Heat exchange core and heat exchanger

Abstract

In the header portion of the heat exchange core, the header flow path includes at least one radial flow path extending in the radial direction and a plurality of circumferential flow paths branched from the respective radial flow paths and communicating with one or more axial flow paths. In each radial flow path, the flow path area at a second position radially inward of the first position is smaller than the flow path area at the first position.

Description

Technical Field

[0001] The present disclosure relates to a heat exchange core and a heat exchanger.

[0002] This application claims priority based on Japanese Patent Application No. 2020-031381 and Japanese Patent Application No. 2020-031402 filed on February 27, 2020, and incorporates their contents herein. Background Art

[0003] For example, a cylindrical heat exchanger in which a flow path group is formed inside a cylindrical housing is known. Generally, in a cylindrical heat exchanger, in order to perform heat exchange between a first fluid and a second fluid, it is configured such that either the first fluid or the second fluid flows in and out from an axial end portion of the cylindrical housing, and the other fluid flows in and out along the radial direction from the side portion of the housing (for example, refer to Patent Document 1).

[0004] Prior Art Documents

[0005] Patent Documents

[0006] Patent Document 1: Japanese Patent Application Laid-Open No. 2018-519490 Summary of the Invention

[0007] Problems to be Solved by the Invention

[0008] In the cylindrical heat exchanger as described above, the flow of the fluid flowing into the housing along the radial direction is turned in the axial direction, and the flow of the fluid flowing in the housing along the axial direction is turned in the radial direction. Therefore, the flow rate of the fluid flowing in the housing may vary depending on the circumferential and radial positions, and the heat exchange efficiency may be reduced due to such a difference in flow rate. In order to suppress such a flow rate difference, it is desirable to ensure a space for turning the flow direction of the fluid to a certain extent. Therefore, it is difficult to miniaturize the cylindrical heat exchanger while ensuring a relatively high heat exchange efficiency.

[0009] In view of the above circumstances, an object of at least one embodiment of the present disclosure is to provide a heat exchange core that can be miniaturized while ensuring a relatively high heat exchange efficiency.

[0010] Means for Solving the Problems

[0011] (1) The heat exchange core of at least one embodiment of the present disclosure includes:

[0012] a core main body portion including a plurality of axial flow paths extending in the axial direction; and

[0013] a header portion adjacent to at least one end of the core main body portion in the axial direction and having a header flow path communicating with the plurality of axial flow paths,

[0014] The header flow path includes:

[0015] At least one radial flow path extending radially; and

[0016] A plurality of circumferential flow paths branching from respective ones of the radial flow paths and communicating with more than one of the axial flow paths,

[0017] In each of the radial flow paths, the flow path area at a second position radially inside the first position is smaller than the flow path area at the first position.

[0018] (2) The heat exchange core according to at least one embodiment of the present disclosure includes:

[0019] A core main body including a plurality of axial flow paths extending in the axial direction; and

[0020] A header portion adjacent to at least one end of the core main body in the axial direction and having a header flow path communicating with the plurality of axial flow paths,

[0021] The header flow path includes:

[0022] At least one radial flow path extending radially; and

[0023] A plurality of circumferential flow paths branching from any one of the radial flow paths and communicating with more than one of the axial flow paths,

[0024] The plurality of circumferential flow paths include:

[0025] A first circumferential flow path; and

[0026] A second circumferential flow path located radially inside the first circumferential flow path and circumferentially arranged within a total angle range larger than that of the first circumferential flow path.

[0027] (3) The heat exchanger according to at least one embodiment of the present disclosure, wherein

[0028] The heat exchanger includes:

[0029] A heat exchange core having the structure of (1) or (2) above; and

[0030] A housing that houses the heat exchange core.

[0031] Advantageous Effects of the Invention

[0032] According to at least one embodiment of the present disclosure, it is possible to miniaturize the heat exchange core while ensuring a relatively high heat exchange efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] Figure 1It is an exploded perspective view of a heat exchange core and a housing included in heat exchangers according to several embodiments.

[0034] Figure 2 It shows Figure 1 A partial cross-sectional view of the housing of the heat exchanger shown and the heat exchange core housed in the housing.

[0035] Figure 3A It is Figure 2 A cross-sectional view taken along line IIIa-IIIa (the first cross-section of the heat exchange core), and shows a first flow path group and a second flow path group.

[0036] Figure 3B It is Figure 3A A partially enlarged view. In the drawings other than this figure, the illustration of the dividing wall W2 is omitted.

[0037] Figure 4 It is Figure 2 A cross-sectional view taken along line IV-IV. (The second cross-section of the heat exchange core)

[0038] Figure 5 It is Figure 2 and Figure 6 A cross-sectional view taken along line V-V. (The third cross-section of the heat exchange core)

[0039] Figure 6 It is a schematic diagram showing the flow of each of the first fluid and the second fluid.

[0040] Figure 7 It is a cross-sectional view showing a part of the heat exchange core according to a modified example of the present disclosure.

[0041] Figure 8 It is a diagram schematically showing a part near a header portion in a side surface of the heat exchange core according to several embodiments, and shows an example of the shape of an opening portion.

[0042] Figure 9 It is a diagram schematically showing a part near a header portion in a side surface of the heat exchange core according to several embodiments, and shows another example of the shape of an opening portion.

[0043] Figure 10 It is a schematic diagram for explaining the change in the flow path area of a radial flow path with respect to the radial position.

[0044] Figure 11 It is a schematic diagram for explaining the change in the flow path area of a radial flow path with respect to the radial position.

[0045] Figure 12 It is a flowchart showing the processing steps in the manufacturing method of the heat exchange core according to several embodiments.

[0046] Figure 13 is a cross-sectional view taken along line IV-IV in a modified example of a radial flow path and a circumferential flow path. Figure 2

[0047] Figure 14 is a schematic diagram showing the flow of each of a first fluid and a second fluid in a modified example of a radial flow path and a circumferential flow path.

[0048] Figure 15A is a schematic diagram for explaining a radial flow path and a circumferential flow path in one embodiment in a modified example of a radial flow path and a circumferential flow path.

[0049] Figure 15B is a schematic diagram for explaining a radial flow path and a circumferential flow path in another embodiment in a modified example of a radial flow path and a circumferential flow path.

[0050] Figure 16 is a schematic diagram for explaining a total angle range. DETAILED DESCRIPTION

[0051] Hereinafter, several embodiments of the present disclosure will be described with reference to the drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of the components described as embodiments or shown in the drawings are not intended to limit the scope of the present disclosure thereto, and are merely illustrative examples.

[0052] For example, expressions indicating relative or absolute arrangements such as "in a certain direction", "along a certain direction", "parallel", "orthogonal", "center", "concentric", or "coaxial" not only represent such strict arrangements, but also represent states in which there are displacements in terms of angles and distances within tolerances or to an extent that can achieve the same function.

[0053] For example, expressions indicating equal states of things such as "same", "equal", and "homogeneous" not only represent strictly equal states, but also represent states in which there are differences within tolerances or to an extent that can achieve the same function.

[0054] For example, expressions indicating shapes such as a quadrilateral shape and a cylindrical shape not only represent geometrically strict quadrilateral shapes, cylindrical shapes, etc., but also represent shapes including concavo-convex portions, chamfered portions, etc. within a range where the same effects can be obtained.

[0055] On the other hand, expressions such as "providing", "disposing", "having", "including", or "comprising" a component do not exclude the existence of other components.

[0056] (Schematic Structure of Heat Exchanger)

[0057] As Figure 1 and Figure 2As shown, the heat exchanger 1 of several embodiments includes a heat exchange core 10 and a housing 20 that houses the heat exchange core 10.

[0058] The heat exchanger 1 of several embodiments can be assembled, for example, to chemical equipment such as gas turbines and CO2 recovery devices, or to devices not shown such as air conditioners and freezers, and, for example, heat exchange between a first fluid and a second fluid is performed. For example, the temperature of the first fluid is relatively high and the temperature of the second fluid is relatively low. Conversely, the temperature of the first fluid may be relatively low and the temperature of the second fluid may be relatively high.

[0059] (Structure of the heat exchange core)

[0060] The heat exchange core 10 of several embodiments includes a core main body portion 13 and header portions 11A and 11B adjacent to one end and the other end in the axial direction of the core main body portion 13. For ease of explanation, the header portion 11A adjacent to one end in the axial direction of the core main body portion 13 is also referred to as the first header portion 11A, and the header portion 11B adjacent to the other end in the axial direction is also referred to as the second header portion 11B.

[0061] Figure 3A is Figure 2 A cross-sectional view taken along line IIIa-IIIa. The core main body portion 13 of several embodiments includes, as described later, a plurality of axial flow paths 3 extending along the axial direction, that is, a part of a plurality of first flow paths 101 and a plurality of second flow paths 102.

[0062] The header portions 11A and 11B of several embodiments each have a header flow path 6 (see Figure 6 ) that communicates with the plurality of axial flow paths 3, as will be described in detail later.

[0063] As Figure 1 and Figure 3A shown, the heat exchange core 10 of several embodiments includes a first flow path group G1 and a second flow path group G2 that are integrally arranged in a concentric circle shape.

[0064] The heat exchanger 1 of several embodiments includes Figure 3A a first cross-section C1 shown in Figure 4 , a second cross-section C2 shown in Figure 5 , and a third cross-section C3 shown in

[0065] . These cross-sections C1 to C3 are all circular. The overall outer shape of the heat exchange core 10 is formed in a cylindrical shape. The heat exchange core 10 includes a partition wall (first partition wall) W1 that is arranged in a concentric circle shape and separates the first flow path group G1 and the second flow path group G2, and a side wall W0 arranged on the outermost periphery of the heat exchange core 10.

[0065] The heat exchange core 10 not only has an outer shape, but also has a shape that is symmetric with respect to the center of the cross sections C1 to C3, that is, the central axis (axis AX) of the heat exchange core 10 having a cylindrical shape. Thus, in addition to the stress homogenization, it is also possible to contribute to the homogenization of the heat exchange efficiency.

[0066] In the heat exchanger 1 of several embodiments, the first flow path group G1 corresponds to the first fluid, and the second flow path group G2 corresponds to the second fluid. In each figure, the first flow path group G1 is marked with a shaded pattern.

[0067] The second flow path group G2 of several embodiments extends from one end portion 10A ( Figure 1 ) of the axial direction D1 of the heat exchange core 10 to the other end portion 10B ( Figure 1 ). The axial direction D1 is orthogonal to the cross sections C1 to C3. That is, in several embodiments, the plurality of second flow paths 102 are included in the axial flow path 3.

[0068] In each figure, the flow of the first fluid is indicated by a solid arrow, and the flow of the second fluid is indicated by a dashed arrow.

[0069] In several embodiments, the first flow path 101 constituting the first flow path group G1 is arranged in a circular ring shape in the first cross section C1 shown in Figure 3A . The same applies to the second flow path 102 constituting the second flow path group G1. In several embodiments, the first fluid flowing in the first flow path group G1 and the second fluid flowing in the second flow path group G2 are indirectly contacted via the first partition wall W1 shown by the thick line in Figure 3A , and thus heat is exchanged.

[0070] As shown in Figure 3A , it is preferable that the plurality of first flow paths 101 and the plurality of second flow paths 102 are alternately stacked several tens of layers in the radial direction of the heat exchange core 10.

[0071] The first flow path 101 and the second flow path 102 are preferably arranged in the entire radial direction of the heat exchange core 10, that is, up to the vicinity of the axis of the heat exchange core 10, that is, the vicinity of the axis AX. In Figure 3A , Figure 3B , Figure 4 and Figure 5 , only a part of the first flow paths 101 and a part of the second flow paths 102 are shown. The illustration of the remaining first flow paths 101 and second flow paths 102 in the region indicated by "..." is omitted.

[0072] As in the present embodiment, by arranging the first flow path 101 and the second flow path 102 in the entire radial direction of the heat exchange core 10, the entire heat exchange core 10 can contribute to heat exchange.

[0073] In several embodiments, the heat exchange core 10 may be within the range between the IV-IV line and the IVx-IVx line shown in Figure 2 and have a constant cross-sectional shape corresponding to the first cross-section C1 ( Figure 3A ). In this range, that is, within the range from near one end 10A of the heat exchange core 10 to near the other end 10B, in the present embodiment, the first fluid and the second fluid flow in opposite directions along the axial direction D1. That is, except for the two ends, within substantially the entire range of the axial direction D1 of the heat exchange core 10, the first fluid and the second fluid form a countercurrent (complete countercurrent).

[0074] The first fluid and the second fluid may also flow along the axial direction D1 in the same orientation. In this case, the first fluid and the second fluid form a parallel flow.

[0075] In consideration of the required heat exchange capacity, stress, etc., appropriate dimensions in the axial direction D1 and the radial direction, flow path cross-sectional area, number of layers of the flow paths 101, 102, etc. are given to the heat exchange core 10 of several embodiments.

[0076] As shown in Figure 3B , it is preferable that each of the first flow paths 101 and each of the second flow paths 102 are divided into a plurality of partitions S by the dividing wall W2 in the circumferential direction D2 of the heat exchange core 10. By providing the dividing wall W2, it is possible to improve the rigidity and strength, particularly in the radial direction, against the pressure of the fluid.

[0077] In addition, the first flow path 101 and the second flow path 102 are each subdivided into partitions S by the dividing wall W2, whereby the surface area of the flow path in contact with the fluid increases, and thus the heat transfer efficiency can be improved.

[0078] The partitions S are preferably arranged over the entire circumference of the heat exchange core 10 with equal flow path diameters. Moreover, it is preferable to give equal flow path diameters to all the partitions S from the outermost circumference to the axis of the heat exchange core 10. In this way, as a result of the flow states such as frictional losses being homogenized in all the partitions S, it is possible to homogenize the heat transfer rate for all the partitions S, and the stress acting on the heat exchange core 10 is evenly dispersed in the entire in-plane direction of the cross-section of the heat exchange core 10, thereby enabling stress homogenization.

[0079] The "flow path diameter" in this specification corresponds to the equivalent diameter D given by the following formula (1).

[0080] D = 4A / L...(1)

[0081] A: Cross-sectional area of the partition S

[0082] L: Length (circumference) of the partition S in the circumferential direction D2

[0083] Since the heat conductivity is equivalent to the reciprocal of the flow path diameter, it is preferable to assign an appropriate flow path diameter to the partition S based on this.

[0084] The heat exchange core 10 of several embodiments can use a metal material such as stainless steel or aluminum alloy that has properties suitable for the fluid, and can be integrally formed including the partition wall W2 by means of laminated molding or the like. According to the laminated molding, for example, by repeatedly supplying metal powder to the forming area in the device, irradiating with a laser beam or an electron beam based on two-dimensional data representing a cross-section of a three-dimensional shape, melting the metal powder, and solidifying the metal powder, a formed object with a two-dimensional shape laminated thereon can be obtained.

[0085] In several embodiments, the thickness of the wall W1 or the like in the heat exchange core 10 obtained by laminated molding using a metal material is, for example, 0.3 to 3 mm.

[0086] The heat exchange core 10 of several embodiments is manufactured through a step of forming the first flow path group G1 and the second flow path group G2 by laminated molding using a metal material. For the formed object obtained through the molding step based on laminated molding, grinding or the like can be performed as needed. The manufacturing method of the heat exchange core 10 of several embodiments will be described in detail later.

[0087] It should be noted that the heat exchange core 10 of several embodiments is not limited to laminated molding, and can also be integrally formed by cutting or the like.

[0088] The heat exchange core 10 of several embodiments can also be constituted by combining a plurality of first partition walls W1 formed by bending a metal plate, but it is preferably integrally formed. If the heat exchange core 10 is integrally formed, a gasket for preventing fluid leakage between components is not required in the heat exchange core 10.

[0089] In the case of using a gasket, in order to reliably seal between components, an appropriate elastic deformation amount needs to be given to the gasket. Then, in order to prevent fluid leakage, adjustment such as disassembling the components of the heat exchange core and re-fastening the gasket between the components is required. Since changes in the deformation amount caused by tolerances of the gasket, assembly tolerances, pressure changes of the fluid, changes over time of the gasket, or damage to the gasket caused by thermal stress or the like may occur, the necessity of adjustment for the gasket is particularly high.

[0090] In contrast, according to the integrally formed heat exchange core 10 of several embodiments, since there is no gasket, the labor for adjustment can be significantly reduced.

[0091] (Housing and header)

[0092] As Figure 1 and Figure 2As shown, the housing 20 of several embodiments is integrally formed into a substantially cylindrical shape. The housing 20 is formed using, for example, stainless steel, aluminum alloy, etc. that have properties suitable for fluids.

[0093] The housing 20 of several embodiments includes: a housing main body 21 that has an inner diameter corresponding to the outer diameter of the heat exchange core 10 and has a circular cross-section; and a large-diameter portion 22 whose diameter is enlarged with respect to the housing main body 21. The large-diameter portions 22 are provided at both ends on the axial direction D1 of the housing main body 21. These large-diameter portions 22 function as a first inlet header 221 and a first outlet header 222.

[0094] These headers 221, 222 each have an annular internal space 221A, 222A as a communication space around the side wall W0 of the heat exchange core 10 ( Figure 2 ).

[0095] In several embodiments, an inlet port 22A for the first fluid to flow in from the outside is provided in the first inlet header 221. In several embodiments, an outlet port 22B for the first fluid to flow out to the outside is provided in the first outlet header 222.

[0096] In several embodiments, the inlet port 22A is not limited to one location and may be provided at multiple locations in the circumferential direction D2. For example, two inlet ports 22A may be symmetrically arranged with respect to the center point of the second cross-section C2. The same applies to the outlet port 22B.

[0097] In several embodiments, the flow path cross-sectional area in the direction intersecting the circumferential direction D2 is sufficiently ensured in the internal spaces 221A, 222A of the headers 221, 222, respectively. Therefore, the resistance of the first fluid in the internal spaces 221A, 222A is smaller than the resistance of the first fluid in the plurality of radial flow paths 61 described later. Therefore, the first fluid easily flows into the radial flow paths 61 equally from the first inlet header 221, and when the first fluid flows out to the first outlet header 222 through the radial flow paths 61, the deviation of the flow rate of each of the radial flow paths 61 is suppressed.

[0098] In several embodiments, a second inlet header 31 is provided at one end portion 10A of the housing 20 in the axial direction D1. A second outlet header 32 is provided at the other end portion 10B of the housing 20 in the axial direction D1.

[0099] In several embodiments, the flange 31A of the second inlet header 31 and the flange 231 of the housing 20 are sealed by an annular sealing member (not shown). The same applies to the flange 32A of the second outlet header 32 and the flange 232 of the housing 20.

[0100] In several embodiments, the first flow path group G1 is connected to the inside of the first inlet header 221 and the inside of the first outlet header 222.

[0101] In several embodiments, the second flow path group G2 is connected to the inside of the second inlet header 31 and the inside of the second outlet header 32. The starting ends of the respective second flow paths 102 open inside the second inlet header 31. The terminal ends of the respective second flow paths 102 open inside the second outlet header 32.

[0102] The directions in which the first fluid and the second fluid flow into and out of the heat exchange core 10, respectively, can be appropriately determined based on considerations such as the processing of the inflow and outflow paths, the interference of the respective headers of the first fluid and the second fluid, and the like.

[0103] For example, contrary to the above description, the first fluid may be made to flow through the second flow path group G2, and the second fluid may be made to flow through the first flow path group G2.

[0104] (Definition of substantially circular shape, substantially circular ring shape, substantially concentric circular shape)

[0105] In several embodiments, the cross-section of the outer shell 20 does not necessarily need to be strictly circular, and may be a "substantially circular shape" that is regarded as approximately circular. It should be noted that the "circular shape" allows for tolerances with respect to a perfect circle.

[0106] The "substantially circular shape" includes, for example, a polygonal shape with many vertices (e.g., a 10 - 20-sided polygon), an n-fold rotationally symmetric shape where, for example, n is 10 - 20, and the like. In addition, a shape in which the arc is continuous over substantially the entire circumferential direction D2 and there are irregularities in a part of the circumference is also included in the "substantially circular shape".

[0107] Similarly to the above, the cross-sections C1 - C3 of the heat exchange core 10 in several embodiments do not need to be strictly circular, and may also be "substantially circular". In this case, in the first cross-section C1, the first flow path 101 and the second flow path 102 only need to be formed into a "substantially circular ring shape" that can be regarded as approximately circular, and similarly, the first flow path group G1 and the second flow path group G2 only need to be arranged in a substantially concentric circular shape that can be regarded as approximately concentric. The "substantially circular ring shape" is based on the meaning of the above-mentioned substantially circular shape.

[0108] In addition, in order to increase the heat transfer area, as Figure 7As shown, a plurality of protrusions 103 that stand up from the first partition wall W1 toward at least one of the first flow path 101 and the second flow path 102 may be provided on the first partition wall W1. It should be noted that, from the viewpoint of suppressing pressure loss and allowing the first fluid to smoothly flow into the first flow path 101 from the radial flow path 61 described later, and also allowing the first fluid to smoothly flow out from the first flow path 101 to the radial flow path 61, the protrusions 103 are preferably provided on the first partition wall W1 while avoiding both end portions of the first flow path 101 in the axial direction D1.

[0109] The heat exchange core 10 having the protrusions 103 can be integrally formed by a laminated molding process.

[0110] Regarding the "concentric circular shape" in which a plurality of circles with different diameters are concentrically arranged, a tolerance is allowed for the coincidence (concentricity) of the centers of the respective circles. That is, the "substantially concentric circular shape" includes a form in which the circular shapes are substantially concentrically arranged. Regarding the elements of each circle constituting the concentric circles, the above-mentioned substantially circular shape is the standard. It is possible to align the centers of a plurality of polygonal shapes, or to align the center of a polygonal shape with the center of a rotationally symmetric shape, and arrange them in a "substantially concentric circular shape".

[0111] In the case where the cross sections of the housing 20 and the heat exchange core 10 are circular, the cross sections of the first flow path 101 and the second flow path 102 are annular, and the first flow path group G1 and the second flow path group G2 are arranged in a concentric circular shape, it is most preferable from the viewpoints of stress, heat transfer area, and uniformization of the flow state.

[0112] However, in the case where the cross sections of the housing 20 and the heat exchange core 10 are substantially circular, or in the first cross section C1, the first flow path 101 and the second flow path 102 are substantially annular, or the first flow path group G1 and the second flow path group G2 are arranged as a whole in a substantially concentric circular shape, effects equivalent to those described later of the present embodiment can also be obtained.

[0113] (Description of the second cross section)

[0114] Hereinafter, the second cross section C2 of several embodiments and the outlines of the radial flow path 61 and the circumferential flow path 66 represented by the second cross section C2 will be described. It should be noted that the details of the radial flow path 61 of several embodiments will be described separately.

[0115] As shown in correspondence with Figure 2 the IV-IV line cross section of Figure 4 shown, a radial flow path 61 that intersects the first flow path group G1 and the second flow path group G2 and is only connected to the first flow path group G1 is formed in the heat exchange core 10. The radial flow path 61 extends in the radial direction of the heat exchange core 10 in the Figure 4 shown second cross section C2, as Figure 2is shown to communicate with the internal space 221A of the first inlet header 221. As Figure 1 and Figure 2 shown, the radial flow path 61 penetrates the side wall W0 in the thickness direction.

[0116] In several embodiments, a plurality of first flow paths 101 extend axially in the heat exchange core 10 and communicate with the radial flow paths 61 on one axial side and the other axial side. In several embodiments, the first flow paths 101 among the plurality of first flow paths 101 included in the axial flow path 3 and disposed in the core main body portion 13 are included. Further, in several embodiments, as described later, the first flow paths 101 among the plurality of first flow paths 101 disposed in the header portions 11A and 11B are also referred to as circumferential flow paths 66. In several embodiments, the circumferential flow paths 66 are alternately arranged in layers with the second flow paths 102 in the radial direction.

[0117] Although the IVx-IVx line cross-sectional view of Figure 2 is omitted, it is the same as Figure 4 . The cross-section corresponding to the IVx-IVx line of Figure 2 also corresponds to the second cross-section C2. The cross-section corresponding to the IVx-IVx line is referred to as the second cross-section C2x. The radial flow path 61 located in the second cross-section C2x communicates with the internal space 222A of the first outlet header 222.

[0118] In several embodiments, at least one radial flow path 61 is provided in each of the second cross-section C2 and the second cross-section C2x. It should be noted that in each of the second cross-section C2 and the second cross-section C2x, it is preferable that a plurality of (for example, 8 in the embodiment shown in Figure 4 ) radial flow paths 61 are distributed in the circumferential direction D2. By distributing the plurality of radial flow paths 61 in the circumferential direction D2, it is possible to equalize the rigidity and strength of the heat exchange core 10 in the circumferential direction D2, and it is also possible to contribute to the equalization of the flow state of the first fluid in the circumferential direction D2.

[0119] The larger the number of the radial flow paths 61, the easier it is to equalize the flow rate of the first fluid flowing in each radial flow path 61. Then, heat is sufficiently exchanged between the first fluid flowing evenly in the entire circumferential direction D2 and the second fluid. Considering this point, it is preferable that 4 or more radial flow paths 61 are distributed in each of the second cross-sections C2 and C2x. However, even if the number of the radial flow paths 61 in each of the second cross-sections C2 and C2x is 3 or less (including 1), it is allowed.

[0120] In several embodiments, in order to facilitate the homogenization of the flow rate of the first fluid flowing in each radial flow path 61, it is preferable that the plurality of radial flow paths 61 are equally spaced in the circumferential direction D2. That is, it is preferable that the heat exchange core 10 is also formed symmetrically with respect to the center of the cross section in the second cross sections C2, C2x.

[0121] The shape of the opening in the side wall W0 of each radial flow path 61 is Figure 1 and Figure 2 In the example shown, it is a rectangular shape. On the side wall W0, the openings of the radial flow paths 61 are distributed in the circumferential direction D2.

[0122] In addition, similar to the above, in order to facilitate the homogenization of the flow rate of the first fluid flowing in each radial flow path 61, it is preferable that the inlet port 22A and the respective phases of the radial flow paths 61 are offset from each other. That is, it is preferable that the inlet port 22A and the radial flow paths 61 are arranged at different positions in the circumferential direction D2. If the phase of the inlet port 22A is offset from the phase of the radial flow path 61, it is possible to more reliably prevent a deviation in the flow rate of the first fluid flowing separately in the radial flow paths 61 compared to the case where there is no offset (being located at the same position in the circumferential direction D2).

[0123] In several embodiments, each radial flow path 61 includes a set of tubular transverse walls W3 located in the region of the second flow path 102. The radial flow paths 61 are separated from the second flow path group G2 by the transverse walls W3. The transverse walls W3 are integrally provided between the first partition walls W1, W1 adjacent in the radial direction of the heat exchange core 10. Each first flow path 101 communicates with the inside of the transverse wall W3.

[0124] All the first flow paths 101 from the first flow path 101 located on the outer peripheral side of the heat exchange core 10 to the unillustrated first flow path near the axis of the heat exchange core 10 communicate with the internal spaces 221A, 222A of the first inlet header 221 and the first outlet header 222 respectively through the plurality of radial flow paths 61 extending radially from near the axis of the heat exchange core 10, and also communicate with the outside of the heat exchange core 10.

[0125] (Description of the third cross section)

[0126] With Figure 2 and Figure 6 The V-V line cross section corresponding to Figure 5 represents the third cross section C3 located at a position outside the second cross section C2 in the axial direction D1.

[0127] In several embodiments, as Figure 6As shown, a closing wall W4 is provided in a first flow path group G1 communicating with the above-described radial flow path 61 at a position on the axial direction D1 outside the second cross-section C2. The first fluid flowing in the first flow path group G1 flows on the axial direction D1 without exceeding the closing wall W4 intersecting the axial direction D1. The closing wall W4 blocks between adjacent first partition walls W1, W1.

[0128] In several embodiments, under the action of the closing wall W4, the first flow path group G1 is closed in the third cross-section C3 ( Figure 5 ). Therefore, only the second flow path group G2 exists in the third cross-section C3. Since there is a closing wall W4 in the region shown in a lattice pattern in Figure 5 , the first flow path group G1 does not exist.

[0129] The second flow path group G2 opens to the second inlet header 31 and the second outlet header 32 at the end portions of the heat exchange core 10, respectively.

[0130] Although the Vx-Vx line cross-sectional view of Figure 2 is omitted, it is the same as Figure 5 . In several embodiments, the cross-section corresponding to the Vx-Vx line of Figure 2 is equivalent to the third cross-section C3x at a position on the axial direction D1 outside the second cross-section C2x. The cross-section corresponding to the Vx-Vx line is referred to as the third cross-section C3x.

[0131] In several embodiments, as Figure 6 shown, under the action of the closing wall W4, the first flow path group G1 is closed in the third cross-section C3x. Therefore, only the second flow path group G2 exists in the third cross-section C3x.

[0132] (Flow of the first fluid and the second fluid)

[0133] Referring to Figure 2 , Figure 4 and Figure 6 , the flow of each of the first fluid and the second fluid in the heat exchange core 10 will be described. Figure 6 shows a part of the longitudinal section of the heat exchange core 10.

[0134] In several embodiments, as Figure 6As shown by the arrow of the dashed line in the figure, the second fluid flowing into the interior of the second inlet header 31 through an inlet port (not shown) flows into the start ends of the respective second flow paths 102 of the second flow path group G2. At this time, since the second flow path group G2 is formed symmetrically with respect to the center of the third cross section C3, that is, the axis AX, the second fluid flows into each of the second flow paths 102 uniformly in the entire circumferential direction D2 and flows in the axial direction D1 in the second flow paths 102. The second fluid flows out from the terminal ends of the second flow paths 102 into the interior of the second outlet header 32, and then flows out of the heat exchanger 1 through an outlet port (not shown).

[0135] In several embodiments, as Figure 6 shown by the arrow of the solid line in the figure, the first fluid flowing into the interior of the first inlet header 221 from the inlet port 22A flows equally from the first inlet header 221 into the first flow path group G1 within the range of the circumferential direction D2 through the radial flow paths 61 opening in the side wall W0.

[0136] At this time, the first fluid does not bias towards a part of the radial flow paths 61 close to the inlet port 22A, but is distributed from the first inlet header 221 to the plurality of radial flow paths 61 respectively. In each radial flow path 61, the first fluid faces the inner side in the radial direction of the heat exchange core 10 and is distributed to each first flow path 101 through the inside of the transverse wall W3 shown by the double-dashed line in the figure. Figure 6 shown by the double-dashed line in the figure, to each first flow path 101.

[0137] After that, based on the symmetry of the heat exchange core 10 on the second cross section C2 where the radial flow paths 61 are located, the flow rate of the first fluid flowing in the axial direction D1 in the first flow paths 101 is evenly maintained in the entire circumferential direction D2. Therefore, it is possible to easily ensure a condition of a countercurrent with a large temperature difference between the second fluid flowing in the second flow paths 102 and the first fluid flowing in the first flow paths 101, and sufficient heat transfer can be achieved within the entire continuous range of the second cross section C2.

[0138] When the first fluid flowing in the axial direction D1 in each first flow path 101 reaches the terminal portion of the first flow path 101, the direction of flow changes from the axial direction D1 to the radial direction. In the respective radial flow paths 61 radially arranged from the axis of the heat exchange core 10, it merges through the inside of the transverse wall W3 and flows in the radial flow paths 61 towards the outer side in the radial direction of the heat exchange core 10. And the first fluid flowing out from the radial flow paths 61 into the interior of the first outlet header 222 flows out of the heat exchanger 1 from the outlet port 22B.

[0139] (Main effects of the heat exchanger of the embodiment)

[0140] The heat exchanger 1 according to the several embodiments described above not only has a shape of the outer shell 20 that is symmetrical with respect to the axis, but also has a structure of the heat exchange core 10 that is symmetrically and concentrically laminated based on the first flow path group G1 and the second flow path group G2. This enables the stress acting due to the pressure of the fluid, etc. to be evenly dispersed throughout the heat exchange core 10, and while ensuring a large heat transfer area between the first fluid and the second fluid, efficient heat exchange can be carried out throughout the heat exchange core 10 where the first fluid and the second fluid flow evenly.

[0141] As described above, it is possible to prevent the heat exchange core 10 from being damaged and improve reliability, and the same heat exchange capacity can be obtained with a smaller heat exchange core 10.

[0142] (Details of the radial flow paths in several embodiments)

[0143] Hereinafter, the details of the radial flow paths in several embodiments will be described.

[0144] It should be noted that in the heat exchange core 10 of several embodiments, since the first header portion 11A and the second header portion 11B have the same structure, in the following description, when there is no need to particularly distinguish between the first header portion 11A and the second header portion 11B, the reference numerals A and B will not be marked, and only the header portion 11 will be described.

[0145] It should be noted that the description of the modified examples of the radial flow path 61 and the circumferential flow path 66 will be described separately later.

[0146] Regarding the modified examples of the radial flow path 61 and the circumferential flow path 66 described later, unless otherwise specified, they are the same as the content described above.

[0147] Moreover, regarding the content of several embodiments described below, within the scope that does not conflict with the modified examples of the radial flow path 61 and the circumferential flow path 66 described later, it can also be applied to the modified examples of the radial flow path 61 and the circumferential flow path 66 described later.

[0148] (Regarding the flow path area of the radial flow path)

[0149] In the heat exchange core 10 of several embodiments, the header flow path 6 includes at least one radial flow path 61 extending in the radial direction. The header flow path 6 includes a plurality of circumferential flow paths 66 branched from each radial flow path 61 and respectively communicating with one or more axial flow paths 3.

[0150] In each radial flow path 61, the flow path area Ca2 at the second position P2 closer to the radial inner side than the first position is smaller than the flow path area Ca1 at the first position P1.

[0151] Here, the flow path area Ca of the radial flow path 61 refers to the cross-sectional area of the radial flow path 61 exhibited when the radial flow path 61 is cut along a plane orthogonal to its extending direction (i.e., the radial direction).

[0152] In addition, the first position P1 and the second position P2 are positions assumed for representing the relative positional relationship in the radial direction in the radial flow path 61, and do not refer to specific radial positions. For example, in the radial flow path 61, when a certain radial position Pa is set as the first position P1, any position radially inward of this radial position Pa can be the second position.

[0153] In the heat exchange core 10 of several embodiments, it is also possible that the circumferential dimension Lc2 of the radial flow path 61 at the second position P2 is smaller than the circumferential dimension Lc1 of the radial flow path 61 at the first position P1 (refer to Figure 4 ), so that the flow path area Ca2 at the second position P2 is smaller than the flow path area Ca1 at the first position P1. In addition, it is also possible that the axial dimension La2 of the radial flow path 61 at the second position P2 is smaller than the axial dimension La1 of the radial flow path 61 at the first position P1 (refer to Figure 6 ), so that the flow path area Ca2 at the second position P2 is smaller than the flow path area Ca1 at the first position P1.

[0154] That is, it is also possible that the flow path area Ca2 at the second position P2 is smaller than the flow path area Ca1 at the first position P1 by making at least any one of the circumferential dimension Lc1 and the axial dimension La1 of the radial flow path 61 at the first position P1 different from the circumferential dimension Lc2 and the axial dimension La2 of the radial flow path 61 at the second position P2.

[0155] In the radial flow path 61, in the region that is more radially outward, the flow rate of the fluid tends to increase and the pressure loss becomes larger. Therefore, reducing the pressure loss in this region helps to reduce the pressure loss of the entire heat exchange core 10.

[0156] According to the above structure, the flow path area Ca2 at the second position P2 is smaller than the flow path area Ca1 at the first position P1. That is, according to the above structure, the flow path area Ca1 at the first position P1 is larger than the flow path area Ca2 at the second position P2. Thereby, the pressure loss in the radially outer region in the radial flow path 61 can be suppressed, and thus the pressure loss of the entire heat exchange core 10 can be suppressed. Therefore, in the axial flow path 3 connected to the radial flow path 61 via the circumferential flow path 66, the flow rate difference caused by the radial position can be suppressed, and the heat exchange efficiency of the heat exchange core 10 can be improved.

[0157] It should be noted that, as described above, each radial flow path 61 can also make the circumferential dimension Lc2 at the second position P2 smaller than the circumferential dimension Lc1 at the first position P1.

[0158] Thereby, the flow path area Ca1 at the first position P1 can be made larger than the flow path area Ca2 at the second position P2.

[0159] In order to make the flow path area Ca1 at the first position P1 larger than the flow path area Ca2 at the second position P2, as described above, there are a method of making the circumferential dimension Lc1 at the first position P1 larger than the circumferential dimension Lc2 at the second position P2 and a method of making the axial dimension La1 at the first position P1 larger than the axial dimension La2 at the second position P2.

[0160] In this case, if the flow path area Ca is changed by mainly changing the circumferential dimension Lc at the first position P1 and the second position P2, the axial dimension La of each radial flow path 61 can be suppressed as a whole along the radial direction. Thereby, the axial dimension of the header portion 11 can be suppressed.

[0161] It should be noted that, as described above, each radial flow path 61 can also make the axial dimension La2 at the second position P2 smaller than the axial dimension La1 at the first position P1.

[0162] Thereby, the flow path area Ca1 at the first position P1 can be made larger than the flow path area Ca2 at the second position P2.

[0163] In addition, if the flow path area Ca is changed by mainly changing the axial dimension La at the first position P1 and the second position P2, the circumferential dimension Lc of each radial flow path 61 can be suppressed as a whole along the radial direction. Thereby, in the cross section (second cross section C2) of the header portion 11 when viewed from the axial direction D1, the proportion of the area occupied by the radial flow path 61 can be suppressed and the proportion of the area occupied by the circumferential flow path 66 can be increased.

[0164] In the header portion 11 of several embodiments, it is preferable that the above-mentioned flow path area Ca is configured to gradually decrease toward the radial inside.

[0165] Thereby, the radial flow path 61 is formed in such a way that the above-mentioned flow path area Ca gradually increases toward the radial outside. Therefore, a sudden change portion of the flow path area Ca can be avoided, and the pressure loss in the radial flow path 61 can be suppressed.

[0166] (Regarding the opening formed by the radial flow path)

[0167] As Figure 1As shown, in the heat exchange core 10 of several embodiments, at least one opening 63 formed by at least one radial flow path 61 is formed on the outer peripheral surface of the heat exchange core 10 at the header portion 11. In the heat exchange core 10 of several embodiments, it is preferable that the total area ∑Oa of the opening areas Oa of the respective openings 63 is equal to or less than the total area ∑Sc of the areas Sc of the plurality of circumferential flow paths 66 when viewed from the axial direction D1.

[0168] In the heat exchange core 10 of several embodiments, when the radial flow path 61 is formed such that the total area ∑Oa of the opening areas Oa of the respective openings 63 exceeds the total area ∑Sc of the areas Sc of the plurality of circumferential flow paths 66 when viewed from the axial direction D1, the pressure loss of the fluid flowing through the radial flow path 61 and the circumferential flow path 66 is greatly affected by the pressure loss in the circumferential flow path 66. Therefore, even if the total area ∑Oa of the opening areas Oa of the respective openings 63 is increased in such a way as to exceed the total area ∑Sc of the areas Sc of the plurality of circumferential flow paths 66 when viewed from the axial direction D1, compared with the case where the total area ∑Sc of the areas Sc of the plurality of circumferential flow paths 66 when viewed from the axial direction D1 is the same as the total area ∑Oa of the opening areas Oa of the respective openings 63, the effect of suppressing the pressure loss in the radially outer region of the radial flow path 61 does not increase much.

[0169] On the contrary, by increasing the total area ∑Oa of the opening areas Oa of the respective openings 63 in such a way as to exceed the total area ∑Sc of the areas Sc of the plurality of circumferential flow paths 66 when viewed from the axial direction D1, the circumferential dimension Lc and the axial dimension La of the radial flow path 61 become larger. The following effects may occur.

[0170] That is, as the circumferential dimension Lc of the radial flow path 61 becomes larger, the proportion of the region occupied by the radial flow path 61 in the cross-section (second cross-section C2) of the header portion 11 when viewed from the axial direction D1 may increase, and the proportion of the region occupied by the circumferential flow path 66 may decrease.

[0171] In addition, since the axial dimension La of the radial flow path 61 becomes larger, the axial dimension of the header portion 11 may be increased.

[0172] According to the heat exchange core 10 of several embodiments, the influence on the region occupied by the circumferential flow path 66 in the cross-section (second cross-section C2) of the header portion 11 when viewed from the axial direction D1 and the influence on the axial dimension of the header portion 11 are suppressed, and the pressure loss in the radially outer region of the radial flow path 61 can be effectively suppressed.

[0173] (Regarding the shape of the opening)

[0174] Figure 8FIG. is a view schematically showing a part near the header portion 11 in a side surface of the heat exchange core 10 according to several embodiments, and shows an example of the shape of the opening portion 63.

[0175] Figure 9 FIG. is a view schematically showing a part near the header portion 11 in a side surface of the heat exchange core 10 according to several embodiments, and shows another example of the shape of the opening portion 63.

[0176] In the heat exchange core 10 according to several embodiments, the flow rate of the fluid is relatively large and the pressure loss is relatively large near the opening portion 63 of the radial flow path 61. Therefore, it is desirable to increase the opening area on the opening portion 63 side as much as possible. However, if the radial flow path 61 is expanded in the circumferential direction D2, it may affect the flow of the fluid in the axial flow path 3. Therefore, it is desirable to suppress the expansion of the flow path width in the circumferential direction D2. Therefore, in the radial flow path 61, it is preferable to expand the flow path width in the axial direction D1.

[0177] Therefore, in the heat exchange core 10 according to several embodiments, the shape of the opening portion 63 is set as follows.

[0178] That is, in the heat exchange core 10 according to several embodiments, as shown in Figure 8 and Figure 9 , the opening dimension AL1 along the axial direction D1 of each opening portion 63 is 1 times or more (1.0×AL2≤AL1) of the opening dimension AL2 along the circumferential direction D2 of each opening portion 63.

[0179] Thereby, the opening dimension AL2 along the circumferential direction D2 of each opening portion 63 can be suppressed. Therefore, the dimension of the radial flow path 61 along the circumferential direction D2 can be suppressed, and thus the proportion of the region occupied by the radial flow path 61 in the cross section (second cross section C2) of the header portion 11 when viewed from the axial direction D1 can be suppressed and the proportion of the region occupied by the circumferential flow path 66 can be increased.

[0180] For example, in the heat exchange core 10 shown in Figure 8 , the opening portion 63 has a rectangular shape when viewed from the radially outer side. Further, for example, in the heat exchange core 10 shown in Figure 9 , the end portion 64 along the axial direction of the opening portion 63 is formed such that the dimension in the circumferential direction D2 becomes smaller as it goes toward the outside of the radial flow path 61 along the axial direction D1 when viewed from the radially outer side. That is, in the heat exchange core 10 according to several embodiments, the radial flow path 61 may also be formed such that the dimension AL2 in the circumferential direction D2 becomes smaller at at least one of the two end portions 64 along the axial direction D1 as it goes toward the outside of the radial flow path 61 along the axial direction D1.

[0181] Accordingly, for example, as described later, in the case of forming the heat exchange core 10 by additive manufacturing, when the axial direction D1 is set as the stacking direction, the end portion 64 along the axial direction D1 in the radial flow path 61 is less likely to become an overhanging region. As a result, the process of forming the support member for forming the overhanging region and the process of removing the support member after forming can be simplified or eliminated.

[0182] (Regarding the change in the flow path area of the radial flow path with respect to the radial position)

[0183] Figure 10 FIG. is a schematic diagram for explaining the change in the flow path area Ca of the radial flow path 61 with respect to the radial position, and is a view of the heat exchange core 10 observed along the axial direction D1.

[0184] For ease of explanation, in Figure 10 the schematic shape of the first radial flow path 61A, which is the radial flow path 61 in the first header portion 11A, and the schematic shape of the second radial flow path 61B, which is the radial flow path 61 in the second header portion 11B, are overlapped and shown along the axial direction D1. It should be noted that for ease of illustration, in Figure 10 the schematic shape of the first radial flow path 61A is represented by a dashed line, and the schematic shape of the second radial flow path 61B is represented by a double-dashed line.

[0185] Figure 11 FIG. is a schematic diagram for explaining the change in the flow path area Ca of the radial flow path 61 with respect to the radial position, and is a view of the heat exchange core 10 observed along the radial direction. It should be noted that in Figure 11 the schematic shapes of the first radial flow path 61A and the second radial flow path 61B are represented by double-dashed lines.

[0186] In the heat exchange core 10 of several embodiments, as described above, near the opening 63 of the radial flow path 61, the flow rate of the fluid is relatively large, so the dynamic pressure is relatively large. On the other hand, near the center of the cylinder of the radial flow path 61, the flow rate becomes smaller compared to the vicinity of the opening 63, so the dynamic pressure becomes very small compared to the vicinity of the opening 63.

[0187] If the difference in dynamic pressure caused by the different radial positions increases beyond a certain level, the deviation between the axial flow path 3 near the opening 63 (i.e., the radial outer side) and the axial flow path 3 near the center becomes larger, which may lead to a reduction in the performance of the heat exchange core 10.

[0188] It should be noted that there is a tendency that the greater the dynamic pressure, the greater the above-mentioned deviation. Therefore, in a fluid with a high density, the above-mentioned deviation is likely to become larger.

[0189] Therefore, preferably, for a fluid with a higher density, the area increase rate Rca described below is increased, thereby further reducing the flow velocity near the opening 63.

[0190] In addition, generally, the density of a fluid varies with temperature. In addition, generally, the change in density of a gas due to temperature is greater than the change in density of a liquid due to temperature.

[0191] Therefore, when the temperature of the fluid changes due to flowing through the heat exchange core 10, it is sometimes preferable to make the area increase rate Rca described below different between the radial flow path 61 in the header portion 11 on the upstream side of the fluid flow and the radial flow path 61 in the header portion 11 on the downstream side of the fluid flow.

[0192] Therefore, in the heat exchange core 10 of several embodiments, the shape of the radial flow path 61 is set as follows.

[0193] That is, in the heat exchange core 10 of several embodiments, regarding the area increase rate Rca of the flow path area Ca that increases as it goes from the inner side to the outer side in at least one radial flow path 61, it is different between at least one radial flow path 61 (first radial flow path 61A) in the first header portion 11A and at least one radial flow path 61 (second radial flow path 61B) in the second header portion 11B.

[0194] Here, the area increase rate Rca is a value obtained by dividing the difference (Ca1 - Ca2) between the flow path area Ca1 at the first position P1 and the flow path area Ca2 at the second position P2 by the difference in the radial positions between the first position P1 and the second position P2.

[0195] It should be noted that, in order to make the area increase rate Rca different between the first radial flow path 61A and the second radial flow path 61B, for example, as Figure 10 shown, it is also possible to make the dimension increase rate Rlc regarding the circumferential dimension Lc that becomes larger as it goes from the inner side to the outer side different between the first radial flow path 61A and the second radial flow path 61B. In addition, in order to make the area increase rate Rca different between the first radial flow path 61A and the second radial flow path 61B, for example, as Figure 11 shown, it is also possible to make the dimension increase rate Rla regarding the axial dimension La that becomes larger as it goes from the inner side to the outer side different between the first radial flow path 61A and the second radial flow path 61B.

[0196] That is, it is also possible to make the area increase rate Rca different between the first radial flow path 61A and the second radial flow path 61B by making at least one of the dimension increase rate Rlc regarding the circumferential dimension Lc and the dimension increase rate Rla regarding the axial dimension La different between the first radial flow path 61A and the second radial flow path 61B.

[0197] In the heat exchange core 10 of several embodiments, it is desirable that the static pressure difference between the first header portion 11A and the second header portion 11B at any radial position of the radial flow path 61 is constant regardless of the radial position.

[0198] When the fluid flowing through the heat exchange core 10 is a gas, for example, as described above, compared with the case of a liquid, the proportion of the change in density caused by the change in temperature tends to be larger. Therefore, if the above area increase rate Rca is the same in the first radial flow path 61A and the second radial flow path 61B, the above static pressure difference may vary greatly depending on the radial position.

[0199] According to the above structure, since the above area increase rate Rca is different in the first radial flow path 61A and the second radial flow path 61B, it is possible to suppress the difference in the above static pressure difference depending on the radial position.

[0200] (Regarding the manufacturing method of the heat exchange core)

[0201] Hereinafter, an example of the manufacturing method of the heat exchange core 10 of the above several embodiments will be described.

[0202] Figure 12 It is a flowchart showing the processing steps in the manufacturing method of the heat exchange core 10 of the above several embodiments.

[0203] The manufacturing method of the heat exchange core 10 of the above several embodiments includes: a core main body forming step S1 of forming a core main body 13 including a plurality of axial flow paths 3 extending along the axial direction D1 by laminated molding; and a header portion forming step S3 of forming a header portion 11 adjacent to at least one end of the core main body 13 in the axial direction D1 and having a header flow path 6 communicating with the plurality of axial flow paths 3 by laminated molding.

[0204] The header portion forming step S3 forms the header flow path 6 in such a manner as to include at least one radial flow path 61 extending in the radial direction and a plurality of circumferential flow paths 66 branched from any one of the radial flow paths 61 and respectively communicating with one or more axial flow paths 3.

[0205] In addition, the header portion forming step S3 may form each radial flow path 61 in such a manner that the flow path area Ca2 at the second position P2 radially inside the first position P1 is smaller than the flow path area Cal at the first position P1.

[0206] In addition, the header portion forming step S3 can also form the header portion 11 in such a manner that at least one opening 63 formed by at least one radial flow path 61 is formed on the outer peripheral surface of the heat exchange core 10 at the header portion 11, and the header portion 11 is formed in such a manner that the opening dimension AL1 along the axial direction D1 in each opening 63 is more than 1 time the opening dimension AL2 along the circumferential direction in each opening 63.

[0207] Accordingly, by additive manufacturing, the heat exchange core 10 can be integrally formed, so that component assembly and sealing between components using gaskets are not required. Therefore, the adjustment effort can be significantly reduced.

[0208] The present disclosure is not limited to the above-described embodiments, and also includes modified forms of the above-described embodiments and forms obtained by appropriately combining these forms.

[0209] The content described in each of the above embodiments can be understood as follows, for example.

[0210] (1) The heat exchange core 10 of at least one embodiment of the present disclosure includes a core main body portion 13 and a header portion 11. The core main body portion 13 includes a plurality of axial flow paths 3 extending along the axial direction D1. The header portion 11 is adjacent to at least one end of the core main body portion 13 in the axial direction D1 and has a header flow path 6 communicating with the plurality of axial flow paths 3.

[0211] The header flow path 6 includes at least one radial flow path 61 extending along the radial direction. The header flow path 6 includes a plurality of circumferential flow paths 66 branched from the respective radial flow paths 61 and respectively communicating with one or more axial flow paths 3.

[0212] In each of the radial flow paths 61, the flow path area Ca2 at a second position P2 radially inner than the first position P1 is smaller than the flow path area Ca1 at the first position P1.

[0213] In the above-described radial flow path 61, in a region that is more radially outer, the flow rate of the fluid tends to increase and the pressure loss becomes larger. Therefore, reducing the pressure loss in this region helps to reduce the pressure loss of the entire heat exchange core 10.

[0214] According to the structure in (1) above, compared with the flow path area Ca1 at the first position P1, the flow path area Ca2 at the second position P2 radially inward of the first position P1 is smaller. That is, according to the structure in (1) above, the flow path area Ca1 at the first position P1 radially outward of the second position P2 is larger than the flow path area Ca2 at the second position P2. Thus, the pressure loss in the radially outer region of the radial flow path 61 can be suppressed, and accordingly, the pressure loss of the entire heat exchange core 10 can be suppressed. Therefore, in the axial flow path 3 connected to the radial flow path 61 via the circumferential flow path 66, the flow rate difference caused by the radial position can be suppressed, and the heat exchange efficiency in the heat exchange core 10 can be improved.

[0215] (2) In several embodiments, based on the structure in (1) above, in each radial flow path 61, the circumferential dimension Lc2 at the second position P2 is smaller than the circumferential dimension Lc1 at the first position P1.

[0216] According to the structure in (2) above, by making the circumferential dimension Lc2 at the second position P2 smaller than the circumferential dimension Lc1 at the first position P1 in each radial flow path 61, that is, by making the circumferential dimension Lc1 at the first position P1 larger than the circumferential dimension Lc2 at the second position P2, the flow path area Ca1 at the first position P1 can be made larger than the flow path area Ca2 at the second position P2.

[0217] If the flow path area Ca is changed by mainly changing the circumferential dimension Lc at the first position P1 and the second position P2, the dimension La of the axial direction D1 of each radial flow path 61 can be suppressed as a whole along the radial direction. Thereby, the axial dimension of the header portion 11 can be suppressed.

[0218] (3) In several embodiments, based on the structure in (1) or (2) above, in each radial flow path 61, the axial dimension La2 at the second position P2 is smaller than the axial dimension La1 at the first position P1.

[0219] According to the structure in (3) above, by making the axial dimension La2 at the second position P2 smaller than the axial dimension La1 at the first position P1 in each radial flow path 61, that is, by making the axial dimension La1 at the first position P1 larger than the axial dimension La2 at the second position P2, the flow path area Ca1 at the first position P1 can be made larger than the flow path area Ca2 at the second position P2.

[0220] If the flow path area Ca is changed by mainly changing the axial dimension La at the first position P1 and the second position P2, the circumferential dimension Lc of each radial flow path 61 can be suppressed overall in the radial direction. As a result, in the cross-section of the header portion 11 (second cross-section C2) when viewed from the axial direction D1, the proportion of the area occupied by the radial flow path 61 can be suppressed and the proportion of the area occupied by the circumferential flow path 66 can be increased.

[0221] (4) In several embodiments, based on any of the structures in the above (1) to (3), the flow path area Ca gradually decreases toward the radial inner side.

[0222] According to the structure of the above (4), the radial flow path 61 is formed such that the flow path area Ca gradually increases toward the radial outer side. Therefore, a sudden change portion of the flow path area Ca can be avoided, and the pressure loss in the radial flow path 61 can be suppressed.

[0223] (5) In several embodiments, based on any of the structures in the above (1) to (4), at least one opening 63 formed by at least one radial flow path 61 is formed on the outer peripheral surface of the heat exchange core 10 at the header portion 11. The total area ∑Oa of the opening areas Oa of each opening 63 is equal to or less than the total area ∑Sc of the areas Sc of the plurality of circumferential flow paths 66 when viewed from the axial direction D1.

[0224] According to the structure of the above (5), the influence on the area occupied by the circumferential flow path 66 in the cross-section of the header portion 11 (second cross-section C2) when viewed from the axial direction D1 and the influence on the axial dimension of the header portion 11 are suppressed, and the pressure loss in the radially outer region of the radial flow path 61 can be effectively suppressed.

[0225] (6) In several embodiments, based on any of the structures in the above (1) to (5), at least one opening 63 formed by at least one radial flow path 61 is formed on the outer peripheral surface of the heat exchange core 10 at the header portion 11. The opening dimension AL1 of each opening 63 along the axial direction D1 is 1 time or more the opening dimension AL2 of each opening 63 along the circumferential direction D2.

[0226] According to the structure of the above (6), the opening dimension AL2 of each opening 63 along the circumferential direction D2 can be suppressed. As a result, the dimension of the radial flow path 61 along the circumferential direction D2 can be suppressed, and therefore the proportion of the area occupied by the radial flow path 61 in the cross-section of the header portion 11 (second cross-section C2) when viewed from the axial direction D1 can be suppressed and the proportion of the area occupied by the circumferential flow path 66 can be increased.

[0227] (7) In several embodiments, based on any one of the structures in the above (1) to (6), at least one radial flow path 61 is formed such that at at least one of the two ends 64 along the axial direction D1, the dimension in the circumferential direction D2 becomes smaller as it moves toward the outside of the radial flow path 61 along the axial direction D1.

[0228] According to the structure of the above (7), for example, in the case of forming the heat exchange core 10 by additive manufacturing, when the axial direction D1 is set as the stacking direction, the end 64 along the axial direction D1 in the radial flow path 61 is less likely to become an overhanging area. Thus, the process of forming the support for the overhanging area and the process of removing the support after forming can be simplified or eliminated.

[0229] (8) In several embodiments, based on any one of the structures in the above (1) to (7), the header portion 11 includes a first header portion 11A adjacent to one end of the core main body portion 13 in the axial direction D1, and a second header portion 11B adjacent to the other end of the core main body portion 13 in the axial direction D1. Regarding the area increase rate Rca of the flow path area Ca that increases as it moves from the inner side to the outer side in at least one radial flow path 61, it is different between at least one radial flow path 61 in the first header portion 11A and at least one radial flow path 61 in the second header portion 11B.

[0230] According to the structure of the above (8), since the area increase rate Rca is different between the radial flow path 61 in the first header portion 11A and the radial flow path 61 in the second header portion 11B, it is possible to suppress the difference in static pressure from varying depending on the radial position.

[0231] (9) The heat exchange core 10 of at least one embodiment of the present disclosure includes a core main body portion 13 and a header portion 11. The core main body portion 13 includes a plurality of axial flow paths 3 extending along the axial direction D1. The header portion 11 is adjacent to at least one end of the core main body portion 13 in the axial direction D1 and has a header flow path 6 communicating with the plurality of axial flow paths 3.

[0232] The header flow path 6 includes at least one radial flow path 61 extending along the radial direction. The header flow path 6 includes a plurality of circumferential flow paths 66 branched from each radial flow path 61 and respectively communicating with one or more axial flow paths 3.

[0233] At least one opening 63 formed by at least one radial flow path 61 is formed on the outer peripheral surface of the heat exchange core 10 at the header portion 11.

[0234] The opening dimension AL1 along the axial direction D1 of each opening 63 is 1 times or more the opening dimension AL2 along the circumferential direction D2 of each opening 63.

[0235] According to the structure of (9) above, the opening dimension AL2 along the circumferential direction D2 of each opening portion 63 can be suppressed. Thereby, the dimension along the circumferential direction D2 of the radial flow path 61 can be suppressed, and thus the proportion of the region occupied by the radial flow path 61 in the cross section (second cross section C2) of the header portion 11 when viewed from the axial direction D1 can be suppressed, and the proportion of the region occupied by the circumferential flow path 66 can be increased.

[0236] (10) In several embodiments, based on the structure of (9) above, the total area ∑Oa of the opening areas Oa of each opening portion 63 is less than or equal to the total area ∑Sc of the areas Sc of the plurality of circumferential flow paths 66 when viewed from the axial direction D1.

[0237] According to the structure of (10) above, the influence on the region occupied by the circumferential flow path 66 in the cross section (second cross section C2) of the header portion 11 when viewed from the axial direction D1 and the influence on the axial dimension of the header portion 11 are suppressed, and the pressure loss in the radially outer region of the radial flow path 61 can be effectively suppressed.

[0238] (11) In several embodiments, based on the structure of (9) or (10) above, at least one radial flow path 61 is formed such that at at least one of the two end portions 64 along the axial direction D1, the dimension in the circumferential direction D2 becomes smaller as it goes toward the outside of the radial flow path 61 along the axial direction D1.

[0239] According to the structure of (11) above, for example, in the case of molding the heat exchange core 10 by additive manufacturing, when the axial direction D1 is set as the stacking direction, the end portion 64 along the axial direction D1 in the radial flow path 61 is less likely to become an overhanging region. Thereby, the process of molding the support member for molding the overhanging region and the process of removing the support member after molding can be simplified or eliminated.

[0240] (12) In several embodiments, based on any of the structures of (1) to (11) above, the plurality of axial flow paths 3 are arranged in a circular shape when viewed from the axial direction D1.

[0241] According to the structure of (12) above, the stress acting due to the pressure of the fluid or the like can be evenly dispersed throughout the heat exchange core 10.

[0242] (13) In several embodiments, based on any of the structures of (1) to (12) above, the plurality of axial flow paths 3 are each divided into a plurality of partitions S in the circumferential direction D2.

[0243] According to the structure of (13) above, by the presence of the walls dividing the axial flow paths 3, the heat transfer efficiency can be improved. Through this wall, the rigidity and strength of the heat exchange core 10, particularly in the radial direction, can be improved.

[0244] (14) In several embodiments, based on the structure of (13) above, in the plurality of axial flow paths 3, the flow path diameters of the plurality of partitions S are homogenized.

[0245] According to the structure of (14) above, by homogenizing the flow states such as frictional losses in all the partitions, it is possible to homogenize the heat transfer rates of all the partitions, and by uniformly dispersing the stress in the entire in-plane direction of the cross-section of the heat exchange core 10, it is possible to achieve stress homogenization.

[0246] (15) The heat exchanger 1 of at least one embodiment of the present disclosure includes a heat exchange core 10 having any one of the structures of (1) to (14) above and a housing 20 that houses the heat exchange core 10.

[0247] According to the structure of (15) above, it is possible to make the heat exchanger 1 relatively compact and improve the heat exchange efficiency.

[0248] (16) The manufacturing method of the heat exchange core 10 of at least one embodiment of the present disclosure is a manufacturing method of the heat exchange core 10, including: a core main body forming step S1 of forming a core main body 13 including a plurality of axial flow paths 3 extending along the axial direction D1 by laminated modeling; and a header forming step S3 of forming a header 11 adjacent to at least one end of the core main body 13 in the axial direction D1 and having a header flow path 6 communicating with the plurality of axial flow paths 3 by laminated modeling.

[0249] The header forming step S3 forms the header flow path 6 in such a manner as to include at least one radial flow path 61 extending in the radial direction and a plurality of circumferential flow paths 66 branched from any one of the radial flow paths 61 and respectively communicating with one or more axial flow paths 3. The header forming step S3 forms each radial flow path 61 in such a manner that the flow path area Ca2 at a second position P2 radially inside the first position P1 is smaller than the flow path area Ca1 at the first position P1.

[0250] According to the method of (16) above, by laminated modeling, it is possible to integrally form the heat exchange core 10, so there is no need for component assembly or sealing between components using gaskets. Therefore, the adjustment effort can be significantly reduced.

[0251] (17) The manufacturing method of the heat exchange core 10 of at least one embodiment of the present disclosure is a manufacturing method of the heat exchange core 10, including: a core main body forming step S1 of forming a core main body 13 including a plurality of axial flow paths 3 extending along the axial direction D1 by laminated modeling; and a header forming step S3 of forming a header 11 adjacent to at least one end of the core main body 13 in the axial direction D1 and having a header flow path 6 communicating with the plurality of axial flow paths 3 by laminated modeling.

[0252] The header part forming step S3 forms the header flow path 6 in such a manner as to include at least one radial flow path 61 extending in the radial direction and a plurality of circumferential flow paths 66 branched from any one of the radial flow paths 61 and respectively communicating with one or more axial flow paths 3. The header part forming step S3 forms the header part 11 in such a manner as to form at least one opening part 63 formed by at least one radial flow path 61 on the outer peripheral surface of the heat exchange core 10 at the header part 11, and forms the header part 11 in such a manner that the opening dimension AL1 along the axial direction D1 in each opening part 63 is 1 time or more the opening dimension AL2 along the circumferential direction D2 in each opening part 63.

[0253] According to the method of the above (17), by additive manufacturing, the heat exchange core 10 can be integrally formed, so that there is no need for component assembly and sealing between components using gaskets. Therefore, the labor for adjustment can be significantly reduced.

[0254] (Regarding modification examples of the radial flow path and the circumferential flow path)

[0255] Hereinafter, modification examples of the radial flow path 61 and the circumferential flow path 66 will be described.

[0256] Figure 13 is a cross-sectional view taken along line IV-IV in the modification examples of the radial flow path and the circumferential flow path Figure 2 of

[0257] Figure 14 is a schematic diagram showing the flow of each of the first fluid and the second fluid in the modification examples of the radial flow path and the circumferential flow path.

[0258] Figure 15A is a schematic diagram of the radial flow path and the circumferential flow path for explaining one embodiment in the modification examples of the radial flow path and the circumferential flow path, and is a diagram showing the second cross-section C2.

[0259] Figure 15B is a schematic diagram of the radial flow path and the circumferential flow path for explaining another embodiment in the modification examples of the radial flow path and the circumferential flow path, and is a diagram showing the second cross-section C2.

[0260] Figure 16 is a schematic diagram for explaining the total angle range, and is equivalent to a diagram showing a part of the second cross-section C2. It should be noted that in Figure 16 in, Figure 15B a part of the second cross-section C2 in another embodiment shown in is enlarged and shown.

[0261] It should be noted that in several embodiments regarding the modification examples of the radial flow path 61 and the circumferential flow path 66, as Figure 13As shown, it is preferable that the flow path cross-sectional areas of the plurality of radial flow paths 61 distributed in the circumferential direction D2 are equal. In this way, it is possible to uniformly ensure the lengths of the sections in which the first fluid and the second fluid flow relative to each other along the axial direction D1 in the circumferential direction D2 of the first flow path 101 and the second flow path 102. It should be noted that tolerances in the flow path cross-sectional areas of the respective radial flow paths 61 are allowed.

[0262] The shape of the cross-section of each radial flow path 61 and the shape of the opening in the side wall W0 are Figure 1 and Figure 2 rectangular in the example shown, but may be an appropriate shape such as circular.

[0263] The axes of the transverse walls W3 are located on the same straight line.

[0264] In the heat exchange core 10 of several embodiments in the modified examples of the radial flow path 61 and the circumferential flow path 66, the first header portion 11A and the second header portion 11B have the same structure. Therefore, in the following description, the first header portion 11A and the second header portion 11B are not distinguished, and the letters A and B are not marked in the reference numerals, and only the header portion 11 is described.

[0265] As Figure 15A and Figure 15B shown, in the header portion 11 of several embodiments in the modified examples of the radial flow path 61 and the circumferential flow path 66, the header flow path 6 includes at least one radial flow path 61 extending in the radial direction. In the header portion 11 of several embodiments in the modified examples, the header flow path 6 includes a plurality of circumferential flow paths 66 branched from any one of the radial flow paths 61 and respectively communicating with one or more axial flow paths 3. It should be noted that the circumferential flow paths 66 in several embodiments of the modified examples are the first flow paths 101 extending in the circumferential direction and the axial direction in the header portion 11 among the plurality of first flow paths 101.

[0266] By including at least one radial flow path 61 and a plurality of circumferential flow paths 66 branched from any one of the radial flow paths 61 and respectively communicating with one or more axial flow paths 3 in the header flow path 6, the header portion 11 can be made relatively smaller.

[0267] In the heat exchanger 1 of several embodiments of the modified example, the header flow path 6 allows the first fluid flowing radially into the radial flow path 61 to flow circumferentially in the circumferential flow path 66, and also turns the flow direction axially to distribute it to the first flow paths 101 disposed in the core main body 13 respectively. Further, in the heat exchanger 1 of several embodiments of the modified example, the flow of the first fluid flowing axially in the core main body 13 is turned radially while flowing through the circumferential flow path 66 and the radial flow path 61. Therefore, the flow rate of the first fluid flowing in the core main body 13 may vary depending on the circumferential and radial positions, and the heat exchange efficiency may be reduced due to such differences in flow rate.

[0268] In the heat exchanger 1 of several embodiments of the modified example, in order to suppress the volume expansion of the header portion 11 and suppress the difference in the flow rate of the first fluid, it has the structure described below. Hereinafter, the structure for suppressing the difference in the flow rate of the first fluid while suppressing the volume expansion of the header portion 11 will be described in sequence.

[0269] For example, as Figure 16 shown, in the heat exchanger 1 of several embodiments of the modified example, the circumferential flow path 66 extends from one end 66a which is an open end and connected to the radial flow path to the other end 66b which is a closed end.

[0270] In the following description, the length along the circumferential direction from one end 66a to the other end 66b in the circumferential flow path 66 is referred to as the flow path length Lc.

[0271] Further, in the following description, each layer in the circumferential flow path 66 arranged in layers along the radial direction is also referred to as a segmented flow path 66s.

[0272] In the following description, the total angular range θt is the sum of the angular ranges centered on the radial center position (axis AX) when moving along the circumferential flow path 66 from one end 66a to the other end 66b. That is, the total angular range θt is the cumulative value of the change amount of the angle when centered on the radial center position (axis AX) from one end 66a to the other end 66b of the circumferential flow path 66. The total angular range θt is, as described later, the sum of the angular ranges in which each segmented flow path 66s included in one circumferential flow path 66 extends.

[0273] Figure 16 As shown, the outermost circumferential flow path 66-1 is composed of Figure 16 the outermost segmented flow path 66s shown. Therefore, the total angular range θt in this circumferential flow path 66-1 becomes Figure 16 the angular range θ1 of the outermost segmented flow path 66s shown.

[0274] For example, on the radial inner side and Figure 16The circumferential flow path 66-2 adjacent to the outermost circumferential flow path 66-1 shown is composed of the segmented flow path 66s of the second layer and the segmented flow path 66s of the third layer counted from the outermost segmented flow path 66s shown. That is, in this circumferential flow path 66-2, the end of the segmented flow path 66s of the second layer on the side opposite to one end 66a is connected to the end of the segmented flow path 66s of the third layer along the radial direction. This circumferential flow path 66-2 is composed of the segmented flow path 66s of the second layer and the segmented flow path 66s of the third layer to form one circumferential flow path 66. Figure 16 The circumferential flow path 66-2 adjacent to the outermost circumferential flow path 66-1 shown is composed of the segmented flow path 66s of the second layer and the segmented flow path 66s of the third layer counted from the outermost segmented flow path 66s shown. That is, in this circumferential flow path 66-2, the end of the segmented flow path 66s of the second layer on the side opposite to one end 66a is connected to the end of the segmented flow path 66s of the third layer along the radial direction. This circumferential flow path 66-2 is composed of the segmented flow path 66s of the second layer and the segmented flow path 66s of the third layer to form one circumferential flow path 66.

[0275] Therefore, the total angular range θt in this circumferential flow path 66-2 becomes the sum of the angular range θ2 of the segmented flow path 66s of the second layer and the angular range θ3 of the segmented flow path 66s of the third layer.

[0276] In addition, in Figure 16 the example shown, one circumferential flow path 66-3 is formed by the segmented flow path 66s of the fourth layer, the segmented flow path 66s of the fifth layer, and the segmented flow path 66s of the sixth layer starting from the outermost segmented flow path 66s shown. That is, in this circumferential flow path 66-3, the end of the segmented flow path 66s of the fourth layer on the side opposite to one end 66a is connected to the end of the segmented flow path 66s of the fifth layer along the radial direction. In this circumferential flow path 66-3, the end of the segmented flow path 66s of the fifth layer on the same side as one end 66a is connected to the end of the segmented flow path 66s of the sixth layer along the radial direction. Figure 16 the example shown, one circumferential flow path 66-3 is formed by the segmented flow path 66s of the fourth layer, the segmented flow path 66s of the fifth layer, and the segmented flow path 66s of the sixth layer starting from the outermost segmented flow path 66s shown. That is, in this circumferential flow path 66-3, the end of the segmented flow path 66s of the fourth layer on the side opposite to one end 66a is connected to the end of the segmented flow path 66s of the fifth layer along the radial direction. In this circumferential flow path 66-3, the end of the segmented flow path 66s of the fifth layer on the same side as one end 66a is connected to the end of the segmented flow path 66s of the sixth layer along the radial direction.

[0277] Therefore, the total angular range θt in this circumferential flow path 66-3 is the sum of the angular range θ4 of the segmented flow path 66s of the fourth layer, the angular range θ5 of the segmented flow path 66s of the fifth layer, and the angular range θ6 of the segmented flow path 66s of the sixth layer.

[0278] The connection part between adjacent segmented flow paths 66s in the radial direction is called the turning part 66f. In addition, the number of turning parts 66f in one circumferential flow path 66 is called the turning number.

[0279] The circumferential flow path 66 with the turning part 66f will be described in detail later.

[0280] It should be noted that in Figure 16 the outermost circumferential flow path 66 shown, since there is no turning part 66f, the turning number is 0.

[0281] Here, consider the circumferential flow path 66 called the first circumferential flow path 661 and the circumferential flow path 66 called the second circumferential flow path 662 located on the radially inner side of the first circumferential flow path 661.

[0282] For ease of explanation, the circumferential flow path length Lc of the first circumferential flow path 661 is referred to as the first flow path length L1, and the circumferential flow path length Lc of the second circumferential flow path 662 is referred to as the second flow path length L2.

[0283] For example, in Figure 16 the range shown, in the relationship between the outermost circumferential flow path 66-1 and the other circumferential flow paths 66-2 and 66-3, the outermost circumferential flow path 66-1 corresponds to the first circumferential flow path 661, and the other circumferential flow paths 66-2 and 66-3 correspond to the second circumferential flow path 662.

[0284] It should be noted that, for example, in Figure 16 the range shown, in the relationship between the innermost circumferential flow path 66-3 in the radial direction and the other circumferential flow paths 66-1 and 66-2, the innermost circumferential flow path 66-3 in the radial direction corresponds to the second circumferential flow path 662, and the other circumferential flow paths 66-1 and 66-2 correspond to the first circumferential flow path 661.

[0285] It should be noted that if there are circumferential flow paths not shown that are radially outside the outermost circumferential flow path 66-1 existing in Figure 16 the range shown, then in the relationship between the unshown circumferential flow path and the outermost circumferential flow path 66-1 and the other circumferential flow paths 66-2 and 66-3, the unshown circumferential flow path and the outermost circumferential flow path 66-1 correspond to the first circumferential flow path 661, and the other circumferential flow paths 66-2 and 66-3 correspond to the second circumferential flow path 662.

[0286] As described above, the first circumferential flow path 661 and the second circumferential flow path 662 have been described with reference to Figure 16 However, not only in Figure 15B the other embodiments shown, Figure 15A but also in each circumferential flow path 66 of the one embodiment shown is the same.

[0287] Even for the same total angular range θt, due to the difference in the radial position, among the first flow path length L1 in the first circumferential flow path 661 and the second flow path length L2 in the second circumferential flow path 662, the first flow path length L1 is longer. Therefore, if the flow path width (radial width) is the same, the pressure loss of the first circumferential flow path 661 is greater than that of the second circumferential flow path 662, and it is difficult for the first fluid to flow.

[0288] Therefore, in the heat exchange core 10 of several embodiments of the modified example, the equal length in the plurality of circumferential flow paths 66 is ensured, and the flow rate deviation in the axial flow path 3 is suppressed. That is, in the heat exchange core 10 of several embodiments of the modified example, by suppressing the deviation of the flow path length Lc of each of the plurality of circumferential flow paths 66, the flow rate of the first fluid flowing from the circumferential flow path 66 into the axial flow path 3 and flowing from the axial flow path 3 into the circumferential flow path 66 does not deviate due to the circumferential flow path 66.

[0289] Specifically, in the heat exchange core 10 of several embodiments of the modified example, as described later, a plurality of circumferential flow paths 66 are configured to include a first circumferential flow path 661 and a second circumferential flow path 662 located at a position radially inside the first circumferential flow path 661 and arranged circumferentially within a total angle range θt larger than that of the first circumferential flow path 661.

[0290] That is, in the heat exchange core 10 of several embodiments of the modified example, as described later, the total angle range θt of the first circumferential flow path 661 is smaller than the total angle range θt of the second circumferential flow path 662.

[0291] Thereby, compared with the case where the total angle range θt is the same in the first circumferential flow path 661 and the second circumferential flow path 662, the difference between the first flow path length L1 and the second flow path length L2 can be suppressed. Therefore, it is possible to suppress the pressure loss of the first circumferential flow path 661 from being larger than the pressure loss of the second circumferential flow path 662, and the difference in the flow velocity between the first circumferential flow path 661 and the second circumferential flow path 662 can be suppressed. Therefore, the difference in the flow rate of the first fluid in the axial flow path 3 connected to the first circumferential flow path 661 and the flow rate of the first fluid in the axial flow path 3 connected to the second circumferential flow path 662 can be suppressed, and the heat exchange efficiency in the heat exchange core 10 can be improved.

[0292] (Regarding the radial flow path in the header part in one embodiment of the modified example)

[0293] Hereinafter, mainly Figure 15A the radial flow path 61 in the header part 11 of the embodiment shown will be described. It should be noted that even for the content regarding the circumferential flow path 66, for the sake of convenience of explanation, the circumferential flow path 66 will also be described for the content that is preferably described in relation to the relationship with the radial flow path 61.

[0294] In Figure 15A the header part 11 of the embodiment shown, a plurality of radial flow paths 61 having different radial lengths are arranged at intervals in the circumferential direction. More specifically, in Figure 15A the header part 11 of the embodiment shown, a variety of radial flow paths 61 having different distances from the side wall W0 to the radially inner end are formed. Figure 15AThe radial flow path 61 of an embodiment shown includes a first radial flow path 611 with the shortest radial length, a second radial flow path 612 with the second shortest radial length, a third radial flow path 613 with the third shortest radial length, and a fourth radial flow path 614 with the fourth shortest (longest) radial length.

[0295] It should be noted that, in Figure 15A the header section 11 of an embodiment shown, a turning section 66f is not provided in the circumferential flow path 66.

[0296] In a radial flow path 61 of an embodiment in a modified example, regardless of which of the radial flow paths 611, 612, 613, 614 it is, the radially outer end of the radial flow path 61 is located on the outer peripheral surface of the side wall W0.

[0297] It should be noted that the radial flow path 61 of an embodiment in a modified example is not limited to Figure 15A the example shown. As long as it includes at least two radial flow paths 61 with different radial lengths. In addition, the radial flow path 61 of an embodiment in a modified example is not limited to Figure 15A the example shown. It may also include five radial flow paths 61 with different radial lengths.

[0298] Thus, in Figure 15A the header section 11 of an embodiment shown, a radial flow path group with different heights is formed by a plurality of radial flow paths 61 with different radial positions of the radially inner ends.

[0299] In this specification, when describing two radial flow paths 61 with different radial lengths, the radial flow path 61 of the type with a shorter radial length among the two radial flow paths 61 is also referred to as the first radial flow path 601, and the radial flow path 61 of the type with a longer radial length is also referred to as the second radial flow path 602.

[0300] For example, when describing the first radial flow path 611 with the shortest radial length and the second radial flow path 612 with the second shortest radial length, the first radial flow path 611 corresponds to the first radial flow path 601, and the second shortest second radial flow path 612 corresponds to the second radial flow path 602.

[0301] Similarly, for example, when describing the second radial flow path 612 with the second shortest radial length and the fourth radial flow path 614 with the fourth shortest radial length, the second radial flow path 612 corresponds to the first radial flow path 601, and the fourth radial flow path 614 corresponds to the second radial flow path 602.

[0302] It should be noted that the first radial flow path 611 with the shortest radial length is equivalent to the first radial flow path 601 when compared with any other radial flow paths 612, 613, and 614. Also, the fourth radial flow path 614 with the fourth shortest (longest) radial length is equivalent to the second radial flow path 602 when compared with any other types of radial flow paths 611, 612, and 613. The second radial flow path 612 with the second shortest radial length and the third radial flow path 613 with the third shortest radial length may be equivalent to the first radial flow path 601 or the second radial flow path 602 depending on the type of the radial flow path 61 serving as the comparison object.

[0303] In Figure 15A In the header portion 11 of the embodiment shown, each radial flow path 61 communicates with all or a part of the circumferential flow paths 66 adjacent to itself on one side and the other side in the circumferential direction.

[0304] For example, in one embodiment of the modification, the first radial flow path 611 communicates with all the circumferential flow paths 66 adjacent to itself on one side and the other side in the circumferential direction. The circumferential flow paths 66 communicating with the first radial flow path 611 are referred to as the first circumferential flow paths 671.

[0305] For example, in one embodiment of the modification, the second radial flow path 612 communicates with all the circumferential flow paths 66 adjacent to itself on one side and the other side in the circumferential direction only within a range radially inward of the radial range occupied by the first radial flow path 611. That is, in one embodiment of the modification, the second radial flow path 612 does not communicate with the circumferential flow paths 66 adjacent to itself in the circumferential direction within the radial range occupied by the first radial flow path 611. The circumferential flow paths 66 communicating with the second radial flow path 612 are referred to as the second circumferential flow paths 672.

[0306] For example, in one embodiment of the modification, the third radial flow path 613 communicates with all the circumferential flow paths 66 adjacent to itself on one side and the other side in the circumferential direction only within a range radially inward of the radial range occupied by the second radial flow path 612. That is, in one embodiment of the modification, the third radial flow path 613 does not communicate with the circumferential flow paths 66 adjacent to itself in the circumferential direction within the radial range occupied by the second radial flow path 612. The circumferential flow paths 66 communicating with the third radial flow path 613 are referred to as the third circumferential flow paths 673.

[0307] For example, the fourth radial flow path 614 of an embodiment in the modified example is limited to a range radially inside the radial range occupied by the third radial flow path 613, and communicates with all the circumferential flow paths 66 adjacent to each other on one side and the other side in the circumferential direction with respect to itself. That is, the fourth radial flow path 614 of an embodiment in the modified example does not communicate with the circumferential flow paths 66 adjacent to it in the circumferential direction within the radial range occupied by the third radial flow path 613. The circumferential flow paths 66 communicating with the fourth radial flow path 614 are referred to as the fourth circumferential flow paths 674.

[0308] In Figure 15A In the header section 11 of an embodiment shown, as indicated by the arrow a1, the first fluid flowing into the interior of the first inlet header 221 from the inlet port 22A flows from the first radial flow path 611 to the first circumferential flow path 671, flows in the circumferential direction from one end 66a to the other end 66b in the first circumferential flow path 671, and flows axially toward the axial flow path 3.

[0309] Similarly, as indicated by the arrow a2, the first fluid flowing into the interior of the first inlet header 221 from the inlet port 22A flows from the second radial flow path 612 to the second circumferential flow path 672, flows in the circumferential direction from one end 66a to the other end 66b in the second circumferential flow path 672, and flows axially toward the axial flow path 3.

[0310] As indicated by the arrow a3, the first fluid flowing into the interior of the first inlet header 221 from the inlet port 22A flows from the third radial flow path 613 to the third circumferential flow path 673, flows in the circumferential direction from one end 66a to the other end 66b in the third circumferential flow path 673, and flows axially toward the axial flow path 3.

[0311] As indicated by the arrow a4, the first fluid flowing into the interior of the first inlet header 221 from the inlet port 22A flows from the fourth radial flow path 614 to the fourth circumferential flow path 674, flows in the circumferential direction from one end 66a to the other end 66b in the fourth circumferential flow path 674, and flows axially toward the axial flow path 3.

[0312] For example, in Figure 15A In an embodiment shown, in the relationship between the first circumferential flow path 671 and other types of circumferential flow paths 672, 673, 674, the first circumferential flow path 671 corresponds to the first circumferential flow path 661, and the other types of circumferential flow paths 672, 673, 674 correspond to the second circumferential flow path 662.

[0313] In addition, for example, in Figure 15AIn one embodiment shown, in the relationship between the first circumferential flow path 671 and the second circumferential flow path 672 and the third circumferential flow path 673 and the fourth circumferential flow path 674, the first circumferential flow path 671 and the second circumferential flow path 672 correspond to the first circumferential flow path 661, and the third circumferential flow path 673 and the fourth circumferential flow path 674 correspond to the second circumferential flow path 662.

[0314] For example, in Figure 15A In one embodiment shown, in the relationship between the fourth circumferential flow path 674 and the other types of circumferential flow paths 671, 672, and 673, the fourth circumferential flow path 674 corresponds to the second circumferential flow path 662, and the other types of circumferential flow paths 671, 672, and 673 correspond to the first circumferential flow path 661.

[0315] That is, in Figure 15A In one embodiment shown, the radial flow path 61 includes a first radial flow path 601 and a second radial flow path 602. The first radial flow path 601 communicates with the first circumferential flow path 661. The second radial flow path 602 is provided within the radial range occupied by the first radial flow path 601 and within a range radially inward of this radial range, and communicates with the second circumferential flow path 662.

[0316] In addition, in Figure 15A In one embodiment shown, the first radial flow path 601 does not communicate with the second circumferential flow path 662, and the second radial flow path 602 does not communicate with the first circumferential flow path 661.

[0317] In Figure 15A , in order to facilitate the description of the circumferential arrangement positions of the respective radial flow paths 61, an angle centered on the axis AX is defined as follows.

[0318] In Figure 15A In one embodiment shown, for example, two fourth radial flow paths 614 having the fourth shortest (longest radial length) radial lengths are provided and arranged at positions offset from each other by 180 degrees across the axis AX. Moreover, one of the two fourth radial flow paths 614 is arranged at an angular position of 90 degrees, and the other is arranged at an angular position of 270 degrees.

[0319] In addition, the upper side of the illustration in Figure 15A is set as the angular position of 90 degrees, the lower side of the illustration is set as the angular position of 270 degrees, the right side of the illustration is set as the angular position of 0 degrees, and the left side of the illustration is set as the angular position of 180 degrees.

[0320] In Figure 15AIn one embodiment shown, a partition wall (second partition wall) W5 is formed at angular positions of 0 degrees and 180 degrees. The second partition wall W5 separates the circumferential flow path 66 at the angular positions of 0 degrees and 180 degrees on one side and the other side in the circumferential direction with the second partition wall W5 interposed therebetween.

[0321] It should be noted that although not shown, the second partition wall W5 can also be formed to separate the second flow path 102 on one side and the other side in the circumferential direction with the second partition wall W5 interposed therebetween.

[0322] In Figure 15A In one embodiment shown, the region on one side sandwiching the second partition wall W5, that is, the region with an angular range from 0 degrees to 180 degrees, is also referred to as the upper half region Ru, and the region on the other side sandwiching the second partition wall W5, that is, the region with an angular range from 180 degrees to 360 degrees, is also referred to as the lower half region Rd.

[0323] In Figure 15A In one embodiment shown, the upper half region Ru and the lower half region Rd can also be formed to be symmetric with the second partition wall W5 interposed therebetween.

[0324] In Figure 15A In one embodiment shown, in each of the upper half region Ru and the lower half region Rd, multiple radial flow paths 61 of other types except the fourth type of radial flow path 614 are arranged at equal intervals along the circumferential direction according to the type of each radial flow path 61. In addition, in Figure 15A In one embodiment shown, the circumferential arrangement intervals between any two adjacent radial flow paths 61 in the circumferential direction are equal to each other.

[0325] It should be noted that, in Figure 15A In one embodiment shown, as described above, one of the two fourth type of radial flow paths 614 is arranged at an angular position of 90 degrees, and the other is arranged at an angular position of 270 degrees, so two are arranged at equal intervals along the circumferential direction.

[0326] That is, in Figure 15A In one embodiment shown, two or more first radial flow paths 601 are arranged at equal intervals along the circumferential direction. Two or more second radial flow paths 602 are arranged at equal intervals along the circumferential direction.

[0327] Thus, compared with the case where the first radial flow paths 601 are arranged at unequal intervals, differences in the length of the flow paths of the circumferential flow path 66 due to the connected first radial flow paths 601 can be suppressed, and deviations in the flow rate in each flow path of the circumferential flow path 66 can be suppressed. Similarly, compared with the case where the second radial flow paths 602 are arranged at unequal intervals, differences in the length of the flow paths of the circumferential flow path 66 due to the connected second radial flow paths 602 can be suppressed, and deviations in the flow rate in each flow path of the circumferential flow path 66 can be suppressed. Thus, a decrease in the heat exchange efficiency can be suppressed.

[0328] In addition, by arranging them at equal intervals, the radial flow paths 61 can be efficiently arranged, and the number of radial flow paths 61 can be suppressed. Thus, the proportion of the area occupied by the radial flow paths 61 in the cross-section (second cross-section C2) of the header portion 11 when viewed from the axial direction can be suppressed, and the proportion of the area occupied by the circumferential flow path 66 can be increased.

[0329] In Figure 15A In one embodiment shown, the shorter the radial length, the more the number of arranged roots. Specifically, in Figure 15A In one embodiment shown, 16 first radial flow paths 611 are arranged, 8 second radial flow paths 612 are arranged, 4 third radial flow paths 613 are arranged, and 2 fourth radial flow paths 614 are arranged. Therefore, in Figure 15A In one embodiment shown, the shorter the radial length, the smaller the circumferential arrangement pitch along the radial flow path 61.

[0330] That is, in Figure 15A In one embodiment shown, the number of first radial flow paths 601 is larger than the number of second radial flow paths 602.

[0331] Thus, compared with the case where the number of first radial flow paths 601 is smaller than the number of second radial flow paths 602, the distance by which two adjacent first radial flow paths 601 are separated in the circumferential direction can be reduced, and thus the first flow path length L1 of the first circumferential flow path 661 can be suppressed. Thus, the difference between the first flow path length L1 of the first circumferential flow path 661 and the second flow path length L2 of the second circumferential flow path 662 can be suppressed, and thus the pressure loss difference between the second circumferential flow path 662 and the first circumferential flow path 661 can be suppressed, and the flow velocity difference between the first circumferential flow path 661 and the second circumferential flow path 662 can be suppressed.

[0332] (Regarding the circumferential flow path in the header portion in an embodiment of the modification)

[0333] Hereinafter, regarding Figure 15A the circumferential flow path 66 in the header portion 11 of one embodiment shown, points not mentioned in the above description will be mainly described.

[0334] In Figure 15A In the header part 11 of one embodiment shown above, as described above, the circumferential flow paths 66 are respectively connected to any one of the radial flow paths 61 at one end 66a which is an open end. Figure 15A In one embodiment shown above, the circumferential flow paths 66 are respectively separated from the other radial flow path 61 by a transverse wall W3 in the other radial flow path 61 different from the radial flow path 61 at the other end 66b or are separated from another circumferential flow path 66 adjacent to the circumferential flow path 66 in the circumferential direction by a second partition wall W5.

[0335] In Figure 15A In one embodiment shown above, for example, if we focus on the first radial flow path 611 with the shortest radial length and the second radial flow path 612 with the second shortest radial length, as described above, the first radial flow path 611 corresponds to the first radial flow path 601, and the second shortest second radial flow path 612 corresponds to the second radial flow path 602. In this case, if we focus on the first circumferential flow path 671 communicating with the first radial flow path 611 and the second circumferential flow path 672 communicating with the second radial flow path 612, the first circumferential flow path 671 corresponds to the first circumferential flow path 661, and the second circumferential flow path 672 corresponds to the second circumferential flow path 662.

[0336] Similarly, for example, if we focus on the second radial flow path 612 with the second shortest radial length and the fourth radial flow path 614 with the fourth shortest radial length, as described above, the second radial flow path 612 corresponds to the first radial flow path 601, and the fourth radial flow path 614 corresponds to the second radial flow path 602. In this case, if we focus on the second circumferential flow path 672 communicating with the second radial flow path 612 and the fourth circumferential flow path 674 communicating with the fourth radial flow path 614, the second circumferential flow path 672 corresponds to the first circumferential flow path 661, and the fourth circumferential flow path 674 corresponds to the second circumferential flow path 662.

[0337] In Figure 15A In one embodiment shown above, for example, when focusing on the first radial flow path 611 and the second radial flow path 612 adjacent to each other in the circumferential direction, the total angular range θt2 of the second circumferential flow path 672 communicating with the second radial flow path 612 is larger than the total angular range θt1 of the first circumferential flow path 671 communicating with the first radial flow path 611.

[0338] In Figure 15AIn one embodiment shown, for example, when focusing on the second radial flow path 612 and the third radial flow path 613 adjacent in the circumferential direction, the total angular range θt3 of the third circumferential flow path 673 communicating with the third radial flow path 613 is larger than the total angular range θt2 of the second circumferential flow path 672 communicating with the second radial flow path 612.

[0339] In Figure 15A In one embodiment shown, for example, when focusing on the third radial flow path 613 and the fourth radial flow path 614 adjacent in the circumferential direction, the total angular range θt4 of the fourth circumferential flow path 674 communicating with the fourth radial flow path 614 is larger than the total angular range θt3 of the third circumferential flow path 673 communicating with the third radial flow path 613.

[0340] That is, in Figure 15A In one embodiment shown, the total angular range Ot of the second circumferential flow path 662 is larger than the total angular range θt of the first circumferential flow path 661.

[0341] In Figure 15A In one embodiment shown, for example, the second circumferential flow path 672 extends in the circumferential direction through the first radial flow path 611 from the second radial flow path 612 to the opposite side across the first radial flow path 611.

[0342] Similarly, in Figure 15A In one embodiment shown, for example, the third circumferential flow path 673 extends in the circumferential direction through the second radial flow path 612 from the third radial flow path 613 to the opposite side across the second radial flow path 612.

[0343] In Figure 15A In one embodiment shown, for example, the fourth circumferential flow path 674 extends in the circumferential direction through the third radial flow path 613 from the fourth radial flow path 614 to the opposite side across the third radial flow path 613.

[0344] That is, in Figure 15A In one embodiment shown, the second circumferential flow path 662 extends in the circumferential direction through the first radial flow path 601 from the second radial flow path 602 to the opposite side across the first radial flow path 601.

[0345] Thereby, the shapes of the first circumferential flow path 661 and the second circumferential flow path 662 are not complicated, the total angular range θt of the second circumferential flow path 662 can be made larger than the total angular range θt of the first circumferential flow path 661, and the difference in flow velocity between the first circumferential flow path 661 and the second circumferential flow path 662 can be suppressed.

[0346] In Figure 15AIn one embodiment shown above, as described above, the first radial flow path 601 is not in communication with the second circumferential flow path 662, and the second radial flow path 602 is not in communication with the first circumferential flow path 661.

[0347] Thus, when the first fluid flows from the first radial flow path 601 to the first circumferential flow path 661, all of the first fluid from the first radial flow path 601 can be supplied to the first circumferential flow path 661. Therefore, it is possible to suppress insufficient supply of the first fluid to the first circumferential flow path 661 and suppress a decrease in heat exchange efficiency.

[0348] Similarly, when the first fluid flows from the second radial flow path 602 to the second circumferential flow path 662, all of the fluid from the second radial flow path 602 can be supplied to the second circumferential flow path 662. Therefore, it is possible to suppress insufficient supply of the first fluid to the second circumferential flow path 662 and suppress a decrease in heat exchange efficiency.

[0349] In addition, when the first fluid flows from the first circumferential flow path 661 to the first radial flow path 601, the first fluid from the second circumferential flow path 662 does not flow into the first radial flow path 601. Therefore, it is possible to prevent the flow rate of the first fluid flowing in the first radial flow path 601 from increasing due to the first fluid from the second circumferential flow path 662. As a result, it is possible to suppress an increase in pressure loss in the first radial flow path 601 and suppress a decrease in flow rate in the first circumferential flow path 661, thereby suppressing a decrease in heat exchange efficiency.

[0350] Similarly, when the first fluid flows from the second circumferential flow path 662 to the second radial flow path 602, the first fluid from the first circumferential flow path 661 does not flow into the second radial flow path 602. Therefore, it is possible to prevent the flow rate of the first fluid flowing in the second radial flow path 602 from increasing due to the fluid from the first circumferential flow path 661. As a result, it is possible to suppress an increase in pressure loss in the second radial flow path 602 and suppress a decrease in flow rate in the second circumferential flow path 662, thereby suppressing a decrease in heat exchange efficiency.

[0351] In Figure 15A In one embodiment shown above, as described above, the radial flow path 61 is connected to the circumferential flow paths 66 located on one side and the other side in the circumferential direction with respect to the radial flow path 61.

[0352] Thus, compared with the case where the radial flow path 61 is only connected to the circumferential flow path 66 on either one side or the other side in the circumferential direction with respect to the radial flow path 61, the number of radial flow paths 61 can be suppressed. As a result, it is possible to suppress the proportion of the area occupied by the radial flow paths 61 in the cross-section of the header portion 11 when viewed from the axial direction and increase the proportion of the area occupied by the circumferential flow paths 66.

[0353] It should be noted that inFigure 15A In one embodiment shown, the flow path length Lc of the circumferential flow path 66 can be adjusted by the number of radial flow paths 61, the number of variations in the radial length, the lengths of various types of radial directions, and the arrangement pattern. Therefore, it is desirable to minimize the difference in the flow path length Lc as much as possible.

[0354] (Regarding the radial flow path in the header part of other embodiments in the modification example)

[0355] Hereinafter, also with reference to Figure 16 , mainly Figure 15B the radial flow path 61 in the header part 11 of the other embodiment shown will be described.

[0356] In Figure 15B the header part 11 of the other embodiment shown, a plurality of radial flow paths 61 having equal radial lengths are arranged at intervals in the circumferential direction. More specifically, in Figure 15B the header part 11 of the other embodiment shown, four identical types of radial flow paths 61 having equal distances from the side wall W0 to the inner end in the radial direction are formed at equal intervals in the circumferential direction.

[0357] In this way, by arranging the plurality of radial flow paths 61 at equal intervals in the circumferential direction, compared with the case where the radial flow paths 61 are arranged at unequal intervals, it is possible to suppress the difference in the flow path length Lc of the circumferential flow path 66 due to the connected radial flow paths 61, and it is possible to suppress the deviation of the flow rate in each flow path in the circumferential flow path 66.

[0358] In addition, by arranging at equal intervals, the radial flow paths 61 can be arranged efficiently, and the number of radial flow paths 61 can be suppressed. As a result, it is possible to suppress the increase in the proportion of the area occupied by the radial flow paths 61 in the cross section (second cross section C2) of the header part 11 when viewed from the axial direction and increase the proportion of the area occupied by the circumferential flow path 66.

[0359] In the radial flow path 61 of the other embodiment of the modification example, the outer ends in the radial direction of the radial flow paths 61 are all located on the outer peripheral surface of the side wall W0.

[0360] The radial flow path 61 of the other embodiment of the modification example communicates with the circumferential flow paths 66 adjacent to it on one side and the other side in the circumferential direction at one end 66a of the circumferential flow path 66. That is, in Figure 15B the header part 11 of the other embodiment shown, the first circumferential flow path 661 and the second circumferential flow path 662 communicate with the same radial flow path 61.

[0361] Accordingly, compared with the case where the first circumferential flow path 661 and the second circumferential flow path 662 are connected to different radial flow paths 61, the number of the radial flow paths 61 can be suppressed. Accordingly, the proportion of the area occupied by the radial flow paths 61 in the cross-section (second cross-section C2) of the header portion 11 when viewed axially can be suppressed, and the proportion of the area occupied by the circumferential flow paths 66 can be increased.

[0362] In Figure 15B in order to facilitate the description of the circumferential arrangement positions of the respective radial flow paths 61, an angle centered on the axis AX is defined as follows.

[0363] In Figure 15B in the other embodiment shown, for example, four radial flow paths 61 are arranged at intervals of 90 degrees. The four radial flow paths 61 are arranged at angular positions of 0 degrees, 90 degrees, 180 degrees, and 270 degrees.

[0364] In addition, the upper side of the illustration in Figure 15B is set as the angular position of 90 degrees, the lower side of the illustration is set as the angular position of 270 degrees, the right side of the illustration is set as the angular position of 0 degrees, and the left side of the illustration is set as the angular position of 180 degrees.

[0365] In Figure 15B in the other embodiment shown, partitions (second partitions) W5 are formed at angular positions of 45 degrees, 135 degrees, 225 degrees, and 315 degrees. In Figure 15B in the other embodiment shown, the second partition W5 separates the circumferential flow path 66 on one side and the other side in the circumferential direction with the second partition W5 interposed therebetween at the above angular positions.

[0366] It should be noted that although not shown, the second partition W5 can also be formed to separate the second flow path 102 on one side and the other side in the circumferential direction with the second partition W5 interposed therebetween.

[0367] In Figure 15B in the other embodiment shown, the region with an angular range from 0 degrees to 180 degrees is also referred to as the upper half region Ru, and the region with an angular range from 180 degrees to 360 degrees is also referred to as the lower half region Rd.

[0368] In Figure 15B in one embodiment shown, the upper half region Ru and the lower half region Rd can also be formed to be symmetric with the radial flow paths 61 arranged at angular positions of 0 degrees and 180 degrees interposed therebetween. In addition, in Figure 15B in one embodiment shown, it can also be formed to be symmetric with the radial flow paths 61 arranged at angular positions of 90 degrees and 270 degrees interposed therebetween.

[0369] (Regarding the circumferential flow paths in the header portion in other embodiments of the modification example)

[0370] In Figure 15B the header 11 of the other embodiments shown, as described above, the circumferential flow paths 66 are each connected to any one of the radial flow paths 61 at one end 66a which is an open end (see Figure 16 ). Figure 15B In the circumferential flow paths 66 of the other embodiments shown, the other end 66b of each circumferential flow path 66 is separated from the radial flow path 61 by the transverse wall W3 of the radial flow path 61 or is separated from another circumferential flow path 66 adjacent to the circumferential flow path 66 in the circumferential direction by the second partition wall W5.

[0371] In Figure 15B the header 11 of the other embodiments shown, among the plurality of circumferential flow paths 66 arranged radially, at least the circumferential flow path 66 that is outermost in the radial direction does not have the above-described return portion 66f. For example, in Figure 15B the header 11 of the other embodiments shown, the first to third circumferential flow paths 66 from the radial outside in the radial direction do not have the above-described return portion 66f.

[0372] In Figure 15B the header 11 of the other embodiments shown, regarding the plurality of segmented flow paths 66s, they are sequentially referred to as the first segmented flow path 66s-1, the second segmented flow path 66s-2, the third segmented flow path 66s-3, the fourth segmented flow path 66s-4, the fifth segmented flow path 66s-5, the sixth segmented flow path 66s-6, the seventh segmented flow path 66s-7, and the eighth segmented flow path 66s-8 from the radial outside in the radial direction.

[0373] In Figure 15B the header 11 of the other embodiments shown, the first segmented flow path 66s-1, the second segmented flow path 66s-2, and the third segmented flow path 66s-3 each independently form one circumferential flow path 66. The number of returns of each of these one circumferential flow paths 66 is 0.

[0374] In addition, in Figure 15B the header 11 of the other embodiments shown, the fourth segmented flow path 66s-4 and the fifth segmented flow path 66s-5 are connected by the return portion 66f, and one circumferential flow path 66 is formed by the fourth segmented flow path 66s-4 and the fifth segmented flow path 66s-5. The number of returns in this one circumferential flow path 66 is 1.

[0375] In Figure 15BIn the header 11 of the other embodiments shown, the sixth segmented flow path 66s-6 and the seventh segmented flow path 66s-7 are connected by a turning section 66f, and the seventh segmented flow path 66s-7 and the eighth segmented flow path 66s-8 are connected by a turning section 66f. Further, one circumferential flow path 66 is formed by the sixth segmented flow path 66s-6, the seventh segmented flow path 66s-7, and the eighth segmented flow path 66s-8. The number of turnbacks in this one circumferential flow path 66 is 2.

[0376] In Figure 15B In the header 11 of the other embodiments shown, the first fluid flowing into the interior of the first inlet header 221 from the inlet port 22A flows from each radial flow path 61 into the circumferential flow path 66 as indicated by the arrow b.

[0377] In the circumferential flow path 66 formed by the first segmented flow path 66s-1, the circumferential flow path 66 formed by the second segmented flow path 66s-2, and the circumferential flow path 66 formed by the third segmented flow path 66s-3, the first fluid flows circumferentially from one end 66a to the other end 66b and axially toward the axial flow path 3.

[0378] In the circumferential flow path 66 formed by the fourth segmented flow path 66s-4 and the fifth segmented flow path 66s-5, the first fluid flows in a meandering manner circumferentially and radially from one end 66a disposed in the fourth segmented flow path 66s-4 to the other end 66b disposed in the fifth segmented flow path 66s-5, and axially toward the axial flow path 3.

[0379] In the circumferential flow path 66 formed by the sixth segmented flow path 66s-6, the seventh segmented flow path 66s-7, and the eighth segmented flow path 66s-8, the first fluid flows in a meandering manner circumferentially and radially from one end 66a disposed in the sixth segmented flow path 66s-6 to the other end 66b disposed in the eighth segmented flow path 66s-8, and axially toward the axial flow path 3.

[0380] In Figure 15B In the header 11 of the other embodiments shown, the circumferential flow path 66 closer to the radial inner side has more turnback numbers. That is, in Figure 15B In the header 11 of the other embodiments shown, the number of turnbacks of the second circumferential flow path 662 is more than the number of turnbacks of the first circumferential flow path 661.

[0381] By making the number of turnbacks in the second circumferential flow path 662 more than the number of turnbacks in the first circumferential flow path 661, the total angle range θt in the second circumferential flow path 662 can be increased to ensure the second flow path length L2. Thereby, the difference in flow velocity between the first circumferential flow path 661 and the second circumferential flow path 662 can be suppressed.

[0382] It should be noted that inFigure 15B In the header part 11 of other embodiments shown, the number of returns is not limited to Figure 15B the example of

[0383] In Figure 15B In the header part 11 of other embodiments shown, a second partition wall W5 is formed between two adjacent radial flow paths 61 in the circumferential direction, which separates in the circumferential direction a plurality of circumferential flow paths 66 branched from one of the two radial flow paths 61 and a plurality of circumferential flow paths 66 branched from the other of the two radial flow paths 61.

[0384] Thereby, the circumferential range in which the circumferential flow paths 66 connected to one of the radial flow paths 61 are arranged and the circumferential range in which the circumferential flow paths 66 connected to the other radial flow path 61 are arranged can be defined by the second partition wall W5.

[0385] In the heat exchanger 1 of the heat exchange core 10 of several of the above-described embodiments in the modification including the radial flow path 61 and the circumferential flow path 66, the heat exchanger 1 can be made relatively small in size and the heat exchange efficiency can be improved.

[0386] (Regarding the manufacturing method of the heat exchange core)

[0387] Hereinafter, with reference to Figure 10 an example of the manufacturing method of the heat exchange core 10 of several of the above-described embodiments in the modification of the radial flow path 61 and the circumferential flow path 66 will be described.

[0388] In the modification of the radial flow path 61 and the circumferential flow path 66, the header part forming step S3 forms the header flow path 6 so as to include at least one radial flow path 61 extending in the radial direction and a plurality of circumferential flow paths 66 branched from any one of the radial flow paths 61 and respectively communicating with one or more axial flow paths 3.

[0389] In addition, in the modification of the radial flow path 61 and the circumferential flow path 66, the header part forming step S3 forms a plurality of circumferential flow paths 66 so as to include a first circumferential flow path 661 and a second circumferential flow path 662 located at a position radially inside the first circumferential flow path 661 and arranged in the circumferential direction within a total angle range θt larger than that of the first circumferential flow path 661.

[0390] Thereby, the heat exchange core 10 can be integrally formed by laminated molding, so that there is no need for assembly of components and sealing between components using gaskets. Therefore, the time and effort for adjustment can be significantly reduced.

[0391] The present disclosure is not limited to the above-described embodiments in the modified examples of the radial flow path 61 and the circumferential flow path 66, and also includes a mode in which the above-described embodiments in the modified examples of the radial flow path 61 and the circumferential flow path 66 are modified, and a mode in which these modes are appropriately combined.

[0392] The content described in each of the above embodiments can be understood as follows, for example.

[0393] (18) The heat exchange core 10 of at least one embodiment of the present disclosure includes a core main body portion 13 and a header portion 11. The core main body portion 13 includes a plurality of axial flow paths 3 extending along the axial direction. The header portion 11 is adjacent to at least one end in the axial direction of the core main body portion 13 and has a header flow path 6 communicating with the plurality of axial flow paths 3.

[0394] The header flow path 6 includes at least one radial flow path 61 extending along the radial direction. The header flow path 6 includes a plurality of circumferential flow paths 66 branched from any one of the radial flow paths 61 and respectively communicating with one or more axial flow paths 3.

[0395] The plurality of circumferential flow paths 66 include a first circumferential flow path 661. The plurality of circumferential flow paths 66 include a second circumferential flow path 662 located at a position radially inside the first circumferential flow path 661 and arranged circumferentially within a total angle range θt larger than that of the first circumferential flow path 661.

[0396] According to the structure of the above (18), by including at least one radial flow path 61 and a plurality of circumferential flow paths 66 branched from any one of the radial flow paths 61 and respectively communicating with one or more axial flow paths 3 in the header flow path 6, the header portion 11 can be made relatively small-sized.

[0397] It should be noted that if only at least one radial flow path 61 and a plurality of circumferential flow paths 66 branched from any one of the radial flow paths 61 and respectively communicating with one or more axial flow paths 3 are included in the header flow path 6, then even if the total angle range θt is the same, due to the different radial positions, among the first flow path length L1 of the first circumferential flow path 661 and the second flow path length L2 of the second circumferential flow path 662, the first flow path length L1 is longer. Therefore, if the flow path width (radial width) is the same, the pressure loss of the first circumferential flow path 661 is larger than that of the second circumferential flow path 662, and it is difficult for the first fluid to flow.

[0398] Regarding this point, in the heat exchange core 10 having the structure of the above (18), since the total angular range θt of the first circumferential flow path 661 is smaller than the total angular range θt of the second circumferential flow path 662, the difference between the first flow path length L1 and the second flow path length L2 can be suppressed as compared with the case where the total angular range θt is the same in the first circumferential flow path 661 and the second circumferential flow path 662. Thereby, it is possible to suppress the pressure loss of the first circumferential flow path 661 from being larger than the pressure loss of the second circumferential flow path 662, and the difference in the flow velocity between the first circumferential flow path 661 and the second circumferential flow path 662 can be suppressed. Therefore, by suppressing the difference in the flow rate of the first fluid in the axial flow path 3 connected to the first circumferential flow path 661 and the flow rate of the first fluid in the axial flow path 3 connected to the second circumferential flow path 662, the heat exchange efficiency in the heat exchange core 10 can be improved.

[0399] (19) In several embodiments, based on the structure of the above (18), at least one radial flow path 61 includes a first radial flow path 601 and a second radial flow path 602. The first radial flow path 601 communicates with the first circumferential flow path 661. The second radial flow path 602 is provided within the radial range occupied by the first radial flow path 601 and within a range radially inward of this radial range, and communicates with the second circumferential flow path 662. The second circumferential flow path 662 passes through the first radial flow path 601 in the circumferential direction and extends from the second radial flow path 602 to the opposite side across the first radial flow path 601.

[0400] According to the structure of the above (19), the shapes of the first circumferential flow path 661 and the second circumferential flow path 662 are not complicated, the total angular range θt of the second circumferential flow path 662 can be made larger than the total angular range θt of the first circumferential flow path 661, and the difference in the flow velocity between the first circumferential flow path 661 and the second circumferential flow path 662 can be suppressed.

[0401] (20) In several embodiments, based on the structure of the above (19), the first radial flow path 601 does not communicate with the second circumferential flow path 662, and the second radial flow path 602 does not communicate with the first circumferential flow path 661.

[0402] According to the structure of the above (20), when the first fluid flows from the first radial flow path 601 to the first circumferential flow path 661, all of the first fluid from the first radial flow path 601 can be supplied to the first circumferential flow path 661. Therefore, it is possible to suppress the shortage of the supply amount of the first fluid supplied to the first circumferential flow path 661 and suppress the reduction of the heat exchange efficiency.

[0403] Similarly, when the first fluid flows from the second radial flow path 602 to the second circumferential flow path 662, all of the fluid from the second radial flow path 602 can be supplied to the second circumferential flow path 662. Therefore, it is possible to suppress insufficient supply of the first fluid to the second circumferential flow path 662 and suppress a decrease in heat exchange efficiency.

[0404] In addition, when the first fluid flows from the first circumferential flow path 661 to the first radial flow path 601, the first fluid from the second circumferential flow path 662 does not flow into the first radial flow path 601. Therefore, it is possible to prevent an increase in the flow rate of the first fluid flowing in the first radial flow path 601 due to the first fluid from the second circumferential flow path 662. As a result, it is possible to suppress an increase in pressure loss in the first radial flow path 601 and suppress a decrease in the flow rate in the first circumferential flow path 661, thereby suppressing a decrease in heat exchange efficiency.

[0405] Similarly, when the first fluid flows from the second circumferential flow path 662 to the second radial flow path 602, the first fluid from the first circumferential flow path 661 does not flow into the second radial flow path 602. Therefore, it is possible to prevent an increase in the flow rate of the first fluid flowing in the second radial flow path 602 due to the fluid from the first circumferential flow path 661. As a result, it is possible to suppress an increase in pressure loss in the second radial flow path 602 and suppress a decrease in the flow rate in the second circumferential flow path 662, thereby suppressing a decrease in heat exchange efficiency.

[0406] (21) In several embodiments, based on the structure of (19) or (20) above, one or more first radial flow paths 601 are arranged. A plurality of second radial flow paths 602 are arranged circumferentially. The number of the first radial flow paths 601 is larger than the number of the second radial flow paths 602.

[0407] According to the structure of (21) above, compared with the case where the number of the first radial flow paths 601 is smaller than the number of the second radial flow paths 602, it is possible to reduce the distance separating two adjacent first radial flow paths 601 in the circumferential direction. Therefore, it is possible to suppress the first flow path length L1 of the first circumferential flow path 661. As a result, it is possible to suppress the difference between the first flow path length L1 of the first circumferential flow path 661 and the second flow path length L2 of the second circumferential flow path 662, thereby suppressing the pressure loss difference between the second circumferential flow path 662 and the first circumferential flow path 661, and thus suppressing the flow velocity difference between the first circumferential flow path 661 and the second circumferential flow path 662.

[0408] (22) In several embodiments, based on any of the structures of (19) to (21) above, two or more first radial flow paths 601 are arranged at equal intervals in the circumferential direction. Two or more second radial flow paths 602 are arranged at equal intervals in the circumferential direction.

[0409] According to the structure of (22) above, compared with the case where the first radial flow paths 601 are arranged at unequal intervals, it is possible to suppress the difference in the length of the flow paths of the circumferential flow path 66 due to the connected first radial flow paths 601, and it is possible to suppress the deviation of the flow rate in each flow path in the circumferential flow path 66. Similarly, compared with the case where the second radial flow paths 602 are arranged at unequal intervals, it is possible to suppress the difference in the length of the flow paths of the circumferential flow path 66 due to the connected second radial flow paths 602, and it is possible to suppress the deviation of the flow rate in each flow path in the circumferential flow path 66. Thereby, it is possible to suppress the reduction of the heat exchange efficiency.

[0410] In addition, by arranging them at equal intervals, it is possible to efficiently arrange the radial flow paths 61 and suppress the number of the radial flow paths 61. Thereby, it is possible to suppress the increase in the ratio of the area occupied by the radial flow paths 61 in the cross section (second cross section C2) of the header portion 11 when viewed from the axial direction and increase the ratio of the area occupied by the circumferential flow path 66.

[0411] (23) In several embodiments, based on the structure of (18) above, the first circumferential flow path 661 and the second circumferential flow path 662 communicate with the same radial flow path 61. The number of turns of the second circumferential flow path 662 is larger than the number of turns of the first circumferential flow path 661.

[0412] According to the structure of (23) above, compared with the case where the first circumferential flow path 661 and the second circumferential flow path 662 are connected to different radial flow paths 61, it is possible to suppress the number of the radial flow paths 61. Thereby, it is possible to suppress the increase in the ratio of the area occupied by the radial flow paths 61 in the cross section (second cross section C2) of the header portion 11 when viewed from the axial direction and increase the ratio of the area occupied by the circumferential flow path 66.

[0413] In addition, by making the number of turns of the second circumferential flow path 662 larger than the number of turns of the first circumferential flow path 661, it is possible to increase the total angular range θt in the second circumferential flow path 662 and ensure the second flow path length L2. Thereby, it is possible to suppress the difference in the flow velocity between the first circumferential flow path 661 and the second circumferential flow path 662.

[0414] (24) In several embodiments, based on the structure of (23) above, two or more radial flow paths 61 are provided separately in the circumferential direction. Between two adjacent radial flow paths 61 in the circumferential direction, a second partition wall W5 is formed, which separates the plurality of circumferential flow paths 66 branched from one of the two radial flow paths 61 and the plurality of circumferential flow paths 66 branched from the other of the two radial flow paths 61 in the circumferential direction.

[0415] According to the structure of the above (24), the circumferential range where the circumferential flow path 66 connected to the radial flow path 61 on one supply side is arranged and the circumferential range where the circumferential flow path 66 connected to the radial flow path 61 on the other supply side is arranged can be defined by the second partition wall W5.

[0416] (25) In several embodiments, based on the structure of the above (23) or (24), a plurality of radial flow paths 61 are arranged at equal intervals in the circumferential direction.

[0417] According to the structure of the above (25), compared with the case where the radial flow paths 61 are arranged at unequal intervals, the difference in the flow path length Lc of the circumferential flow path 66 caused by the connected radial flow paths 61 can be suppressed, and the deviation of the flow rate in each flow path in the circumferential flow path 66 can be suppressed.

[0418] In addition, by arranging at equal intervals, the radial flow paths 61 can be arranged efficiently, and the number of radial flow paths 61 can be suppressed. As a result, the proportion of the area occupied by the radial flow paths 61 in the cross section (second cross section C2) of the header portion 11 when viewed from the axial direction can be suppressed, and the proportion of the area occupied by the circumferential flow paths 66 can be increased.

[0419] (26) In several embodiments, based on any one of the structures of the above (18) to (25), the radial flow path 61 is connected to the circumferential flow paths 66 located on one side and the other side in the circumferential direction with respect to the radial flow path 61, respectively.

[0420] According to the structure of the above (26), compared with the case where the radial flow path 61 is only connected to the circumferential flow path 66 on either one side in the circumferential direction with respect to the radial flow path 61, the number of radial flow paths 61 can be suppressed. As a result, the proportion of the area occupied by the radial flow paths 61 in the cross section of the header portion 11 when viewed from the axial direction can be suppressed, and the proportion of the area occupied by the circumferential flow paths 66 can be increased.

[0421] (27) In several embodiments, based on any one of the structures of the above (18) to (26), a plurality of axial flow paths 3 are arranged in an annular shape when viewed from the axial direction.

[0422] According to the structure of the above (27), the stress acting due to the pressure of the fluid or the like can be evenly dispersed throughout the heat exchange core 10.

[0423] (28) In several embodiments, based on any one of the structures of the above (18) to (27), at least one of the radial flow paths 61 is two or more radial flow paths 61. The two or more radial flow paths 61 are each given an equal flow path cross-sectional area.

[0424] According to the structure of the above (28), compared with the case where different flow path cross-sectional areas are given to two or more radial flow paths 61, the difference in the flow rates of the fluid in two or more radial flow paths 61 can be suppressed, and thus the reduction in the heat exchange efficiency can be suppressed.

[0425] (29) In several embodiments, based on any of the structures in the above (18) to (28), the plurality of axial flow paths 3 are each divided into a plurality of partitions S in the circumferential direction.

[0426] According to the structure of the above (29), by the presence of the wall that divides the axial flow path 3 into partitions, the heat transfer efficiency can be improved. Through this wall, the rigidity and strength of the heat exchange core 10, particularly in the radial direction, can be improved.

[0427] (30) In several embodiments, based on the structure of the above (29), the plurality of axial flow paths 3 equalize the flow path diameters of the plurality of partitions S.

[0428] According to the structure of the above (30), by equalizing the flow states such as frictional loss in all partitions, the heat transfer rates of all partitions can be equalized, and by uniformly dispersing the stress in the entire in-plane direction of the cross-section of the heat exchange core 10, the stress can be equalized.

[0429] (31) The heat exchanger 1 according to at least one embodiment of the present disclosure includes a heat exchange core 10 having any of the structures in the above (18) to (30) and a housing 20 that houses the heat exchange core 10.

[0430] According to the structure of the above (31), the heat exchanger 1 can be made relatively small in size, and the heat exchange efficiency can be improved.

[0431] (32) The manufacturing method of the heat exchange core according to at least one embodiment of the present disclosure is a manufacturing method of the heat exchange core 10, including: a core main body portion forming step S1 of forming a core main body portion 13 including a plurality of axial flow paths 3 extending along the axial direction by additive manufacturing; and a header portion forming step S3 of forming a header portion 11 adjacent to at least one end in the axial direction of the core main body portion 13 and having a header flow path 6 communicating with the plurality of axial flow paths 3 by additive manufacturing.

[0432] The header portion forming step S3 forms the header flow path 6 in such a manner as to include at least one radial flow path 61 extending in the radial direction and a plurality of circumferential flow paths 66 branched from any one of the radial flow paths 61 and respectively communicating with one or more axial flow paths 3. The header portion forming step S3 forms the plurality of circumferential flow paths 66 in such a manner as to include a first circumferential flow path 661 and a second circumferential flow path 662 located at a position radially inside the first circumferential flow path 661 and circumferentially arranged within a total angle range θt larger than the first circumferential flow path 661.

[0433] According to the method of (32) above, the heat exchange core 10 can be integrally formed by stacked molding, so there is no need for component assembly or sealing between components using gaskets. Therefore, the adjustment work can be significantly reduced.

[0434] Description of Reference Numerals

[0435] 1 Heat exchanger

[0436] 3 Axial flow path

[0437] 6 Header flow path

[0438] 10 Heat exchange core

[0439] 11 Header section

[0440] 11A First header section (header section)

[0441] 11B Second header section (header section)

[0442] 13 Core main body section

[0443] 20 Outer shell

[0444] 61 Radial flow path

[0445] 63 Opening

[0446] 66 Circumferential flow path

[0447] 101 First flow path

[0448] 102 Second flow path

[0449] 601 First radial flow path

[0450] 602 Second radial flow path

[0451] 661 First circumferential flow path

[0452] 662 Second circumferential flow path

[0453] W0 Side wall

[0454] W3 Transverse wall

[0455] W5 Partition wall (second partition wall).

Claims

1. A heat exchange core, wherein, the heat exchange core comprises: a core main body portion including a plurality of axial flow paths extending along an axial direction; and a header portion adjacent to at least one end of the core main body portion in the axial direction and having a header flow path communicating with the plurality of axial flow paths, the header flow path includes: at least one radial flow path extending in a radial direction; and a plurality of circumferential flow paths branching from each of the radial flow paths and respectively communicating with one or more of the axial flow paths, in each of the radial flow paths, the flow path area at a second position closer to the inner side in the radial direction than a first position is smaller than the flow path area at the first position, at least one opening formed by the at least one radial flow path is formed on an outer peripheral surface of the heat exchange core at the header portion, the total area of the opening areas of each of the openings is equal to or less than the total area of the areas of the plurality of circumferential flow paths when viewed from the axial direction.

2. A heat exchange core, wherein, the heat exchange core comprises: a core main body portion including a plurality of axial flow paths extending along an axial direction; and a header portion adjacent to at least one end of the core main body portion in the axial direction and having a header flow path communicating with the plurality of axial flow paths, the header flow path includes: at least one radial flow path extending in a radial direction; and a plurality of circumferential flow paths branching from each of the radial flow paths and respectively communicating with one or more of the axial flow paths, in each of the radial flow paths, the flow path area at a second position closer to the inner side in the radial direction than a first position is smaller than the flow path area at the first position, the at least one radial flow path is formed such that at at least one end of the two ends along the axial direction, the circumferential dimension becomes smaller as it extends toward the outer side of the radial flow path along the axial direction.

3. The heat exchange core according to claim 1 or 2, wherein, in each of the radial flow paths, the circumferential dimension at the second position is smaller than the circumferential dimension at the first position.

4. The heat exchange core according to claim 1 or 2, wherein, in each of the radial flow paths, the axial dimension at the second position is smaller than the axial dimension at the first position.

5. The heat exchange core according to claim 1 or 2, wherein, the flow path area gradually decreases toward the inner side in the radial direction.

6. The heat exchange core according to claim 1 or 2, wherein, at least one opening formed by the at least one radial flow path is formed on an outer peripheral surface of the heat exchange core at the header portion, the opening dimension of each of the openings along the axial direction is 1 time or more the opening dimension of each of the openings along the circumferential direction.

7. The heat exchange core according to claim 1 or 2, wherein, the header portion includes a first header portion adjacent to one end of the core main body portion in the axial direction and a second header portion adjacent to the other end of the core main body portion in the axial direction, Regarding the area increase rate of the flow path area that increases from the inner side to the outer side in the at least one radial flow path, it is different between the at least one radial flow path in the first header portion and the at least one radial flow path in the second header portion.

8. A heat exchange core, wherein, the heat exchange core includes: a core body portion including a plurality of axial flow paths extending along the axial direction; and a header portion adjacent to at least one end of the core body portion in the axial direction and having a header flow path communicating with the plurality of axial flow paths, the header flow path includes: at least one radial flow path extending in the radial direction; and a plurality of circumferential flow paths branching from any one of the radial flow paths and respectively communicating with one or more of the axial flow paths, the plurality of circumferential flow paths include: a first circumferential flow path; and a second circumferential flow path located radially inward of the first circumferential flow path and arranged circumferentially within a total angle range larger than that of the first circumferential flow path, the total angle range is the cumulative value of the change in angle centered on the central position in the radial direction from one end to the other end of one of the circumferential flow paths.

9. The heat exchange core according to claim 8, wherein, the at least one radial flow path includes: a first radial flow path communicating with the first circumferential flow path; and a second radial flow path provided within the radial range occupied by the first radial flow path and within a range radially inward of this radial range and communicating with the second circumferential flow path, the second circumferential flow path passes through the first radial flow path in the circumferential direction and extends to the opposite side across the first radial flow path from the second radial flow path.

10. The heat exchange core according to claim 9, wherein, the first radial flow path is not connected to the second circumferential flow path, the second radial flow path is not connected to the first circumferential flow path.

11. The heat exchange core according to claim 9, wherein, one or more first radial flow paths are arranged, a plurality of second radial flow paths are arranged along the circumferential direction, the number of the first radial flow paths is larger than the number of the second radial flow paths.

12. The heat exchange core according to claim 9, wherein, two or more first radial flow paths are arranged at equal intervals along the circumferential direction, two or more second radial flow paths are arranged at equal intervals along the circumferential direction.

13. The heat exchange core according to claim 8, wherein, the first circumferential flow path and the second circumferential flow path communicate with the same radial flow path, the number of turns back of the second circumferential flow path is larger than the number of turns back of the first circumferential flow path.

14. The heat exchange core according to claim 13, wherein, two or more radial flow paths are separately arranged in the circumferential direction, a partition wall is formed between two adjacent radial flow paths in the circumferential direction to separate, in the circumferential direction, the plurality of circumferential flow paths branching from one of the two radial flow paths and the plurality of circumferential flow paths branching from the other of the two radial flow paths.

15. The heat exchange core according to claim 13, wherein, A plurality of the radial flow paths are arranged at equal intervals along the circumferential direction.

16. The heat exchange core according to any one of claims 8 to 15, wherein the radial flow path is connected to the circumferential flow paths respectively located on one side and the other side of the circumferential direction with respect to the radial flow path.

17. The heat exchange core according to any one of claims 1 to 2, 8 to 15, wherein at least one opening formed by the at least one radial flow path is formed on the outer peripheral surface of the heat exchange core at the header portion, the opening dimension along the axial direction of each of the openings is 1 time or more the opening dimension along the circumferential direction of each of the openings.

18. The heat exchange core according to claim 17, wherein the total area of the opening areas of each of the openings is equal to or less than the total area of the areas of the plurality of circumferential flow paths when viewed from the axial direction.

19. A heat exchanger, wherein the heat exchanger includes: the heat exchange core according to any one of claims 1 to 18; and a housing that houses the heat exchange core.

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