded to form through-holes 381a in the cut-and-raised wall portions 38. Therefore, the heat medium also flows through the through-holes 381a of the cut-and-raised wall portions 38 between adjacent narrow flow paths 30a in the planar longitudinal direction Dw, thereby promoting heat transfer between the heat medium and the first inner fins 34. As a result, the heat exchange performance between the electronic component 2 and the heat medium can be improved.

[0154] In addition, according to this embodiment, the cut and raised portion 381 is cut and folded so that the through hole 381a is formed on one side or the other side of the pipe flow direction Df of the cut and raised portion 381. Therefore, the cut and raised portion 381 also overcomes the compressive external force Fa (see Figure 12 ).

[0155] Therefore, compared to the case where the opening is provided in the inner fin, for example, as in Patent Document 1, the middle portion 363 having the cut-and-raised portion 381 can make the first inner fin 34 less likely to bend in the flat thickness direction Dt. Thus, when compared to the heat exchanger of Patent Document 1, for example, the multiple narrow flow paths 30a within the flow tube 3 can be miniaturized, thereby suppressing the reduction in strength of the first inner fin 34 caused by providing the through-hole 381a in the middle portion 363.

[0156] Except for the above-described contents, this embodiment is the same as the first embodiment. Also, in this embodiment, similarly to the first embodiment, the effects obtained by the configuration common to the first embodiment can be obtained.

[0157] In addition, this embodiment is a modification example based on the first embodiment, and this embodiment can also be combined with the above-mentioned second embodiment.

[0158] (Fourth embodiment)

[0159] Next, a fourth embodiment will be described. In this embodiment, differences from the third embodiment described above will be mainly described.

[0160] In the third embodiment described above, if Figure 20 As shown in FIG. 3 , each cut-and-raised wall portion 38 is provided with a cut-and-raised portion 381 and a through hole 381a. Figures 21 to 23 As shown, each cut-and-raised wall portion 38 is provided with two cut-and-raised portions 381 and a through-hole 381a. In other words, in this embodiment, a plurality of cut-and-raised portions 381, which are cut and folded to form the through-hole 381a in the cut-and-raised wall portion 38, are provided on each of the plurality of cut-and-raised wall portions 38. This aspect differs from the third embodiment.

[0161] Except for the above-described contents, this embodiment is the same as the third embodiment. Also, in this embodiment, similarly to the third embodiment, the effects obtained by the configuration common to the third embodiment can be obtained.

[0162] (Fifth embodiment)

[0163] Next, a fifth embodiment will be described. In this embodiment, differences from the first embodiment described above will be mainly described.

[0164] In the first embodiment described above, Figure 8 As shown, the peripheral edge 364b of the communication port 364a is formed so that the positions of the end edge 365a of the one side wall portion 365 and the end edge 366a of the other side wall portion 366 included in the peripheral edge 364b are the same in the pipe flow direction Df.

[0165] In contrast, in this embodiment, the peripheral edge 364b of the communication port 364a is as shown in FIG. Figure 24 and Figure 25 That is, the peripheral edge 364b of the communication port 364a is formed so that the position of the end edge 365a of the one side wall portion 365 included in the peripheral edge 364b and the position of the end edge 366a of the other side wall portion 366 are different from each other in the pipe flow direction Df.

[0166] Specifically, the one side wall portion 365 and the other side wall portion 366 of the communicating portion 364 are separated in the pipe flow direction Df. In other words, the communicating portion 364 is shaped such that one of the one side wall portion 365 and the other side wall portion 366 extending therefrom is set back relative to the other in the pipe flow direction Df.

[0167] In addition, in this embodiment, unlike the first embodiment, the first distance C1 (see Figure 8 ) and the second distance C2 are the same size.

[0168] Except for the above-described contents, this embodiment is the same as the first embodiment. Also, in this embodiment, similarly to the first embodiment, the effects obtained by the configuration common to the first embodiment can be obtained.

[0169] In addition, this embodiment is a modification of the first embodiment, and this embodiment can be combined with any of the second to fourth embodiments described above.

[0170] (Sixth embodiment)

[0171] Next, a sixth embodiment will be described. In this embodiment, differences from the first embodiment described above will be mainly described.

[0172] In the first embodiment described above, Figure 8 As shown, the peripheral edge 364b of the communication port 364a is formed so that the positions of the end edge 365a of the one side wall portion 365 and the end edge 366a of the other side wall portion 366 included in the peripheral edge 364b are the same in the pipe flow direction Df.

[0173] In contrast, in this embodiment, the peripheral edge 364b of the communication port 364a is as shown in FIG. Figure 26 That is, the peripheral edge 364b of the communication port 364a is formed so that the position of the end edge 365a of the one side wall portion 365 included in the peripheral edge 364b and the position of the end edge 366a of the other side wall portion 366 are different from each other in the pipe flow direction Df.

[0174] Specifically, in the communication portion 364, one side wall portion 365 is partially overlapped with the other side wall portion 366 on one side or the other side in the planar longitudinal direction Dw. In other words, the communication portion 364 has a shape in which one side wall portion 365 and the other side wall portion 366 extending to the communication portion 364 overlap with the other side on one side or the other side in the planar longitudinal direction Dw.

[0175] In addition, in this embodiment, unlike the first embodiment, the first distance C1 (see Figure 8 ) and the second distance C2 are the same size.

[0176] Except for the above-described contents, this embodiment is the same as the first embodiment. Also, in this embodiment, similarly to the first embodiment, the effects obtained by the configuration common to the first embodiment can be obtained.

[0177] In addition, this embodiment is a modification of the first embodiment, and this embodiment can be combined with any of the second to fourth embodiments described above.

[0178] (Seventh embodiment)

[0179] Next, a seventh embodiment will be described. In this embodiment, differences from the first embodiment described above will be mainly described.

[0180] In this embodiment, if Figure 27 As shown, the first inner fin 34 has a second cross section perpendicular to the flat thickness direction Dt (ie, Figure 27In the cross-section (see FIG. 2 ), a plurality of corrugated shapes 36 are arranged in parallel in the longitudinal direction Dw and extend in the flow direction Df within the tube. Furthermore, the corrugated shapes 36 are formed by connecting one side top 361 and the other side top 362 via an intermediate portion 363 in the flow direction Df within the tube. In this respect, this embodiment is the same as the first embodiment.

[0181] However, this embodiment is different from the first embodiment in that a first convex portion 371 (see Figure 11 ) is not a shape offset in the flat longitudinal direction Dw with respect to the second convex portion 372. Furthermore, the communication port 364a is not formed in the portion that is not offset.

[0182] Specifically, among the plurality of corrugated shapes 36 arranged in the planar longitudinal direction Dw, none of the intermediate portions 363 of the corrugated shapes 36 disposed at the end portion on one side in the planar longitudinal direction Dw have the communication openings 364a formed therein. In short, the corrugated shapes 36 disposed at the end portion on this one side have no communication openings 364a.

[0183] And, although in Figure 27 Although not shown in the figure, the communication openings 364a are not formed in all the middle portions 363 of the corrugated shapes 36 that form the end portion arranged on the other side in the flat longitudinal direction Dw. In short, the communication openings 364a are not provided in the corrugated shapes 36 that are arranged on the other side.

[0184] With this structure, according to this embodiment, it is possible to prevent the heat medium in the flow pipe 3 from flowing toward the end in the flat longitudinal direction Dw through the communication port 364a. If a large amount of heat medium in the flow pipe 3 flows toward the end in the flat longitudinal direction Dw, the heat exchange performance between the heat medium in the flow pipe 3 and the electronic component 2 will be reduced.

[0185] In addition, in this embodiment, the first distance C1 (see Figure 8 ) and the second distance C2 are the same size.

[0186] Except for the above-described contents, this embodiment is the same as the first embodiment. Also, in this embodiment, similarly to the first embodiment, the effects obtained by the configuration common to the first embodiment can be obtained.

[0187] In addition, this embodiment is a modification of the first embodiment, and this embodiment can be combined with any of the second to sixth embodiments described above.

[0188] (Eighth Embodiment)

[0189] Next, an eighth embodiment will be described. In this embodiment, differences from the first embodiment described above will be mainly described.

[0190] like Figure 28 As shown, in this embodiment, in a portion of the first inner fin 34, the first convex portion 371 (see Figure 11 ) is offset in the flattened longitudinal direction Dw relative to the second convex portion 372. Furthermore, in the portion not having this offset shape, the intermediate portion 363 does not have the communicating portion 364 having the communicating opening 364a. This embodiment differs from the first embodiment in this respect.

[0191] Specifically, in this embodiment, the communication portion 364 is provided in the first inner fin 34 as a part of the Figure 28 Therefore, the communication portions 364 of the first inner fin 34 are distributed more densely in the central portion than on one side and the other side in the tube flow direction Df.

[0192] With this structure, according to this embodiment, the central portion of the first inner fin 34, which facilitates high heat exchange performance between the electronic component 2 and the heat medium within the flow tube 3, can actively promote heat exchange between the electronic component 2 and the heat medium via the communication portion 364. Furthermore, by eliminating or reducing the number of communication portions 364 in areas of the first inner fin 34 other than the central portion, the pressure loss generated by the heat medium flowing through the narrow flow channel 30a can be reduced.

[0193] In addition, in this embodiment, the first distance C1 (see Figure 8 ) and the second distance C2 are the same size.

[0194] Except for the above-described contents, this embodiment is the same as the first embodiment. Also, in this embodiment, similarly to the first embodiment, the effects obtained by the configuration common to the first embodiment can be obtained.

[0195] In addition, this embodiment is a modification of the first embodiment, and this embodiment can be combined with any of the second to seventh embodiments described above.

[0196] (Ninth embodiment)

[0197] Next, a ninth embodiment will be described. In this embodiment, differences from the first embodiment described above will be mainly described.

[0198] like Figure 29As shown, the communication portion 364 includes an edge 365a of one side wall portion 365 and an edge 366a of the other side wall portion 366, which form the peripheral edge 364b of the communication opening 364a. Furthermore, one of the two edges 365a and 366a (i.e., the edge of one end) faces the upstream side of the heat medium flow of the narrow flow path 30b, while the other faces the downstream side of the heat medium flow. In this respect, this embodiment is similar to the first embodiment.

[0199] However, unlike the first embodiment, this embodiment has one end edge of the peripheral edge 364b of the communication port 364a, in other words, the end edge facing the heat medium flow of the narrow flow path 30a, which has a pointed shape that tapers toward the top in the second cross-section. For example, the opposite end edge has a sharp shape in the second cross-section.

[0200] With this structure, in this embodiment, the heat medium flow smoothly splits at the opposite edges as indicated by arrows FLc and FLd. Therefore, the heat medium flow is less likely to separate from the wall surface around the opposite edges, thereby suppressing the increase in pressure loss caused by the heat medium flow separating from the wall surface.

[0201] Except for the above-described contents, this embodiment is the same as the first embodiment. Also, in this embodiment, similarly to the first embodiment, the effects obtained by the configuration common to the first embodiment can be obtained.

[0202] In addition, this embodiment is a modification example based on the first embodiment, and this embodiment can be combined with any of the second to eighth embodiments described above.

[0203] (Tenth embodiment)

[0204] Next, a tenth embodiment will be described. In this embodiment, differences from the first embodiment described above will be mainly described.

[0205] In the first embodiment described above, Figure 3 As shown, two in-tube flow paths 3a and 3b are formed in the flow path tube 3 in a stacked manner in the flat thickness direction Dt via an intermediate plate 33. In contrast, in this embodiment, as shown in FIG. Figure 30 As shown, one of the two in-tube flow paths 3a and 3b is provided in the flow tube 3, while the other in-tube flow path 3b is not provided. That is, the in-tube flow path 3a is not stacked in the flow tube 3, and thus has a single-layer structure.

[0206] Furthermore, since the in-tube flow channel 3 a in the flow channel tube 3 has a single-layer structure, the flow channel tube 3 includes the first outer shell plate 31 and the second outer shell plate 32 , but does not include the intermediate plate 33 .

[0207] In addition, although the second shell plate 32 of the present embodiment is formed of a flat plate member, it may also have a concave shape with the first shell plate 31 side being the concave side, similarly to the first embodiment.

[0208] Except for the above-described contents, this embodiment is the same as the first embodiment. Also, in this embodiment, similarly to the first embodiment, the effects obtained by the configuration common to the first embodiment can be obtained.

[0209] In addition, this embodiment is a modification example based on the first embodiment, and this embodiment can be combined with any of the second to ninth embodiments described above.

[0210] (Other embodiments)

[0211] (1) In each of the above embodiments, Figure 1 As shown, the heat exchanger 1 is used as a cooler to cool a plurality of electronic components 2 as heat exchange objects. However, the use of the heat exchanger 1 is not limited to vehicles and can be used in various types, and the heat exchange objects are not limited to electronic components 2. Alternatively, the heat exchanger 1 can be used as a heater to heat the heat exchange objects.

[0212] (2) In the above embodiments, the heat medium flowing in the flow tubes 3 of the heat exchanger 1 is a liquid. However, this is merely an example. For example, the heat medium may be a gas or a fluid that changes phase between a gas phase and a liquid phase in the flow tubes 3.

[0213] (3) In each of the above embodiments, if Figure 2 As shown in the figure, the flow direction Df in the tube is the longitudinal direction of the flow tube 3, but this is an example. For example, the flat longitudinal direction Dw may be the longitudinal direction of the flow tube 3.

[0214] (4) In the first embodiment described above, if Figure 3 As shown, the peripheral edge of the flow tube 3 is sandwiched between the pair of outer shell plates 31 and 32. However, this is merely an example. The intermediate plate 33 may not reach the peripheral edge of the flow tube 3, and the entire intermediate plate 33 may be housed within the interior space of the flow tube 3. Alternatively, the flow tube 3 may not include the intermediate plate 33, and the first inner fins 34 and the second inner fins 35 may be stacked in contact with each other within the flow tube 3.

[0215] (5) In the second embodiment described above, if Figure 17 As shown, although the one side elevation angle θb and the other side elevation angle θc have a magnitude relationship of "θc>θb", this magnitude relationship of "θc>θb" does not necessarily hold at all locations where the side wall top 36a is provided.

[0216] (6) In the second embodiment described above, if Figure 17 As shown, the pair of extended wall portions 36b and 36c extend from the side wall top portion 36a to the communication portion 364 adjacent to the side wall top portion 36a in the pipe flow direction Df. However, this is merely an example. It is also possible that the other extended wall portion 36c of the pair of extended wall portions 36b and 36c does not extend to the communication portion 364. Therefore, the other extended wall portion 36c does not necessarily correspond to either the one side wall portion 365 or the other side wall portion 366 extending to the communication portion 364.

[0217] (7) In the description of the first embodiment above, although Figure 14 and Figure 15 The second comparative example is shown for comparison with the first embodiment, but the second comparative example may also be interpreted as one of a plurality of embodiments.

[0218] (8) In the third and fourth embodiments described above, if Figure 20 and Figure 23 As shown, in addition to the through hole 381a formed by the cut-and-raised portion 381, the middle portion 363 also has a communication port 364a. However, this is an example. For example, it is also possible to form the through hole 381a in the middle portion 363 without forming the communication port 364a.

[0219] In the structure where the communication port 364a is not formed, the intermediate portion 363 is Figure 20 and Figure 23 In the second cross section, the intermediate portion 363 is formed as a wall extending from one top portion 361 to the other top portion 362. The intermediate portion 363 separates two adjacent thin flow paths 30a in the longitudinal direction Dw across the first inner fin 34 among the plurality of thin flow paths 30a.

[0220] Furthermore, the cut-and-raised portion 381 of the middle portion 363 is cut and folded so that the through-hole 381a is formed in the middle portion 363. Specifically, the cut-and-raised portion 381 is cut and folded so that the through-hole 381a penetrating the middle portion 363 is formed on one side or the other side of the cut-and-raised portion 381 in the pipe flow direction Df.

[0221] Thus, for example, by providing the through-holes 381 a formed by the cut-and-raised portions 381 instead of the openings provided in the inner fins of Patent Document 1, the heat exchange performance of the heat exchanger 1 can be improved.

[0222] In addition, similarly to the third and fourth embodiments, the cut-and-raised portion 381 overcomes the compressive external force Fa (see Figure 12), it is possible to suppress a reduction in the strength of the first inner fin 34 caused by providing the through hole 381a in the middle portion 363.

[0223] (9) In the third and fourth embodiments described above, if Figure 20 and Figure 23 As shown, among the plurality of cut-and-raised portions 381, there is a cut-and-raised portion 381 having a through-hole 381a formed on one side of the cut-and-raised portion 381 in the pipe flow direction Df. Furthermore, there is also a cut-and-raised portion 381 having a through-hole 381a formed on the other side of the cut-and-raised portion 381 in the pipe flow direction Df. However, this is merely an example.

[0224] For example, all of the cut-and-raised portions 381 provided on the first inner fin 34 may form the through-hole 381a on one side of the cut-and-raised portion 381 in the tube flow direction Df. Alternatively, conversely, all of the cut-and-raised portions 381 provided on the first inner fin 34 may form the through-hole 381a on the other side of the cut-and-raised portion 381 in the tube flow direction Df.

[0225] (10) In the first embodiment described above, if Figure 8 As shown, the first inner fin 34 is provided with a plurality of communication portions 364 each having a communication port 364a, but this is merely an example. For example, it is also conceivable that only one communication portion 364 is provided on the first inner fin 34.

[0226] (11) In the third and fourth embodiments described above, if Figure 20 and Figure 23 As shown, the first inner fin 34 is provided with a plurality of through-holes 381a and cut-and-raised portions 381, but this is merely an example. For example, it is also possible to provide only one through-hole 381a and only one cut-and-raised portion 381 on the first inner fin 34.

[0227] (12) The present invention is not limited to the above-mentioned embodiments and can be implemented in various modifications. In addition, the above-mentioned embodiments are not mutually exclusive and can be appropriately combined except for cases where the combination is obviously impossible.

[0228] In addition, in each of the above embodiments, the elements constituting the embodiments are not necessarily required, except in cases where they are specifically stated to be required or in cases where they are clearly required in principle, and this is self-evident. In addition, in each of the above embodiments, when the number, value, amount, range, and other numerical values ​​of the elements constituting the embodiments are mentioned, they are not limited to the specific numbers, except in cases where they are specifically stated to be required or in cases where they are clearly limited to a specific number in principle, and this is self-evident. In addition, in each of the above embodiments, when the materials, shapes, positional relationships, and the like of the elements are mentioned, they are not limited to the specific materials, shapes, positional relationships, and the like, except in cases where they are specifically stated to be required or in cases where they are limited to a specific material, shape, positional relationship, and the like in principle, and this is self-evident.

Claims

1. A heat exchanger for exchanging heat between an object to be exchanged and a heat medium, the heat exchanger comprising: a flow pipe having a flat cross-sectional shape in a first cross-section perpendicular to one direction, wherein the heat medium flows through the flow pipe with one side in the one direction being an upstream side of the flow of the heat medium and the other side in the one direction being a downstream side of the flow of the heat medium; and An inner fin is arranged inside the flow tube to divide the internal space of the flow tube into a plurality of thin flow paths arranged in the long side direction of the flat cross-sectional shape. The inner fin has a cross-sectional wave shape in the first cross-section, in which a convex shape on one side and a convex shape on the other side are alternately connected and extend in the long side direction. The convex shape on one side bulges toward one side in the thickness direction of the flat cross-sectional shape, and the convex shape on the other side bulges toward the other side in the thickness direction, and the inner fin extends in the one direction. The inner fin has a corrugated shape in which one side top and the other side top are alternately arranged in the one direction via a middle portion in a second cross-section perpendicular to the thickness direction, the one side top is arranged between the plurality of fine flow paths and is curved so as to bulge toward one side in the longitudinal direction, and the other side top is arranged between the plurality of fine flow paths and is curved so as to bulge toward the other side in the longitudinal direction. The middle portion includes a communicating portion, a side wall portion, and another side wall portion, wherein the communicating portion is formed with a communicating port that connects two adjacent thin flow paths across the inner fin among the plurality of thin flow paths, the one side wall portion extends from the top portion of the one side adjacent to the communicating portion in the one direction to the communicating portion and separates the two adjacent thin flow paths, and the other side wall portion extends from the top portion of the other side adjacent to the communicating portion in the one direction to the communicating portion and separates the two adjacent thin flow paths. The inner fin is provided with one or more communicating portions. The communication port is arranged in the middle portion away from each of the one side top and the other side top. In the first cross-section perpendicular to the one direction, the periphery of the communication port includes an end edge of the one side wall portion and an end edge of the other side wall portion, and the end edge of the one side wall portion is formed in a manner that allows the end edge of the other side wall portion to move parallel to the long side direction.

2. The heat exchanger according to claim 1, characterized in that The inner fin is configured as an offset fin having an offset shape in which a first convex portion including the one top and the one side wall is parallelly displaced relative to a second convex portion including the other top and the other side wall in the longitudinal direction to widen the communication port.

3. The heat exchanger according to claim 2, characterized in that The offset shape is a shape obtained by parallel shifting the first convex portion relative to the second convex portion toward the other side in the longitudinal direction so as to widen the communication opening in the longitudinal direction.

4. The heat exchanger according to claim 1 or 2, characterized in that The inner fin is provided with a plurality of the communication portions. In each of the plurality of communicating portions, an end edge of the one side wall portion is arranged on the other side in the longitudinal direction relative to an end edge of the other side wall portion.

5. The heat exchanger according to claim 1 or 2, characterized in that In the first section, the cross-sectional shape of one of the two adjacent thin flow paths is a trapezoidal shape in which the other side in the thickness direction is wider than the one side in the thickness direction, and the cross-sectional shape of the other of the two adjacent thin flow paths is a trapezoidal shape in which the one side in the thickness direction is wider than the other side in the thickness direction.

6. The heat exchanger according to claim 1 or 2, characterized in that In the second cross-section, the elevation angle formed by the extended wall portion of one of the pair of extended wall portions and the one direction is larger than the elevation angle formed by the extended wall portion of the other of the pair of extended wall portions and the one direction. The pair of extended wall portions extend from the top of the side wall and are arranged across the top of the side wall, and separate the two adjacent thin flow paths. The top of the side wall is the top of one side or the top of the other side that is adjacent to the other side of the one direction relative to the connecting portion. The extended wall portion of one side extends from the top of the side wall to the one side of the one direction and is equivalent to the one side wall portion or the other side wall portion. The extended wall portion of the other side extends from the top of the side wall to the other side of the one direction.

7. The heat exchanger according to claim 1 or 2, characterized in that The communication port is formed in each of the intermediate portions arranged in the one direction. In the second cross section, the top portion on one side or the top portion on the other side disposed between the two adjacent communication openings in the one direction is disposed between the two adjacent communication openings so as to be offset toward the one side in the one direction.

8. The heat exchanger according to claim 1 or 2, characterized in that A plurality of the flow tubes are stacked in the thickness direction with the heat exchange object interposed therebetween. The heat exchange object is pressed in the thickness direction by the pair of flow tubes sandwiching the heat exchange object.

9. The heat exchanger according to claim 1 or 2, characterized in that A first inner fin and a second inner fin are provided as the inner fins, The flow tube has an intermediate plate that divides the inner space of the flow tube in the thickness direction and extends in the one direction. Inside the flow tube, the first inner fin is arranged on the one side in the thickness direction relative to the intermediate plate, and the second inner fin is arranged on the other side in the thickness direction relative to the intermediate plate.

10. The heat exchanger according to claim 1 or 2, characterized in that The inner fin has a plurality of the communication portions. The communication portions are distributed densely in a central portion of the inner fin in the one direction than in the one side and the other side in the one direction.

11. The heat exchanger according to claim 1 or 2, characterized in that The middle portion has a cut-and-raised wall portion, which is provided as the one side wall portion or the other side wall portion and has a cut-and-raised portion. The cut-and-raised portion is in a cut and folded shape, so that a through hole penetrating the cut-and-raised wall portion is formed on the one side or the other side of the cut-and-raised portion in the one direction. The inner fin is provided with one or more through holes and one or more cut-and-raised portions.

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