JP2021134984A - Heat exchange core, heat exchanger, and method of manufacturing heat exchange core - Google Patents

Abstract

To provide a heat exchange core which can securely have relatively high heat exchange efficiency while the size thereof is reduced.SOLUTION: In a header part of a heat exchange core, a header flow channel includes at least one radial flow channel extending along a radial direction, and a plurality of circumferential flow channels communicating with one or more respective axial flow channels diverging from any one of the radial flow channels. The plurality of circumferential flow channels includes a first circumferential flow channel, and a second circumferential flow channels placed inside the first circumferential flow channel in the radial direction, and arranged in a circumferential direction over a total angle range larger than that of the first circumferential flow channel.SELECTED DRAWING: Figure 1

Description

The present disclosure relates to heat exchange cores, heat exchangers and methods for manufacturing heat exchange cores.

For example, a cylindrical heat exchanger in which a group of flow paths is formed inside a cylindrical casing is known. Generally, in a cylindrical heat exchanger, in order to exchange heat between the first fluid and the second fluid, either the first fluid or the second fluid is transferred to the axial end of the cylindrical casing. It is configured to flow in and out from the portion and allow the other fluid to flow in and out along the radial direction from the side portion of the casing (see, for example, Patent Document 1).

Special Table 2018-591490

In the cylindrical heat exchanger as described above, the flow of the fluid flowing into the casing along the radial direction is deflected in the axial direction, and the flow of the fluid flowing in the casing along the axial direction is redirected in the radial direction. ing. Therefore, the flow rate of the fluid flowing in the casing may differ depending on the position in the circumferential direction or the radial direction, and the heat exchange efficiency may decrease due to such a difference in the flow rate. In order to suppress such a difference in flow rate, it is desirable to secure a certain amount of space for turning the direction of the fluid flow. Therefore, it is difficult to miniaturize the cylindrical heat exchanger while ensuring a relatively high heat exchange efficiency.

At least one embodiment of the present disclosure aims to provide a heat exchange core that can be miniaturized while ensuring a relatively high heat exchange efficiency in view of the above circumstances.

(1) The heat exchange core according to at least one embodiment of the present disclosure is
A core body including a plurality of axial flow paths extending along the axial direction,
A header portion having a header flow path adjacent to at least one end of the core main body portion in the axial direction and communicating with the plurality of axial flow paths is provided.
The header flow path is
At least one radial flow path extending along the radial direction,
A plurality of circumferential flow paths that branch from any of the radial flow paths and communicate with one or more of the axial flow paths, respectively.
Including
The plurality of circumferential flow paths are
1st circumferential flow path and
A second circumferential flow path located radially inside the first circumferential flow path and arranged in the circumferential direction over a total angular range larger than the first circumferential flow path.
including.

(2) The heat exchanger according to at least one embodiment of the present disclosure is
With the heat exchange core of the above (1) configuration,
A casing accommodating the heat exchange core and
To be equipped.

(3) The method for manufacturing a heat exchange core according to at least one embodiment of the present disclosure is described.
It is a method of manufacturing a heat exchange core.
A step of forming a core main body including a plurality of axial flow paths extending along the axial direction by laminating molding, and
A step of forming a header portion having a header flow path that is adjacent to at least one end of the core main body portion in the axial direction and communicates with the plurality of axial flow paths by laminating molding is provided.
The step of forming the header portion is
At least one radial flow path extending along the radial direction,
A plurality of circumferential flow paths that branch from any of the radial flow paths and communicate with one or more of the axial flow paths, respectively.
The header flow path is formed so as to include
The step of forming the header portion is
1st circumferential flow path and
A second circumferential flow path located radially inside the first circumferential flow path and arranged in the circumferential direction over a total angular range larger than the first circumferential flow path.
The plurality of circumferential flow paths are formed so as to include.

According to at least one embodiment of the present disclosure, the heat exchange core can be miniaturized while ensuring a relatively high heat exchange efficiency.

It is an exploded perspective view which shows the heat exchange core and the casing provided in the heat exchanger which concerns on some embodiments. It is a partial cross-sectional view which shows the casing of the heat exchanger shown in FIG. 1 and the heat exchange core housed in the casing. FIG. 2 is a cross-sectional view taken along the line IIIa-IIIa of FIG. 2 (first cross section of the heat exchange core), showing a first flow path group and a second flow path group. It is a partially enlarged view of FIG. 3A. Other than this figure, the illustration of the dividing wall (W2) is omitted. FIG. 2 is a sectional view taken along line IV-IV of FIG. (Second cross section of heat exchange core) 2 is a sectional view taken along line VV of FIGS. 2 and 6. (Third cross section of heat exchange core) It is a schematic diagram which shows the flow of each of the 1st fluid and the 2nd fluid. It is sectional drawing which shows a part of the heat exchange core which concerns on the modification of this disclosure. It is a schematic diagram for demonstrating the radial flow path and the circumferential flow path which concerns on one Embodiment. It is a schematic diagram for demonstrating the radial flow path and the circumferential flow path which concerns on other embodiment. It is a schematic diagram for demonstrating the total angle range. It is a flowchart which showed the processing procedure in the manufacturing method of the heat exchange core which concerns on some Embodiments.

Hereinafter, some embodiments of the present disclosure will be described with reference to the accompanying 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 to this, and are merely explanatory examples. No.
For example, expressions that represent relative or absolute arrangements such as "in a certain direction", "along a certain direction", "parallel", "orthogonal", "center", "concentric" or "coaxial" are exact. Not only does it represent such an arrangement, but it also represents a state of relative displacement with tolerances or angles and distances to the extent that the same function can be obtained.
For example, expressions such as "same", "equal", and "homogeneous" that indicate that things are in the same state not only represent exactly the same state, but also have tolerances or differences to the extent that the same function can be obtained. It shall also represent the existing state.
For example, an expression representing a shape such as a quadrangular shape or a cylindrical shape not only represents a shape such as a quadrangular shape or a cylindrical shape in a geometrically strict sense, but also an uneven portion or chamfering within a range in which the same effect can be obtained. The shape including the part and the like shall also be represented.
On the other hand, the expressions "equipped", "equipped", "equipped", "included", or "have" one component are not exclusive expressions that exclude the existence of other components.

(Outline configuration of heat exchanger)
As shown in FIGS. 1 and 2, the heat exchanger 1 according to some embodiments includes a heat exchange core 10 and a casing 20 that houses the heat exchange core 10.
The heat exchanger 1 according to some embodiments _{can be incorporated into, for example, a chemical plant such as a gas turbine or a CO 2} recovery device, or a device (not shown) such as an air conditioner or a freezer, for example, a first fluid and a first fluid. 2 Heat exchange with the fluid. For example, the temperature of the first fluid is relatively high, and the temperature of the second fluid is relatively low. On the contrary, the temperature of the first fluid may be relatively low and the temperature of the second fluid may be relatively high.

(Structure of heat exchange core)
The heat exchange core 10 according to some embodiments includes a core body portion 13 and header portions 11A and 11B adjacent to one and the other end portions of the core body portion 13 in the axial direction. For convenience of explanation, the header portion 11A adjacent to one end of the core body 13 in the axial direction 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 referred to as the second header portion. Also referred to as 11B.

FIG. 3 is a cross-sectional view taken along the line IIIa-IIIa of FIG. As will be described later, the core main body 13 according to some embodiments is a part of a plurality of first flow paths 101 which are a plurality of axial flow paths 3 extending along the axial direction, and a plurality of a plurality of first flow paths 101. The second flow path 102 is included.
Each of the header portions 11A and 11B according to some embodiments has a header flow path 6 communicating with a plurality of axial flow paths 3 (see FIG. 6), as will be described in detail later.

As shown in FIGS. 1 and 3A, the heat exchange core 10 according to some embodiments includes a first flow path group G1 and a second flow path group G2 arranged concentrically as a whole.
The heat exchanger 1 according to some embodiments includes a first cross section C1 shown in FIG. 3A, a second cross section C2 shown in FIG. 4, and a third cross section C3 shown in FIG. All of these cross sections C1 to C3 have a circular shape. The overall outer shape of the heat exchange core 10 is formed in a columnar shape. The heat exchange core 10 is a partition wall (first partition wall) W1 arranged concentrically to separate 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. And include.

The heat exchange core 10 is given a shape symmetrical with respect to the center of the cross sections C1 to C3, that is, the central axis (axis line AX) of the heat exchange core 10 having a cylindrical shape, as a whole, not only the outer shape. This makes it possible to contribute to the homogenization of heat exchange efficiency in addition to the homogenization of stress.

In the heat exchanger 1 according to some 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, a shaded pattern is attached to the first flow path group G1.
The second flow path group G2 according to some embodiments extends from one end 10A (FIG. 1) to the other end 10B (FIG. 1) of the heat exchange core 10 in the axial direction D1. The axial direction D1 is orthogonal to the cross sections C1 to C3. That is, in some embodiments, the plurality of second flow paths 102 are included in the axial flow path 3.
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 broken line arrow.

In some embodiments, the first flow paths 101 constituting the first flow path group G1 are arranged in an annular shape in the first cross section C1 shown in FIG. 3A. The same applies to the second flow path 102 constituting the second flow path group G1. In some embodiments, the first fluid flowing through the first flow path group G1 and the second fluid flowing through the second flow path group G2 indirectly pass through the first partition wall W1 shown by the thick line in FIG. 3A. Transfers heat by contact.

As shown in FIG. 3A, it is preferable that the plurality of first flow paths 101 and the plurality of second flow paths 102 are alternately laminated in the radial direction of the heat exchange core 10, for example, over several tens of layers. ..
It is preferable that the first flow path 101 and the second flow path 102 are arranged over the entire radial direction of the heat exchange core 10, that is, near the axis of the heat exchange core 10, that is, near the axis AX. In FIGS. 3A, 3B, 4 and 5, only a part of the first flow path 101 and a part of the second flow path 102 are shown. The remaining first flow path 101 and second flow path 102 in the region indicated by “...” are not shown.
By arranging the first flow path 101 and the second flow path 102 over the entire radial direction of the heat exchange core 10 as in the present embodiment, the entire heat exchange core 10 can contribute to heat exchange. can.

In some embodiments, the heat exchange core 10 spans a range between the IV-IV and IVx-IVx lines shown in FIG. 2 and has a constant cross-sectional shape corresponding to the first cross section C1 (FIG. 3A). May be. In this range, that is, from the vicinity of one end 10A of the heat exchange core 10 to the vicinity of the other end 10B, in the present embodiment, the first fluid and the second fluid are respectively along the axial direction D1. It flows in the opposite direction. That is, the first fluid and the second fluid form a countercurrent (completely countercurrent) over substantially the entire axial direction D1 of the heat exchange core 10 except for both ends.
The first fluid and the second fluid may flow in the same direction along the axial direction D1. In that case, the first fluid and the second fluid form parallel flows.

In the heat exchange core 10 according to some embodiments, the appropriate dimensions in the axial direction D1 and the radial direction, the cross-sectional area of the flow path, and the number of layers of the flow paths 101 and 102 are taken into consideration in consideration of the required heat exchange capacity and stress. Etc. are given.

As shown in FIG. 3B, it is preferable that each of the first flow paths 101 and each second flow path 102 is divided into a plurality of sections S by the division wall W2 in the circumferential direction D2 of the heat exchange core 10. According to the installation of the partition wall W2, it is possible to improve the rigidity and strength particularly in the radial direction with respect to the pressure of the fluid.
Further, since the first flow path 101 and the second flow path 102 are each subdivided into compartments S by the partition wall W2, the surface area of the flow path in contact with the fluid is increased, so that the heat transfer efficiency can be improved. can.

It is preferable that the compartments S have the same flow path diameter and are arranged over the entire circumference of the heat exchange core 10. Further, it is preferable that the same flow path diameter is given to all the compartments S extending from the outermost circumference to the axial center of the heat exchange core 10. Then, as a result of the flow state such as friction loss being made uniform in all the compartments S, the heat transfer coefficient can be made uniform in all the compartments S, and the stress acting on the heat exchange core 10 is applied to the heat exchange core 10. The stress can be made uniform by uniformly dispersing the cross section in the in-plane direction.

The "flow path diameter" in the present specification corresponds to the equivalent diameter D given by the following equation (1).
D = 4A / L ... (1)
A: Cross-sectional area of compartment S
L: Length of section S in circumferential direction D2 (perimeter)
Since the heat transfer coefficient corresponds to the reciprocal of the flow path diameter, it is preferable to give an appropriate flow path diameter to the compartment S based on this.

The heat exchange core 10 according to some embodiments is integrally formed of a metal material such as stainless steel or an aluminum alloy, which has characteristics suitable for a fluid, by laminating molding or the like, including the partition wall W2. Can be molded. According to laminated molding, for example, supply of metal powder to a molding region in an apparatus, irradiation of a laser beam or electron beam based on two-dimensional data showing a cross section of a three-dimensional shape, melting of metal powder, and metal powder. By repeating the solidification of the above, it is possible to obtain a molded product in which two-dimensional shapes are laminated.
In some embodiments, the thickness of the wall W1 or the like in the heat exchange core 10 obtained by laminating molding using a metal material is, for example, 0.3 to 3 mm.
The heat exchange core 10 according to some embodiments is manufactured by performing a step of forming a first flow path group G1 and a second flow path group G2 by laminated molding using a metal material. If necessary, the molded product obtained by the molding step by the laminated molding can be polished or the like. The method for manufacturing the heat exchange core 10 according to some embodiments will be described in detail later.
The heat exchange core 10 according to some embodiments is not limited to laminated molding, and can be integrally molded by cutting or the like.

The heat exchange core 10 according to some embodiments may be formed by combining a plurality of first partition walls W1 formed by bending a metal plate material, but is preferably integrally formed. When the heat exchange core 10 is integrally formed, the heat exchange core 10 does not need a gasket for preventing fluid from leaking between the members.
When a gasket is used, it is necessary to give an appropriate amount of elastic deformation to the gasket in order to reliably seal between the members. Then, in order to prevent fluid leakage, it is necessary to perform maintenance such as disassembling the members of the heat exchange core and re-tightening the gaskets between the members. Gasket tolerances and assembly tolerances, changes in the amount of deformation due to changes in fluid pressure and changes over time of the gaskets, damage to the gaskets due to thermal stress, etc. may occur, so maintenance is particularly necessary for gaskets.
On the other hand, according to the integrally molded heat exchange core 10 according to some embodiments, since the gasket is not provided, the labor for maintenance can be significantly reduced.

(Casing and header)
As shown in FIGS. 1 and 2, the casing 20 according to some embodiments is formed in a substantially cylindrical shape as a whole. The casing 20 is formed of, for example, stainless steel, an aluminum alloy, or the like, which has properties suitable for a fluid.
The casing 20 according to some embodiments has an inner diameter corresponding to the outer diameter of the heat exchange core 10, and the diameter is expanded with respect to the casing main body 21 having a circular cross section and the casing main body 21. It is provided with a large diameter portion 22. The large diameter portions 22 are provided at both ends of the casing main body 21 in the axial direction D1. These large diameter portions 22 function as the first inlet header 221 and the first outlet header 222.
Each of these headers 221 and 222 has an annular internal space 221A and 222A (FIG. 2) as a communication space around the side wall W0 of the heat exchange core 10.

In some embodiments, the first inlet header 221 is provided with an inlet port 22A into which the first fluid flows in from the outside. In some embodiments, the first outlet header 222 is provided with an outlet port 22B through which the first fluid flows out.
In some embodiments, the inlet ports 22A are not limited to one location, and may be provided at a plurality of locations in the circumferential direction D2. For example, the two inlet ports 22A may be arranged point-symmetrically with respect to the center of the second cross section C2. The same applies to the exit port 22B.

In some embodiments, the internal spaces 221A and 222A of the headers 221 and 222 have a sufficient flow path cross-sectional area in the direction intersecting the circumferential direction D2, so that the internal spaces 221A, The resistance of the first fluid in 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 path 61 evenly from the first inlet header 221 and flows out to the first outlet header 222 through the radial flow path 61. Variations in the flow rate for each road 61 are suppressed.

In some embodiments, a second inlet header 31 is provided at one end 10A of the casing 20 in the axial direction D1. A second outlet header 32 is provided at the other end 10B of the casing 20 in the axial direction D1.
In some embodiments, the flange 31A of the second inlet header 31 and the flange 231 of the casing 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 casing 20.

In some embodiments, the first flow path group G1 is connected to the inside of the first inlet header 221 and the inside of the first exit header 222.
In some embodiments, the second flow path group G2 is connected to the inside of the second inlet header 31 and the inside of the second exit header 32. Each start end of the second flow path 102 is open inside the second inlet header 31. Each end of the second flow path 102 is open inside the second exit header 32.

The directions in which the first fluid and the second fluid flow into and out of the heat exchange core 10, respectively, are appropriately determined in consideration of the routing of the inflow and outflow routes, the interference of the headers of the first fluid and the second fluid, and the like. Can be specified in.
For example, contrary to the above description, the first fluid may be circulated in the second flow path group G2, and the second fluid may be circulated in the first flow path group G2.

(Definition of approximately circular shape, approximately annular shape, approximately concentric circle)
In some embodiments, the cross section of the casing 20 does not necessarily have to be strictly circular, and may be "substantially circular" which can be regarded as substantially circular. Note that the "circular shape" allows tolerances for a perfect circle.
The "substantially circular shape" includes, for example, a polygonal shape having many vertices (for example, 10 to 20 icosagons), a shape having n rotational symmetry, and for example, a shape in which n is 10 to 20. In addition, a shape in which an arc is continuous over substantially the entire circumference direction D2 and unevenness is present in a part of the circumference is also included in the "substantially circular shape".

Similar to the above, the cross sections C1 to C3 of the heat exchange core 10 according to some embodiments do not have to be strictly circular, and may be "substantially circular". In that case, in the first cross section C1, it is sufficient that the first flow path 101 and the second flow path 102 are formed in a "substantially annular shape" that can be regarded as a substantially circular ring, and similarly, the first flow path group G1. It is sufficient that the second flow path group G2 is arranged substantially concentrically, which can be regarded as substantially concentric. "Approximately circular ring" shall be based on the meaning of the substantially circular shape described above.

By the way, in order to increase the heat transfer area, as shown in FIG. 7, a plurality of protrusions 103 rising from the first partition wall W1 toward at least one of the first flow path 101 and the second flow path 102 on the first partition wall W1. May be provided. The protrusion 103 suppresses pressure loss from the radial flow path 61 to the first flow path 101, which will be described later, to allow the first fluid to flow smoothly, and also from the first flow path 101 to the radial flow path 61. From the viewpoint of smooth outflow, it is preferable to provide the first flow path 101 on the first partition wall W1 while avoiding both ends in the axial direction D1.
The heat exchange core 10 provided with the protrusions 103 can be integrally formed by a laminating molding process.

For "concentric circles" in which a plurality of circular shapes having different diameters are arranged concentrically, a tolerance is allowed for the coincidence (concentricity) of the centers of each circle. That is, the "substantially concentric circle" includes a form in which circular shapes are arranged substantially concentrically. Each circular element that constitutes a concentric circle shall conform to the meaning of the substantially circular shape described above. The centers of the plurality of polygonal shapes can be matched, or the centers of the polygonal shape and the rotationally symmetric shape can be matched, and the polygonal shapes can be arranged in a "substantially concentric circle".

The cross section of the casing 20 and the heat exchange core 10 is circular, the cross section of the first flow path 101 and the second flow path 102 is annular, and the first flow path group G1 and the second flow flow are circular. When the road groups G2 are arranged concentrically, it is most preferable from the viewpoint of stress, heat transfer area, and uniform flow state.
However, the cross section of the casing 20 and the heat exchange core 10 may be substantially circular, or the first flow path 101 and the second flow path 102 may be substantially circular in the first cross section C1, or the first flow path group. Even when the G1 and the second flow path group G2 are arranged substantially concentrically as a whole, the same effect as the effect described later according to the present embodiment can be obtained.

(Explanation of the second cross section)
Hereinafter, the outlines of the radial flow path 61 and the circumferential flow path 66 appearing in the second cross-section C2 and the second cross-section C2 according to some embodiments will be described. The details of the radial flow path 61 and the circumferential flow path 66 according to some embodiments will be described separately.
As shown in FIG. 4 corresponding to the IV-IV line cross section of FIG. 2, the heat exchange core 10 crosses the first flow path group G1 and the second flow path group G2, and has only the first flow path group G1. A communicating radial flow path 61 is formed. The radial flow path 61 extends in the radial direction of the heat exchange core 10 in the second cross section C2 shown in FIG. 4, and communicates with the internal space 221A of the first inlet header 221 as shown in FIG. As shown in FIGS. 1 and 2, the radial flow path 61 penetrates the side wall W0 in the thickness direction.

In some embodiments, the plurality of first flow paths 101 extend axially within the heat exchange core 10 and communicate with the radial flow paths 61 on one side and the other side in the axial direction. In some embodiments, it is assumed that the axial flow path 3 includes the first flow path 101 arranged in the core main body 13 among the plurality of first flow paths 101. Further, in some embodiments, as will be described later, among the plurality of first flow paths 101, the first flow path 101 arranged in the header portions 11A and 11B is also referred to as a circumferential flow path 66. In some embodiments, the circumferential flow paths 66 are arranged in layers alternately with the second flow path 102 along the radial direction. The details of the circumferential flow path 66 according to some embodiments will be described separately.

The IVx-IVx line cross-sectional view of FIG. 2 is omitted, but is the same as that of FIG. The cross section corresponding to the IVx-IVx line in FIG. 2 also corresponds to the second cross section C2. The cross section corresponding to the IVx-IVx line is referred to as a 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.

In some embodiments, at least one radial flow path 61 is provided in each of the second cross section C2 and the second cross section C2x. In each of the second cross section C2 and the second cross section C2x, it is preferable that a plurality of (for example, eight in the embodiment shown in FIG. 4) radial flow paths 61 are distributed in the circumferential direction D2. Since the plurality of radial flow paths 61 are distributed in the circumferential direction D2, the rigidity and strength of the heat exchange core 10 can be made uniform in the circumferential direction D2, and the first in the circumferential direction D2. It can also contribute to the uniformization of the fluid flow state.
The larger the number of radial flow paths 61, the easier it is for the flow rate of the first fluid flowing through each radial flow path 61 to be made uniform. Then, sufficient heat is transferred between the first fluid and the second fluid that flow evenly over the entire circumferential direction D2. Considering this, it is preferable that four or more radial flow paths 61 are distributed in each of the second cross sections C2 and C2x. However, it is permissible that the number of radial flow paths 61 is 3 or less (including 1) in each of the second cross sections C2 and C2x.

In some embodiments, the plurality of radial flow paths 61 are distributed at equal intervals in the circumferential direction D2 in order to contribute to the uniform flow rate of the first fluid flowing through each radial flow path 61. Is preferable. That is, it is preferable that the heat exchange core 10 is formed symmetrically with respect to the center of the cross section even in the second cross sections C2 and C2x.
Furthermore, in some embodiments, it is preferable that the cross-sectional areas of the radial channels 61 are equal. Then, the length of the section in which the first fluid and the second fluid flow in the countercurrent along the axial direction D1 can be uniformly ensured in the circumferential direction D2 of the first flow path 101 and the second flow path 102. The tolerance of the flow path cross-sectional area in each of the radial flow paths 61 is allowed.

The shape of the cross section of each radial flow path 61 and the shape of the opening in the side wall W0 are rectangular in the examples shown in FIGS. 1 and 2, but may be an appropriate shape such as a circle. On the side wall W0, openings of the radial flow path 61 are distributed in the circumferential direction D2.

In addition, similarly to the above, in order to contribute to the uniform flow rate of the first fluid flowing through each radial flow path 61, the phases of the inlet port 22A and the radial flow path 61 are shifted from each other. That is, it is preferable that the inlet port 22A and the radial flow path 61 are arranged at different positions in the circumferential direction D2. When the phase of the inlet port 22A and the phase of the radial flow path 61 are shifted, the first flow through the radial flow path 61 is different from the case where the phase is not shifted (they are at the same position in the circumferential direction D2). It is possible to more reliably prevent the flow rate of the fluid from being biased.

In some embodiments, each radial flow path 61 comprises an assembly of tubular cross-walls W3 located in the region of the second flow path 102. The radial flow path 61 is separated from the second flow path group G2 by the cross wall W3. The cross wall W3 is provided integrally with the first partition wall W1 between the first partition walls W1 and W1 adjacent to each other in the radial direction of the heat exchange core 10. The respective axes of the cross wall W3 are located on the same straight line. Each first flow path 101 communicates with the inside of the cross wall W3.
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 first flow path (not shown) located near the axis of the heat exchange core 10 are the heat exchange core 10. It communicates with the internal spaces 221A and 222A of the first inlet header 221 and the first outlet header 222, respectively, through a plurality of radial flow paths 61 extending radially from the vicinity of the axis, and further communicates with the outside of the heat exchange core 10. doing.

(Explanation of the third cross section)
FIG. 5 corresponding to the VV line cross section of FIGS. 2 and 6 shows a third cross section C3 located outside the second cross section C2 in the axial direction D1.
In some embodiments, the first flow path group G1 communicating with the above-mentioned radial flow path 61 has a closed wall located outside the second cross section C2 in the axial direction D1 as shown in FIG. W4 is provided. The first fluid flowing through the first flow path group G1 does not flow beyond the closed wall W4 intersecting the axial direction D1 in the axial direction D1. The closing wall W4 closes between the adjacent first partition walls W1 and W1.

In some embodiments, the obstruction wall W4 obstructs the first flow path group G1 in the third cross section C3 (FIG. 5). Therefore, only the second flow path group G2 exists in the third cross section C3. Since the closed wall W4 exists in the region shown by the grid pattern in FIG. 5, the first flow path group G1 does not exist.
The second flow path group G2 is open to the second inlet header 31 and the second outlet header 32 at the end of the heat exchange core 10, respectively.

Although the cross-sectional view taken along the line Vx-Vx in FIG. 2 is omitted, it is the same as in FIG. In some embodiments, the cross section corresponding to the Vx-Vx line of FIG. 2 corresponds to a third cross section C3x located outside the second cross section C2x in the axial direction D1. The cross section corresponding to the Vx-Vx line is referred to as a third cross section C3x.
In some embodiments, as shown in FIG. 6, the closing wall W4 closes the first flow path group G1 in the third cross section C3x. Therefore, only the second flow path group G2 exists in the third cross section C3x.

(Flow of first fluid and second fluid)
The flow of the first fluid and the second fluid in the heat exchange core 10 will be described with reference to FIGS. 2, 4, and 6. FIG. 6 shows a part of the vertical cross section of the heat exchange core 10.
In some embodiments, as shown by the dashed arrow in FIG. 6, the second fluid that has flowed into the interior of the second inlet header 31 through an inlet port (not shown) is the second flow path 102 of the second flow path group G2. It flows into each of the beginnings of. 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, each of the second flow paths 102 is the first in the circumferential direction D2. The two fluids flow uniformly and flow in the second flow path 102 in the axial direction D1. The second fluid flows out from the end of the second flow path 102 to the inside of the second outlet header 32, and further flows out to the outside of the heat exchanger 1 through an outlet port (not shown).

In some embodiments, as shown by the solid arrows in FIG. 6, the first fluid that has flowed from the inlet port 22A into the first inlet header 221 is first through a radial flow path 61 that opens into the side wall W0. It flows evenly from the inlet header 221 into the first flow path group G1 in the circumferential direction D2.
At this time, the first fluid is distributed from the first inlet header 221 to each of the plurality of radial flow paths 61 without being biased to a part of the radial flow paths 61 near the inlet port 22A, and each radial flow path 61 is distributed. In, the first fluid passes through the inside of the cross wall W3 shown by the alternate long and short dash line in FIG. 6 toward the inside of the heat exchange core 10 in the radial direction, and is distributed to each first flow path 101.

After that, based on the symmetry of the heat exchange core 10 in the second cross section C2 where the radial flow path 61 is located, the flow rate of the first fluid flowing in the axial direction D1 in the first flow path 101 is the entire circumferential direction D2. It is maintained evenly over the years. Therefore, under the countercurrent, it is easy to secure a large temperature difference between the second fluid flowing through the second flow path 102 and the first fluid flowing through the first flow path 101 while flowing through the flow paths 101 and 102. , The heat can be sufficiently transferred over the entire range where the second cross section C2 is continuous.
When the first fluid flowing in the axial direction D1 in each of the first flow paths 101 reaches the end of the first flow path 101, the direction of the flow is changed from the axial direction D1 in the radial direction, and the axis of the heat exchange core 10 In each of the radial flow paths 61 arranged radially from the center, the radial flow paths 61 pass through the inside of the cross wall W3, merge, and flow toward the outside in the radial direction of the heat exchange core 10. Then, the first fluid flowing out from the radial flow path 61 to the inside of the first outlet header 222 flows out from the outlet port 22B to the outside of the heat exchanger 1.

(Main effects of the heat exchanger of the embodiment)
According to the heat exchanger 1 according to some embodiments described above, not only the casing 20 has a shape symmetrical with respect to the axial center, but also the first flow path group G1 and the second flow path group G2 Based on the configuration of the heat exchange core 10 which is symmetrically and concentrically laminated, the stress acting by the pressure of the fluid or the like is uniformly dispersed throughout the heat exchange core 10, and the first fluid and the second fluid are combined. While ensuring a large heat transfer area, heat exchange can be efficiently performed over the entire heat exchange core 10 through which the first fluid and the second fluid flow evenly.
From the above, it is possible to prevent damage to the heat exchange core 10 and improve reliability, and it is possible to obtain the same heat exchange capacity with a smaller heat exchange core 10.

(Details of radial flow path and circumferential flow path)
Hereinafter, details of the radial flow path and the circumferential flow path according to some embodiments will be described.
FIG. 8A is a schematic diagram for explaining a radial flow path and a circumferential flow path according to an embodiment, and is a diagram showing a second cross section C2.
FIG. 8B is a schematic diagram for explaining a radial flow path and a circumferential flow path according to another embodiment, and is a diagram showing a second cross section C2.
FIG. 9 is a schematic diagram for explaining the total angle range, and corresponds to a diagram showing a part of the second cross section C2. Note that FIG. 9 shows an enlarged part of the second cross section C2 in the other embodiment shown in FIG. 8B.

In the heat exchange core 10 according to some embodiments, 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 11A and the second header portion 11B have the same structure. The description will be given simply by referring to the header part 11 without distinguishing it from the part 1B and not adding the letters A and B to the reference numerals.

As shown in FIGS. 8A and 8B, in the header portion 11 according to some embodiments, the header flow path 6 includes at least one radial flow path 61 extending along the radial direction. In the header portion 11 according to some embodiments, the header flow path 6 is a plurality of circumferential flow paths 66 that branch from any of the radial flow paths 61 and communicate with one or more axial flow paths 3, respectively. including. The circumferential flow path 66 according to some embodiments is the first flow path 101 extending in the circumferential direction and the axial direction in the header portion 11 among the plurality of first flow paths 101.
At least one radial flow path 61 and a plurality of circumferential flow paths 66 branching from any of the radial flow paths 61 and communicating with one or more axial flow paths 3 are provided in the header flow path 6. By including it, the header portion 11 can be made relatively small.

In the heat exchanger 1 according to some embodiments, the header flow path 6 flows while circulating the first fluid that has flowed in the radial flow path 61 along the radial direction in the circumferential flow path 66 in the circumferential direction. Is also rotated in the axial direction and distributed to each of the first flow paths 101 arranged in the core main body 13. Further, in the heat exchanger 1 according to some embodiments, in the process of circulating the flow of the first fluid flowing along the axial direction in the core main body 13 through the circumferential flow path 66 and the radial flow path 61. It is turned in the radial direction. Therefore, the flow rate of the first fluid flowing in the core main body 13 may differ depending on the position in the circumferential direction or the radial direction, and the heat exchange efficiency may decrease due to such a difference in flow rate.
The heat exchanger 1 according to some embodiments has a configuration as described below in order to suppress the difference in the flow rate of the first fluid while suppressing the volume expansion of the header portion 11. Hereinafter, a configuration for suppressing the difference in the flow rate of the first fluid while suppressing the volume expansion of the header portion 11 will be sequentially described.

For example, as is well shown in FIG. 9, in the heat exchanger 1 according to some embodiments, the circumferential flow path 66 is an open end and is connected to the radial flow path from one end 66a to the closed end. It extends to the end 66b.
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 a flow path length Lc.
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 segment flow path 66s.

In the following description, the sum of the angular ranges centered on the radial center position (axis AX) when the circumferential flow path 66 is traced from one end 66a to the other end 66b is referred to as a total angle range θt. That is, the total angle range θt is an integrated value of the amount of change in the angle when the center position (axis AX) in the radial direction is taken as the center when tracing from one end 66a to the other end 66b in the circumferential flow path 66. be. The total angle range θt is the sum of the angle ranges in which the individual segment flow paths 66s included in one circumferential flow path 66 extend, as will be described later.

The outermost circumferential flow path 66-1 shown in FIG. 9 is composed of the outermost layer segment flow path 66s shown in FIG. Therefore, the total angle range θt in the circumferential flow path 66-1 is the angle range θ1 of the outermost layer segment flow path 66s shown in FIG.

For example, the circumferential flow path 66-2 adjacent to the outermost circumferential flow path 66-1 shown in FIG. 9 on the inner side in the radial direction is the outermost segment flow path 66s shown in FIG. It is composed of a second layer segment flow path 66s and a third layer segment flow path 66s counting from. That is, in the circumferential flow path 66-2, the segment flow path 66s of the second layer is along the radial direction with the end of the segment flow path 66s of the third layer at the end opposite to the one end 66a. Is connected. The circumferential flow path 66-2 is configured as one circumferential flow path 66 by the second layer segment flow path 66s and the third layer segment flow path 66s.
Therefore, the total angle range θt in the circumferential flow path 66-2 is the sum of the angle range θ2 of the second layer segment flow path 66s and the angle range θ3 of the third layer segment flow path 66s.

Further, in the example shown in FIG. 9, the segment flow path 66s of the fourth layer, the segment flow path 66s of the fifth layer, and the segment flow of the sixth layer counting from the segment flow path 66s of the outermost layer shown in FIG. 9 are counted. One circumferential flow path 66-3 is configured by the road 66s. That is, in the circumferential flow path 66-3, the segment flow path 66s of the fourth layer is along the radial direction with the end of the segment flow path 66s of the fifth layer at the end opposite to the one end 66a. Is connected. In the circumferential flow path 66-3, the fifth layer segment flow path 66s is connected to the end of the sixth layer segment flow path 66s along the radial direction at the end on the same side as the one end 66a. ing.
Therefore, the total angle range θt in the circumferential flow path 66-3 includes the angle range θ4 of the fourth layer segment flow path 66s, the angle range θ5 of the fifth layer segment flow path 66s, and the sixth layer segment. It is the sum of the angle range θ6 of the flow path 66s.

The connecting portion between the segment flow paths 66s adjacent to each other in the radial direction is referred to as a folded portion 66f. Further, the number of folded portions 66f in one circumferential flow path 66 is referred to as the number of folded portions.
The circumferential flow path 66 having the folded-back portion 66f will be described in detail later.
In the circumferential flow path 66 on the outermost circumference shown in FIG. 9, since the folded-back portion 66f does not exist, the number of folded-back portions is 0.

Here, the circumferential flow path 66 called the first circumferential flow path 661, and the circumferential flow path 66 located radially inside the first circumferential flow path 661 and the second circumferential flow path 662. Consider the so-called circumferential flow path 66.
For convenience of explanation, the flow path length Lc along the circumferential direction of the first circumferential flow path 661 is referred to as the first flow path length L1, and the flow path length Lc along the circumferential direction of the second circumferential flow path 662 is referred to as the first flow path length L1. Is referred to as a second flow path length L2.

For example, in the range shown in FIG. 9, in the relationship between the outermost circumferential flow path 66-1 and the other circumferential flow paths 66-2 and 66-3, the outermost peripheral 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.
Further, for example, in the range shown in FIG. 9, 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 in the radial direction. The circumferential flow path 66-3 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.
Including the not shown circumferential flow path existing outside the radial direction of the outermost circumferential flow path 66-1 in the range shown in FIG. 9, the not shown circumferential flow path and the outermost circumference Regarding the relationship between the directional flow path 66-1 and the other circumferential flow paths 66-2 and 66-3, the circumferential flow path (not shown) and the outermost peripheral circumferential flow path 66-1 are in the first circumferential direction. It corresponds to the flow path 661, and the other circumferential flow paths 66-2 and 66-3 correspond to the second circumferential flow path 662.
Although the first circumferential flow path 661 and the second circumferential flow path 662 have been described above with reference to FIG. 9, not only the other embodiment shown in FIG. 8B but also one embodiment shown in FIG. 8A. The same applies to each circumferential flow path 66 according to the above.

Even if the total angle range is θt, 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 are different due to the difference in radial position. Since the length of one flow path L1 is longer, if the flow path width (width in the radial direction) is the same, the pressure loss of the first circumferential flow path 661 is larger than that of the second circumferential flow path 662. This makes it difficult for the first fluid to flow.

Therefore, in the heat exchange core 10 according to some embodiments, the equal length in the plurality of circumferential flow paths 66 is ensured, and the flow rate deviation in the axial direction flow path 3 is suppressed. That is, in the heat exchange core 10 according to some embodiments, the flow from the circumferential flow path 66 into the axial flow path 3 by suppressing the deviation of the flow path length Lc in each of the plurality of circumferential flow paths 66. And, the flow rate of the first fluid flowing from the axial flow path 3 into the circumferential flow path 66 is prevented from being dispersed by the circumferential flow path 66.
Specifically, in the heat exchange core 10 according to some embodiments, as will be described later, the first circumferential flow path 661 and the first circumferential flow path 661 are located radially inside the first circumferential flow path 661. A plurality of circumferential flow paths 66 are configured so as to include a second circumferential flow path 662 arranged in the circumferential direction over a total angular range θt larger than the circumferential flow path 661.
That is, in the heat exchange core 10 according to some embodiments, 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, as will be described later. I have to.

As a result, the difference between the first flow path length L1 and the second flow path length L2 is increased as compared with the case where the total angle range θt is the same between the first circumferential flow path 661 and the second circumferential flow path 662. Can be suppressed. Therefore, it is possible to prevent the pressure loss from becoming larger in the first circumferential flow path 661 than in the second circumferential flow path 662, and to reduce the flow velocity in the first circumferential flow path 661 and the second circumferential flow path 662. The difference can be suppressed. Therefore, the difference between 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 is suppressed. , The heat exchange efficiency in the heat exchange core 10 can be improved.

(Regarding the radial flow path in the header portion according to one embodiment)
Hereinafter, the radial flow path 61 in the header portion 11 according to the embodiment shown in FIG. 8A will be mainly described. Regarding the contents of the circumferential flow path 66, for convenience of explanation, the contents that should be described in relation to the radial flow path 61 will also be described with respect to the circumferential flow path 66.
In the header portion 11 according to the embodiment shown in FIG. 8A, a plurality of radial flow paths 61 having different radial lengths are arranged at intervals in the circumferential direction. More specifically, in the header portion 11 according to the embodiment shown in FIG. 8A, a plurality of types of radial flow paths 61 having different distances from the side wall W0 to the inner end in the radial direction are formed. The radial flow path 61 according to the embodiment shown in FIG. 8A includes a first-class radial flow path 611 having the shortest radial length and a second-class radial flow path having the second shortest radial length. 612, the third type radial flow path 613 with the third shortest radial length, and the fourth type radial flow path 614 with the fourth shortest radial length (the longest radial length). Includes.
In the header portion 11 according to the embodiment shown in FIG. 8A, the folded-back portion 66f is not provided in the circumferential flow path 66.

Regardless of the type of radial flow path 611, 612, 613, 614, the radial outer end of the radial flow path 61 is the outer peripheral surface of the side wall W0. Located in.
The radial flow path 61 according to the embodiment is not limited to the example shown in FIG. 8A, and may include at least two types of radial flow paths 61 having different radial lengths. Further, the radial flow path 61 according to one embodiment is not limited to the example shown in FIG. 8A, and may include five types of radial flow paths 61 having different radial lengths.

As described above, in the header portion 11 according to the embodiment shown in FIG. 8A, a stepwise radial flow path group is formed by a plurality of radial flow paths 61 having different radial positions of the inner end portions in the radial direction.

In the present specification, when two types of radial flow paths 61 having different radial lengths and different lengths are described, the shorter radial length of the two types of radial flow paths 61 is described. The radial flow path 61 is also referred to as a first radial flow path 601, and the type of radial flow path 61 having a longer radial length is also referred to as a second radial flow path 602.
For example, in the case of explaining the first type radial flow path 611 having the shortest radial length and the second type radial flow path 612 having the second shortest radial length, the first kind radial flow path 611 corresponds to the first radial flow path 601 and the second shortest type 2 radial flow path 612 corresponds to the second radial flow path 602.
Similarly, in the case of explaining, for example, the second type radial flow path 612 having the second shortest radial length and the fourth type radial flow path 614 having the fourth shortest radial length, the second type The radial flow path 612 corresponds to the first radial flow path 601 and the type 4 radial flow path 614 corresponds to the second radial flow path 602.

The first type radial flow path 611 having the shortest radial length is the first radial flow path even when compared with any other type of radial flow path 612, 613, 614. It corresponds to 601. Further, when the type 4 radial flow path 614 having the fourth shortest radial length (the longest radial length) is compared with any other type of radial flow path 611, 612, 613. Even so, it corresponds to the second radial flow path 602. The second type radial flow path 612, which has the second shortest radial length, and the third type radial flow path 613, which has the third shortest radial length, depend on the type of the radial flow path 61 to be compared. In some cases, it corresponds to the first radial flow path 601 and in other cases, it corresponds to the second radial flow path 602.

In the header portion 11 according to the embodiment shown in FIG. 8A, each radial flow path 61 communicates with all or a part of the circumferential flow paths 66 adjacent to each other on one side and the other side in the circumferential direction. doing.

For example, the first type radial flow path 611 according to one embodiment communicates with all of the circumferential flow paths 66 adjacent to one side and the other side in the circumferential direction with respect to itself. The circumferential flow path 66 communicating with the first-class radial flow path 611 is referred to as a first-class circumferential flow path 671.

For example, the second type radial flow path 612 according to one embodiment is limited to a range radially inside the radial range occupied by the first type radial flow path 611, and is on one side in the circumferential direction with respect to itself. It communicates with all of the circumferential flow paths 66 adjacent to the other side. That is, the second type radial flow path 612 according to one embodiment communicates with the circumferential flow path 66 adjacent to itself in the radial direction in the radial range occupied by the first type radial flow path 611. No. The circumferential flow path 66 communicating with the type 2 radial flow path 612 is referred to as a type 2 circumferential flow path 672.

For example, the type 3 radial flow path 613 according to one embodiment is limited to a range radially inside the radial range occupied by the type 2 radial flow path 612, and is on one side in the circumferential direction with respect to itself. It communicates with all of the circumferential flow paths 66 adjacent to the other side. That is, the third type radial flow path 613 according to one embodiment communicates with the circumferential flow path 66 adjacent to itself in the radial direction in the radial range occupied by the second type radial flow path 612. No. The circumferential flow path 66 communicating with the type 3 radial flow path 613 is referred to as a type 3 circumferential flow path 673.

For example, the type 4 radial flow path 614 according to one embodiment is limited to a range radially inside the radial range occupied by the type 3 radial flow path 613, and is on one side in the circumferential direction with respect to itself. It communicates with all of the circumferential flow paths 66 adjacent to the other side. That is, the type 4 radial flow path 614 according to one embodiment communicates with the circumferential flow path 66 adjacent to itself in the radial direction in the radial range occupied by the type 3 radial flow path 613. No. The circumferential flow path 66 communicating with the type 4 radial flow path 614 is referred to as a type 4 circumferential flow path 674.

In the header portion 11 according to the embodiment shown in FIG. 8A, the first fluid flowing into the inside of the first inlet header 221 from the inlet port 22A is the first from the first type radial flow path 611 as shown by the arrow a1. It circulates to the type 1 circumferential flow path 671 and flows along the circumferential direction from one end 66a to the other end 66b in the type 1 circumferential flow path 671 toward the axial flow path 3 along the axial direction. To circulate.

Similarly, the first fluid flowing into the inside of the first inlet header 221 from the inlet port 22A flows from the second type radial flow path 612 to the second type circumferential flow path 672 as shown by the arrow a2. , In the type 2 circumferential flow path 672, it flows from one end 66a to the other end 66b along the circumferential direction and flows toward the axial flow path 3 along the axial direction.

The first fluid that has flowed into the inside of the first inlet header 221 from the inlet port 22A flows from the third type radial flow path 613 to the third type circumferential flow path 673 as shown by the arrow a3, and is the third. In the seed circumferential flow path 673, it flows from one end 66a to the other end 66b along the circumferential direction and flows toward the axial flow path 3 along the axial direction.

The first fluid that has flowed into the inside of the first inlet header 221 from the inlet port 22A flows from the fourth type radial flow path 614 to the fourth type circumferential flow path 674 as shown by the arrow a4, and is the fourth. In the seed circumferential flow path 674, it flows from one end 66a to the other end 66b along the circumferential direction and flows toward the axial flow path 3 along the axial direction.

For example, in one embodiment shown in FIG. 8A, in relation to the type 1 circumferential flow path 671 and the other types of circumferential flow paths 672, 673, 674, the type 1 circumferential flow path 671 is the first. Corresponding to the circumferential flow path 661, other types of circumferential flow paths 672, 673, 674 correspond to the second circumferential flow path 662.
Further, for example, in one embodiment shown in FIG. 8A, a type 1 circumferential flow path 671 and a type 2 circumferential flow path 672, and a type 3 circumferential flow path 673 and a type 4 circumferential flow path 674. In this relationship, the type 1 circumferential flow path 671 and the type 2 circumferential flow path 672 correspond to the first type circumferential flow path 661, and the type 3 circumferential flow path 673 and the type 4 circumferential flow path 674. Corresponds to the second circumferential flow path 662.
For example, in one embodiment shown in FIG. 8A, in relation to the type 4 circumferential flow path 674 and the other types of circumferential flow paths 671, 672, 673, the type 4 circumferential flow path 674 is the second. Corresponding to the circumferential flow path 662, other types of circumferential flow paths 671, 672, 673 correspond to the first circumferential flow path 661.

That is, in one embodiment shown in FIG. 8A, 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 over the radial range occupied by the first radial flow path 601 and the range radially inside the radial range, and communicates with the second circumferential flow path 662. doing.

Further, in one embodiment shown in FIG. 8A, the first radial flow path 601 does not communicate with the second circumferential flow path 662, and the second radial flow path 602 is the first circumferential flow path 661. Not communicating with.

In FIG. 8A, for convenience of explaining the arrangement position of each radial flow path 61 in the circumferential direction, the angle about the axis AX is defined as follows.
In one embodiment shown in FIG. 8A, for example, two Type 4 radial flow paths 614 having the fourth shortest radial length (the longest radial length) are provided, sandwiching the axis AX. It is assumed that they are arranged at positions that are 180 degrees apart from each other. Then, it is assumed that one of the two Type 4 radial flow paths 614 is arranged at an angle position of 90 degrees and the other is arranged at an angle position of 270 degrees.
Further, in FIG. 8A, the upper part in the drawing is an angle position of 90 degrees, the lower part in the drawing is an angle position of 270 degrees, the right side in the drawing is an angle position of 0 degrees, and the left side in the drawing is an angle position of 180 degrees.

In one embodiment shown in FIG. 8A, the partition wall (second partition wall) W5 is formed at the angle positions of 0 degrees and 180 degrees. The second partition wall W5 isolates the circumferential flow path 66 on one side and the other side in the circumferential direction with the second partition wall W5 at an angle position of 0 degrees and 180 degrees.
Although not shown, the second partition wall W5 may be further formed so as to partition the second flow path 102 on one side and the other side in the circumferential direction with the second partition wall W5 interposed therebetween.

In one embodiment shown in FIG. 8A, a region having an angle range of 0 to 180 degrees, which is a region on one side of the second partition wall W5, is also referred to as an upper half region Ru and sandwiches the second partition wall W5. The region on the other side, which has an angle range of 180 degrees to 360 degrees, is also referred to as a lower half region Rd.
In one embodiment shown in FIG. 8A, the upper half region Ru and the lower half region Rd may be formed so as to be symmetrical with respect to the second partition wall W5.

In one embodiment shown in FIG. 8A, in each of the upper half region Ru and the lower half region Rd, the other types of radial flow paths 61 except for the fourth type radial flow path 614 are the types of the radial flow paths 61. A plurality of lines are arranged at an even pitch along the circumferential direction. Further, in one embodiment shown in FIG. 8A, the arrangement pitches of any two radial flow paths 61 adjacent to each other in the circumferential direction along the circumferential direction are the same.
In one embodiment shown in FIG. 8A, as described above, one of the two Type 4 radial flow paths 614 is arranged at an angle position of 90 degrees, and the other is arranged at an angle position of 270 degrees. Therefore, two of them are arranged at a uniform pitch along the circumferential direction.

That is, in one embodiment shown in FIG. 8A, two or more first radial flow paths 601 are arranged at equal pitches along the circumferential direction. Two or more of the second radial flow paths 602 are arranged at equal pitches along the circumferential direction.
As a result, the length of the flow path of the circumferential flow path 66 differs depending on the connected first radial flow path 601 as compared with the case where the arrangement of the first radial flow path 601 has an uneven pitch. This can be suppressed, and it is possible to suppress the variation in the flow rate for each flow path in the circumferential flow path 66. Similarly, the length of the flow path of the circumferential flow path 66 differs depending on the connected second radial flow path 602 as compared with the case where the arrangement of the second radial flow path 602 has an uneven pitch. This can be suppressed, and it is possible to suppress the variation in the flow rate for each flow path in the circumferential flow path 66. As a result, it is possible to suppress a decrease in heat exchange efficiency.
Further, by arranging them at uniform pitches, the radial flow paths 61 can be efficiently arranged, and the number of radial flow paths 61 can be suppressed. As a result, 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 is suppressed, and the proportion of the region occupied by the circumferential flow path 66 is increased. Can be done.

In one embodiment shown in FIG. 8A, the shorter the radial length, the larger the number of arrangements. Specifically, in one embodiment shown in FIG. 8A, 16 types 1 radial flow paths 611 are arranged, 8 types 2 radial flow paths 612 are arranged, and 3 types radial flow paths 613 are arranged. Is arranged, and two types 4 radial flow paths 614 are arranged. Therefore, in one embodiment shown in FIG. 8A, the shorter the radial length, the smaller the arrangement pitch along the circumferential direction of the radial flow path 61.
That is, in one embodiment shown in FIG. 8A, the number of the first radial flow paths 601 is larger than the number of the second radial flow paths 602.
As a result, the number of the first radial flow paths 601 is smaller than the number of the second radial flow paths 602, and the two first radial flow paths 601 adjacent to each other in the circumferential direction are along the circumferential direction. Since the separation distance can be reduced, the first flow path length L1 of the first circumferential flow path 661 can be suppressed. As a result, 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, so that the second circumferential flow path 662 and the first The difference in pressure loss from the circumferential flow path 661 can be suppressed, and the difference in flow velocity between the first circumferential flow path 661 and the second circumferential flow path 662 can be suppressed.

(Regarding the circumferential flow path in the header portion according to one embodiment)
Hereinafter, the circumferential flow path 66 in the header 11 portion according to the embodiment shown in FIG. 8A will be mainly described with respect to the points not mentioned in the above description.
In the header 11 portion according to the embodiment shown in FIG. 8A, each of the circumferential flow paths 66 is connected to any radial flow path 61 at one end 66a, which is an open end, as described above. Each of the circumferential flow paths 66 according to the embodiment shown in FIG. 8A has the other radial flow path due to the cross wall W3 in the other radial flow path 61 different from the radial flow path 61 at the other end 66b. It is separated from 61 or is separated from the circumferential flow path 66 by another circumferential flow path 66 adjacent to the circumferential flow path 66 in the circumferential direction by a second partition wall W5.

In one embodiment shown in FIG. 8A, for example, focusing on the first type radial flow path 611 having the shortest radial length and the second type radial flow path 612 having the second shortest radial length. As described above, the first type radial flow path 611 corresponds to the first radial flow path 601 and the second shortest second type radial flow path 612 corresponds to the second radial flow path 602. In this case, focusing on the type 1 circumferential flow path 671 communicating with the type 1 radial flow path 611 and the type 2 circumferential flow path 672 communicating with the type 2 radial flow path 612, the first The seed circumferential flow path 671 corresponds to the first circumferential flow path 661, and the seed circumferential flow path 672 corresponds to the second circumferential flow path 662.

Similarly, for example, focusing on the second type radial flow path 612 having the second shortest radial length and the fourth type radial flow path 614 having the fourth shortest radial length, as described above. The second type radial flow path 612 corresponds to the first radial flow path 601 and the fourth type radial flow path 614 corresponds to the second radial flow path 602. In this case, focusing on the type 2 circumferential flow path 672 that communicates with the type 2 radial flow path 612 and the type 4 circumferential flow path 674 that communicates with the type 4 radial flow path 614, the second type The seed circumferential flow path 672 corresponds to the first circumferential flow path 661, and the type 4 circumferential flow path 674 corresponds to the second circumferential flow path 662.

In one embodiment shown in FIG. 8A, for example, when the first type radial flow path 611 and the second type radial flow path 612 that are adjacent in the circumferential direction are focused on, they communicate with the second type radial flow path 612. The total angle range θt2 of the type 2 circumferential flow path 672 is larger than the total angle range θt1 of the type 1 circumferential flow path 671 communicating with the type 1 radial flow path 611.

In one embodiment shown in FIG. 8A, for example, when focusing on the type 2 radial flow path 612 and the type 3 radial flow path 613 that are adjacent to each other in the circumferential direction, they communicate with the type 3 radial flow path 613. The total angle range θt3 of the type 3 circumferential flow path 673 is larger than the total angle range θt2 of the type 2 circumferential flow path 672 communicating with the type 2 radial flow path 612.

In one embodiment shown in FIG. 8A, for example, when focusing on the type 3 radial flow path 613 and the type 4 radial flow path 614 that are adjacent to each other in the circumferential direction, they communicate with the type 4 radial flow path 614. The total angle range θt4 of the type 4 circumferential flow path 674 is larger than the total angle range θt3 of the type 3 circumferential flow path 673 communicating with the type 3 radial flow path 613.

That is, in one embodiment shown in FIG. 8A, the total angle range θt of the second circumferential flow path 662 is larger than the total angle range θt of the first circumferential flow path 661.

In one embodiment shown in FIG. 8A, for example, the type 2 circumferential flow path 672 passes through the type 1 radial flow path 611 in the circumferential direction, and the type 2 radial flow path 612 to the first type. It extends to the opposite side of the radial flow path 611.
Similarly, in one embodiment shown in FIG. 8A, for example, the type 3 circumferential flow path 673 passes through the type 2 radial flow path 612 in the circumferential direction and from the type 3 radial flow path 613. It extends to the opposite side across the Type 2 radial flow path 612.
In one embodiment shown in FIG. 8A, for example, the type 4 circumferential flow path 674 passes through the type 3 radial flow path 613 in the circumferential direction, and the type 4 radial flow path 614 to the type 3 It extends to the opposite side of the radial flow path 613.

That is, in one embodiment shown in FIG. 8A, the second circumferential flow path 662 passes through the first radial flow path 601 in the circumferential direction, and the second radial flow path 602 to the first radial flow path 602. It extends to the opposite side across 601.
As a result, the total angular range θt of the second circumferential flow path 662 is made larger than that of the first circumferential flow path 661 without complicating the shapes of the first circumferential flow path 661 and the second circumferential flow path 662. The difference in flow velocity between the first circumferential flow path 661 and the second circumferential flow path 662 can be suppressed.

In one embodiment shown in FIG. 8A, as described above, the first radial flow path 601 does not communicate with the second circumferential flow path 662, and the second radial flow path 602 is in the first circumferential direction. It does not communicate with the flow path 661.
As a result, 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 is supplied to the first circumferential flow path 661. Therefore, it is possible to suppress an insufficient supply amount of the first fluid to the first circumferential flow path 661, and it is possible to suppress a decrease in heat exchange efficiency.
Similarly, when the first fluid flows from the second radial flow path 602 to the second circumferential flow path 662, all the fluid from the second radial flow path 602 can be supplied to the second circumferential flow path 662. , It is possible to suppress an insufficient supply amount of the first fluid to the second circumferential flow path 662, and it is possible to suppress a decrease in heat exchange efficiency.
Further, 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. It is possible to prevent the flow rate of the first fluid flowing through the first radial flow path 601 from being increased by the first fluid from the second circumferential flow path 662. As a result, an increase in pressure loss in the first radial flow path 601 can be suppressed, a decrease in flow rate in the first circumferential flow path 661 can be suppressed, and a decrease in heat exchange efficiency can be suppressed.
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. , It is possible to prevent the flow rate of the first fluid flowing through the second radial flow path 602 from being increased by the fluid from the first circumferential flow path 661. As a result, an increase in pressure loss in the second radial flow path 602 can be suppressed, a decrease in flow rate in the second circumferential flow path 662 can be suppressed, and a decrease in heat exchange efficiency can be suppressed.

In one embodiment shown in FIG. 8A, as described above, the radial flow path 61 is connected to the circumferential flow path 66 located on one side and the other side in the circumferential direction with respect to the radial flow path 61, respectively. ing.
As a result, the diameter of the radial flow path 61 is larger than that of the case where the radial flow path 61 is connected only to the circumferential flow path 66 located on either one side or the other side in the circumferential direction with respect to the radial flow path 61. The number of directional flow paths 61 can be suppressed. As a result, the proportion of the region occupied by the radial flow path 61 in the cross section of the header portion 11 when viewed from the axial direction can be suppressed, and the proportion of the region occupied by the circumferential flow path 66 can be increased.

In one embodiment shown in FIG. 8A, the flow path length of the circumferential flow path 66 depends on the number of radial flow paths 61, the number of variations in radial length, the radial length of each type, and the arrangement pattern. Since Lc can be adjusted, it is desirable to make the difference in flow path length Lc as small as possible.

(Regarding the radial flow path in the header portion according to another embodiment)
Hereinafter, the radial flow path 61 in the header portion 11 according to the other embodiment shown in FIG. 8B will be mainly described with reference to FIG. 9.
In the header portion 11 according to another embodiment shown in FIG. 8B, a plurality of radial flow paths 61 having the same radial length are arranged at intervals in the circumferential direction. More specifically, in the header portion 11 according to the other embodiment shown in FIG. 8B, radial flow paths 61 of the same type having the same distance from the side wall W0 to the inner end in the radial direction have uniform pitches in the circumferential direction. It is formed of four.
By arranging the plurality of radial flow paths 61 at uniform pitches in the circumferential direction in this way, the connected radial flow paths are compared with the case where the radial flow paths 61 are arranged at uneven pitches. It is possible to suppress a difference in the flow path length Lc of the circumferential flow path 66 depending on the 61, and it is possible to suppress the variation in the flow rate for each flow path in the circumferential flow path 66.
Further, by arranging them at uniform pitches, the radial flow paths 61 can be efficiently arranged, and the number of radial flow paths 61 can be suppressed. As a result, 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 is suppressed, and the proportion of the region occupied by the circumferential flow path 66 is increased. Can be done.

In each of the radial flow paths 61 according to the other embodiments, the radial outer end of the radial flow path 61 is located on the outer peripheral surface of the side wall W0.
The radial flow path 61 according to the other embodiment communicates with the circumferential flow path 66 adjacent to each other on one side and the other side in the circumferential direction at one end 66a of the circumferential flow path 66. That is, in the header portion 11 according to the other embodiment shown in FIG. 8B, the first circumferential flow path 661 and the second circumferential flow path 662 communicate with the same radial flow path 61.
As a result, the number of radial flow paths 61 can be suppressed as 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. As a result, 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 is suppressed, and the proportion of the region occupied by the circumferential flow path 66 is increased. Can be done.

In FIG. 8B, for convenience of explaining the arrangement position of each radial flow path 61 in the circumferential direction, the angle about the axis AX is defined as follows.
In another embodiment shown in FIG. 8B, for example, four radial flow paths 61 are arranged at 90 degree intervals. It is assumed that the four radial flow paths 61 are arranged at an angle position of 0 degrees, an angle position of 90 degrees, an angle position of 180 degrees, and an angle position of 270 degrees.
Further, in FIG. 8B, the upper part in the drawing is an angle position of 90 degrees, the lower part in the drawing is an angle position of 270 degrees, the right side in the drawing is an angle position of 0 degrees, and the left side in the drawing is an angle position of 180 degrees.

In another embodiment shown in FIG. 8B, partition walls (second partition walls) W5 are formed at angular positions of 45 degrees, 135 degrees, 225 degrees, and 315 degrees. In another embodiment shown in FIG. 8B, the second partition wall W5 isolates the circumferential flow path 66 on one side and the other side in the circumferential direction with the second partition wall W5 interposed therebetween at the above-mentioned angular position.
Although not shown, the second partition wall W5 may be further formed so as to partition the second flow path 102 on one side and the other side in the circumferential direction with the second partition wall W5 interposed therebetween.

In another embodiment shown in FIG. 8B, the region having an angle range of 0 to 180 degrees is also referred to as an upper half region Ru, and the region having an angle range of 180 degrees to 360 degrees is also referred to as a lower half region Rd.
In one embodiment shown in FIG. 8B, the upper half region Ru and the lower half region Rd are formed so as to be symmetrical with respect to the radial flow path 61 arranged at the angle positions of 0 degrees and 180 degrees. May be good. Further, in one embodiment shown in FIG. 8B, it may be formed so as to be symmetrical with respect to the radial flow path 61 arranged at the angle positions of 90 degrees and 270 degrees.

(Regarding the circumferential flow path in the header portion according to another embodiment)
In the header portion 11 according to the other embodiment shown in FIG. 8B, each of the circumferential flow paths 66 is connected to any radial flow path 61 at one end 66a, which is an open end, as described above. (See FIG. 9). Each of the circumferential flow paths 66 according to the other embodiment shown in FIG. 8B is separated from the radial flow path 61 by the cross wall W3 in the radial flow path 61 at the other end 66b, or the circumferential flow. It is separated from another circumferential flow path 66 adjacent to the road 66 in the circumferential direction by a second partition wall W5.

In the header portion 11 according to the other embodiment shown in FIG. 8B, among the plurality of circumferential flow paths 66 arranged along the radial direction, at least the outermost circumferential flow path 66 in the radial direction is described above. It does not have a folded-back portion 66f. For example, in the header portion 11 according to another embodiment shown in FIG. 8B, the first to third circumferential flow paths 66 in order from the outer side in the radial direction along the radial direction have the above-mentioned folded portion 66f. No.

In the header portion 11 according to the other embodiment shown in FIG. 8B, with respect to the plurality of segment flow paths 66s, the first segment flow path 66s-1 and the second segment flow path 66s- are arranged in order from the outside in the radial direction along the radial direction. 2. 3rd segment flow path 66s-3, 4th segment flow path 66s-4, 5th segment flow path 66s-5, 6th segment flow path 66s-6, 7th segment flow path 66s-7, and 8th segment flow path It is referred to as a segment flow path 66s-8.

In the header portion 11 according to the other embodiment shown in FIG. 8B, each of the first segment flow path 66s-1, the second segment flow path 66s-2, and the third segment flow path 66s-3 is individually one. It constitutes a circumferential flow path 66. The number of folds in each of these one circumferential flow paths 66 is 0.

Further, in the header portion 11 according to another embodiment shown in FIG. 8B, the fourth segment flow path 66s-4 and the fifth segment flow path 66s-5 are connected by a folded-back portion 66f, and the fourth segment flow path is connected. One circumferential flow path 66 is formed by 66s-4 and the fifth segment flow path 66s-5. The number of folds in the one circumferential flow path 66 is 1.

In the header portion 11 according to another embodiment shown in FIG. 8B, the sixth segment flow path 66s-6 and the seventh segment flow path 66s-7 are connected by a folded-back portion 66f, and the seventh segment flow path 66s- 7 and the 8th segment flow path 66s-8 are connected by a folded-back portion 66f. Then, one circumferential flow path 66 is formed by the sixth segment flow path 66s-6, the seventh segment flow path 66s-7, and the eighth segment flow path 66s-8. The number of folds in the one circumferential flow path 66 is 2.

In the header portion 11 according to the other embodiment shown in FIG. 8B, the first fluid flowing into the inside of the first inlet header 221 from the inlet port 22A flows from each radial flow path 61 in the circumferential direction as shown by an arrow b. It circulates to the flow path 66.
Circumferential flow path 66 composed of first segment flow path 66s-1, circumferential flow path 66 composed of second segment flow path 66s-2, and circumference composed of third segment flow path 66s-3. In the directional flow path 66, the first fluid flows from one end 66a to the other end 66b along the circumferential direction and flows toward the axial flow path 3 along the axial direction.

In the circumferential flow path 66 composed of the fourth segment flow path 66s-4 and the fifth segment flow path 66s-5, the first fluid is sent from one end 66a arranged in the fourth segment flow path 66s-4. It circulates along the axial direction toward the axial flow path 3 while meandering along the circumferential direction and the radial direction to the other end 66b arranged in the fifth segment flow path 66s-5.

In the circumferential flow path 66 composed of the sixth segment flow path 66s-6, the seventh segment flow path 66s-7, and the eighth segment flow path 66s-8, the first fluid is the sixth segment flow path 66s-. From one end 66a arranged at 6 to the other end 66b arranged at the eighth segment flow path 66s-8, meandering along the circumferential direction and the radial direction and flowing, the axial flow path 3 along the axial direction. It circulates toward.

The header portion 11 according to another embodiment shown in FIG. 8B is configured so that the number of push-backs increases as the circumferential flow path 66 increases in the radial direction. That is, in the header portion 11 according to the other embodiment shown in FIG. 8B, the second circumferential flow path 662 has a larger number of turns than the first circumferential flow path 661.
By increasing the number of turns in the second circumferential flow path 662 from the first circumferential flow path 661, the total angle range θt in the second circumferential flow path 662 can be increased and the second flow path length L2 can be secured. Thereby, the difference in the flow velocities between the first circumferential flow path 661 and the second circumferential flow path 662 can be suppressed.
In the header portion 11 according to the other embodiment shown in FIG. 8B, the number of folds is not limited to the example of FIG. 8B, and may be 3 or more.

In the header portion 11 according to the other embodiment shown in FIG. 8B, between the two radial flow paths 61 adjacent to each other in the circumferential direction, a plurality of lines branched from one of the two radial flow paths 61 A second partition wall W5 is formed which is a partition wall separating the circumferential flow path 66 and a plurality of circumferential flow paths 66 branched from the other of the two radial flow paths 61 in the circumferential direction.
As a result, the circumferential range in which the circumferential flow path 66 connected to one radial flow path 61 is arranged and the circumference in which the circumferential flow path 66 connected to the other radial flow path 61 is arranged. The range of directions can be defined by the second partition wall W5.

In the heat exchanger 1 provided with the heat exchange core 10 according to some of the above-described embodiments, the heat exchanger 1 can be relatively miniaturized and the heat exchange efficiency can be improved.

(About the manufacturing method of heat exchange core)
Hereinafter, an example of a method for manufacturing the heat exchange core 10 according to some of the above-described embodiments will be described.
FIG. 10 is a flowchart showing a processing procedure in the method for manufacturing the heat exchange core 10 according to some of the above-described embodiments.
In the method for manufacturing the heat exchange core 10 according to some of the above-described embodiments, the core main body portion 13 is formed by laminating molding to form the core main body portion 13 including a plurality of axial flow paths 3 extending along the axial direction. A header portion is formed by step S1 and laminating molding to form a header portion 11 having a header flow path 6 adjacent to at least one end of the core main body portion 13 in the axial direction and communicating with a plurality of axial flow paths 3. The process S3 and the like are provided.

In the header portion forming step S3, at least one radial flow path 61 extending along the radial direction and one or more radial flow paths 3 branched from any of the radial flow paths 61 are communicated with each other. The header flow path 6 is formed so as to include a plurality of circumferential flow paths 66.
Further, the header portion forming step S3 is located radially inside the first circumferential flow path 661 and the first circumferential flow path 661, and covers a total angle range θt larger than the first circumferential flow path 661. A plurality of circumferential flow paths 66 are formed so as to include a second circumferential flow path 662 arranged in the circumferential direction.

As a result, the heat exchange core 10 can be integrally formed by the laminated molding, so that it is not necessary to assemble the members or seal the members with a gasket. Therefore, the labor for maintenance can be significantly reduced.

The present disclosure is not limited to the above-described embodiment, and includes a modified form of the above-described embodiment and a combination of these embodiments as appropriate.

The contents described in each of the above embodiments are grasped as follows, for example.
(1) The heat exchange core 10 according to at least one embodiment of the present disclosure includes a core main body portion 13 and a header portion 11. The core body 13 includes a plurality of axial flow paths 3 extending along the axial direction. The header portion 11 has a header flow path 6 that is adjacent to at least one end of the core main body portion 13 in the axial direction and communicates with a plurality of axial flow paths 3.
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 that branch from any of the radial flow paths 61 and communicate with one or more axial flow paths 3, respectively.
The plurality of circumferential flow paths 66 include the first circumferential flow path 661. The plurality of circumferential flow paths 66 are located radially inside the first circumferential flow path 661 and are arranged in the circumferential direction over a total angular range θt larger than the first circumferential flow path 661. Includes a bi-circumferential flow path 662.

According to the configuration of (1) above, the header flow path 6 is branched from at least one radial flow path 61 and any of the radial flow paths 61 and communicates with one or more axial flow paths 3, respectively. By including a plurality of circumferential flow paths 66, the header portion 11 can be made relatively small.
It should be noted that simply, at least one radial flow path 61 in the header flow path 6 and a plurality of circumferential flows branching from any of the radial flow paths 61 and communicating with one or more axial flow paths 3 respectively. If only the road 66 is included, the first flow path length L1 in the first circumferential flow path 661 and the second flow path 662 in the second circumferential direction flow path 662 due to the difference in radial position even if the total angle range θt is the same. Since the first flow path length L1 is longer than the two flow path lengths L2, if the flow path widths (diameter width) are the same, the first circumferential flow direction is higher than the second circumferential flow path 662. The pressure loss is larger in the path 661, and the first fluid is less likely to flow.
In that respect, in the case of the heat exchange core 10 having the configuration of the above (1), 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, so that the first Compared with the case where the total angle range θt is the same between the 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. As a result, the pressure loss of the first circumferential flow path 661 is suppressed to be larger than that of the second circumferential flow path 662, and the flow velocities in the first circumferential flow path 661 and the second circumferential flow path 662 are suppressed. The difference can be suppressed. Therefore, the difference between 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 is suppressed. , The heat exchange efficiency in the heat exchange core 10 can be improved.

(2) In some embodiments, in the configuration of (1) above,
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 over the radial range occupied by the first radial flow path 601 and the range radially inside the radial range, and communicates with the second circumferential flow path 662. doing. 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 with the first radial flow path 601 in between.

According to the configuration of (2) above, the second circumferential flow path 662 is more than the first circumferential flow path 661 without complicating the shapes of the first circumferential flow path 661 and the second circumferential flow path 662. The total angle range θt can be increased, and the difference in flow velocity between the first circumferential flow path 661 and the second circumferential flow path 662 can be suppressed.

(3) In some embodiments, in the configuration of (2) above, the first radial flow path 601 does not communicate with the second circumferential flow path 662, and the second radial flow path 602 is It does not communicate with the first circumferential flow path 661.

According to the configuration of (3) above, when the first fluid flows from the first radial flow path 601 to the first circumferential flow path 661, all the first fluids from the first radial flow path 601 are first. Since it can be supplied to the circumferential flow path 661, it is possible to suppress an insufficient supply amount of the first fluid to the first circumferential flow path 661, and it is possible to suppress a decrease in heat exchange efficiency.
Similarly, when the first fluid flows from the second radial flow path 602 to the second circumferential flow path 662, all the fluid from the second radial flow path 602 can be supplied to the second circumferential flow path 662. , It is possible to suppress an insufficient supply amount of the first fluid to the second circumferential flow path 662, and it is possible to suppress a decrease in heat exchange efficiency.
Further, 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. It is possible to prevent the flow rate of the first fluid flowing through the first radial flow path 601 from being increased by the first fluid from the second circumferential flow path 662. As a result, an increase in pressure loss in the first radial flow path 601 can be suppressed, a decrease in flow rate in the first circumferential flow path 661 can be suppressed, and a decrease in heat exchange efficiency can be suppressed.
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. , It is possible to prevent the flow rate of the first fluid flowing through the second radial flow path 602 from being increased by the fluid from the first circumferential flow path 661. As a result, an increase in pressure loss in the second radial flow path 602 can be suppressed, a decrease in flow rate in the second circumferential flow path 662 can be suppressed, and a decrease in heat exchange efficiency can be suppressed.

(4) In some embodiments, in the configuration of (2) or (3) above, one or more first radial flow paths 601 are arranged. A plurality of second radial flow paths 602 are arranged along the circumferential direction. The number of the first radial flow paths 601 is larger than the number of the second radial flow paths 602.

According to the configuration of (4) above, the number of the first radial flow paths 601 is smaller than the number of the second radial flow paths 602, as 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. Since the distance at which 601 is separated along the circumferential direction can be reduced, the first flow path length L1 of the first circumferential flow path 661 can be suppressed. As a result, 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, so that the second circumferential flow path 662 and the first The difference in pressure loss from the circumferential flow path 661 can be suppressed, and the difference in flow velocity between the first circumferential flow path 661 and the second circumferential flow path 662 can be suppressed.

(5) In some embodiments, in any of the configurations (2) to (4) above, two or more first radial flow paths 601 are arranged at equal pitches along the circumferential direction. .. Two or more of the second radial flow paths 602 are arranged at equal pitches along the circumferential direction.

According to the configuration of (5) above, as compared with the case where the arrangement of the first radial flow path 601 is uneven pitch, the flow path of the circumferential flow path 66 by the connected first radial flow path 601 It is possible to suppress the occurrence of a difference in the lengths of the above, and it is possible to suppress the variation in the flow rate for each flow path in the circumferential flow path 66. Similarly, the length of the flow path of the circumferential flow path 66 differs depending on the connected second radial flow path 602 as compared with the case where the arrangement of the second radial flow path 602 has an uneven pitch. This can be suppressed, and it is possible to suppress the variation in the flow rate for each flow path in the circumferential flow path 66. As a result, it is possible to suppress a decrease in heat exchange efficiency.
Further, by arranging them at uniform pitches, the radial flow paths 61 can be efficiently arranged, and the number of radial flow paths 61 can be suppressed. As a result, 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 is suppressed, and the proportion of the region occupied by the circumferential flow path 66 is increased. Can be done.

(6) In some embodiments, in the configuration of (1) above, the first circumferential flow path 661 and the second circumferential flow path 662 communicate with the same radial flow path 61. The second circumferential flow path 662 has a larger number of turns than the first circumferential flow path 661.

According to the configuration of (6) above, the number of radial flow paths 61 is larger than that in the case where the first circumferential flow path 661 and the second circumferential flow path 662 are connected to different radial flow paths 61. Can be suppressed. As a result, 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 is suppressed, and the proportion of the region occupied by the circumferential flow path 66 is increased. Can be done.
Further, by increasing the number of turns in the second circumferential flow path 662 from the first circumferential flow path 661, the total angle range θt in the second circumferential flow path 662 is increased to secure the second flow path length L2. can. Thereby, the difference in the flow velocities between the first circumferential flow path 661 and the second circumferential flow path 662 can be suppressed.

(7) In some embodiments, in the configuration of (6) above, two or more radial flow paths 61 are provided apart from each other in the circumferential direction. Between the two radial flow paths 61 adjacent to each other in the circumferential direction, a plurality of circumferential flow paths 66 branched from one of the two radial flow paths 61 and the two radial flow paths A second partition wall W5, which is a partition wall separating the plurality of circumferential flow paths 66 branched from the other side of the 61 in the circumferential direction, is formed.

According to the configuration of (7) above, the circumferential range in which the circumferential flow path 66 connected to one radial flow path 61 is arranged and the circumferential flow connected to the other radial flow path 61. The range in the circumferential direction in which the road 66 is arranged can be defined by the second partition wall W5.

(8) In some embodiments, in the configuration of (6) or (7) above, a plurality of radial flow paths 61 are arranged at equal pitches along the circumferential direction.

According to the configuration of (8) above, the flow path length Lc of the circumferential flow path 66 differs depending on the connected radial flow path 61 as compared with the case where the radial flow paths 61 are arranged at uneven pitches. Can be suppressed, and the flow rate can be suppressed from fluctuating in each flow path in the circumferential flow path 66.
Further, by arranging them at uniform pitches, the radial flow paths 61 can be efficiently arranged, and the number of radial flow paths 61 can be suppressed. As a result, 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 is suppressed, and the proportion of the region occupied by the circumferential flow path 66 is increased. Can be done.

(9) In some embodiments, in any of the configurations (1) to (8) above, the radial flow path 61 is located on one side and the other side in the circumferential direction with respect to the radial flow path 61. It is connected to the circumferential flow path 66 located at each position.

According to the configuration of (9) above, the radial flow path 61 is connected only to the circumferential flow path 66 located 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 compared with the case where there is. As a result, the proportion of the region occupied by the radial flow path 61 in the cross section of the header portion 11 when viewed from the axial direction can be suppressed, and the proportion of the region occupied by the circumferential flow path 66 can be increased.

(10) In some embodiments, in any of the configurations (1) to (9) above, the plurality of axial flow paths 3 are arranged in an annular shape when viewed from the axial direction.

According to the configuration of (10) above, the stress acting by the pressure of the fluid or the like can be uniformly dispersed throughout the heat exchange core 10.

(11) In some embodiments, in any of the configurations (1) to (10), the at least one radial flow path 61 is two or more radial flow paths 61. The two or more radial flow paths 61 are given the same flow path cross-sectional area.

According to the configuration of (11) above, the difference in the flow rate of the fluid in the two or more radial flow paths 61 as compared with the case where different flow path cross-sectional areas are given in the two or more radial flow paths 61. Can be suppressed, so that a decrease in heat exchange efficiency can be suppressed.

(12) In some embodiments, in any of the configurations (1) to (11) above, the plurality of axial flow paths 3 are each divided into a plurality of compartments S in the circumferential direction.

According to the configuration of (12) above, the heat transfer efficiency can be improved by the existence of the wall that divides the axial flow path 3 into sections. The wall can improve the rigidity and strength of the heat exchange core 10, especially in the radial direction.

(13) In some embodiments, in the configuration of (12) above, the flow paths of the plurality of compartments S are made uniform in the plurality of axial flow paths 3.

According to the configuration of (13) above, the flow state such as friction loss is made uniform in all the sections, so that the heat transfer coefficient can be made uniform in all the sections, and the stress is the cross section of the heat exchange core 10. The stress can be made uniform by uniformly dispersing the heat in the entire in-plane direction.

(14) The heat exchanger 1 according to at least one embodiment of the present disclosure includes a heat exchange core 10 having the configuration according to any one of (1) to (13) above, and a casing 20 accommodating the heat exchange core 10. Be prepared.

According to the configuration of (14) above, the heat exchanger 1 can be made relatively small and the heat exchange efficiency can be improved.

(15) The method for manufacturing a heat exchange core according to at least one embodiment of the present disclosure is a method for manufacturing a heat exchange core 10, and a plurality of axial flow paths 3 extending along the axial direction by laminated molding. A header flow that is adjacent to at least one end of the core body 13 in the axial direction and communicates with a plurality of axial flow paths 3 by the core body forming step S1 for forming the core body 13 including the core body 13 and the laminated molding. A header portion forming step S3 for forming the header portion 11 having the path 6 is provided.
In the header portion forming step S3, at least one radial flow path 61 extending along the radial direction and one or more axial flow paths 3 branched from any of the radial flow paths 61 are communicated with each other. The header flow path 6 is formed so as to include a plurality of circumferential flow paths 66. The header portion forming step S3 is located radially inside the first circumferential flow path 661 and the first circumferential flow path 661, and goes around over a total angle range θt larger than the first circumferential flow path 661. A plurality of circumferential flow paths 66 are formed so as to include a second circumferential flow path 662 arranged in the direction.

According to the method (15) above, since the heat exchange core 10 can be integrally formed by the laminated molding, it is not necessary to assemble the members or seal the members with a gasket. Therefore, the labor for maintenance can be significantly reduced.

1 Heat exchanger 3 Axial flow path 6 Header flow path 10 Heat exchange core 11 Header part 11A Header part (first header part)
11B header part (second header part)
13 Core body 20 Casing 61 Radial flow path 66 Circumferential flow path 101 First flow path 102 Second flow path 601 First radial flow path 602 Second radial flow path 661 First circumferential flow path 662 Second Circumferential flow path W0 Side wall W3 Cross wall W5 Partition (second partition)

Claims (15)

A core body including a plurality of axial flow paths extending along the axial direction,
A header portion having a header flow path adjacent to at least one end of the core main body portion in the axial direction and communicating with the plurality of axial flow paths is provided.
The header flow path is
At least one radial flow path extending along the radial direction,
A plurality of circumferential flow paths that branch from any of the radial flow paths and communicate with one or more of the axial flow paths, respectively.
Including
The plurality of circumferential flow paths are
1st circumferential flow path and
A second circumferential flow path located radially inside the first circumferential flow path and arranged in the circumferential direction over a total angular range larger than the first circumferential flow path.
Heat exchange core including. The at least one radial flow path is
The first radial flow path communicating with the first circumferential flow path and
A second radial flow path provided over a radial range occupied by the first radial flow path and a range radially inside the radial range and communicating with the second circumferential flow path.
Including
The second circumferential flow path passes through the first radial flow path in the circumferential direction and extends from the second radial flow path to the opposite side of the first radial flow path. The heat exchange core according to claim 1. The first radial flow path does not communicate with the second circumferential flow path, and the first radial flow path does not communicate with the second circumferential flow path.
The second radial flow path does not communicate with the first circumferential flow path.
The heat exchange core according to claim 2. One or more of the first radial flow paths are arranged.
A plurality of the second radial flow paths are arranged along the circumferential direction.
The heat exchange core according to claim 2 or 3, wherein the number of the first radial flow paths is larger than the number of the second radial flow paths. Two or more of the first radial flow paths are arranged at an equal pitch along the circumferential direction.
Two or more of the second radial flow paths are arranged at an equal pitch along the circumferential direction.
The heat exchange core according to any one of claims 2 to 4. The first circumferential flow path and the second circumferential flow path communicate with the same radial flow path.
The heat exchange core according to claim 1, wherein the second circumferential flow path has a larger number of turns than the first circumferential flow path. Two or more radial flow paths are provided so as to be separated from each other in the circumferential direction.
Between the two radial flow paths adjacent to each other in the circumferential direction, a plurality of the circumferential flow paths branched from one of the two radial flow paths and the two radial flow paths. The heat exchange core according to claim 6, wherein a partition wall is formed to separate the plurality of circumferential flow paths branched from the other of the flow paths in the circumferential direction.
A plurality of the radial flow paths are arranged at an equal pitch along the circumferential direction.
The heat exchange core according to claim 6 or 7. The invention according to any one of claims 1 to 8, wherein the radial flow path is connected to the circumferential flow path located on one side and the other side in the circumferential direction with respect to the radial flow path. Heat exchange core. The heat exchange core according to any one of claims 1 to 9, wherein the plurality of axial flow paths are arranged in an annular shape when viewed from the axial direction. The at least one radial flow path is two or more of the radial flow paths.
The heat exchange core according to any one of claims 1 to 10, wherein the two or more radial flow paths are each provided with an equal flow path cross-sectional area. The heat exchange core according to any one of claims 1 to 11, wherein each of the plurality of axial flow paths is divided into a plurality of sections in the circumferential direction. In the plurality of axial flow paths, the flow path diameters of the plurality of sections are made uniform.
The heat exchange core according to claim 12. The heat exchange core according to any one of claims 1 to 13.
A casing accommodating the heat exchange core and
A heat exchanger equipped with. It is a method of manufacturing a heat exchange core.
A step of forming a core main body including a plurality of axial flow paths extending along the axial direction by laminating molding, and
A step of forming a header portion having a header flow path that is adjacent to at least one end of the core main body portion in the axial direction and communicates with the plurality of flow paths by laminating molding is provided.
The step of forming the header portion is
At least one radial flow path extending along the radial direction,
A plurality of circumferential flow paths that branch from any of the radial flow paths and communicate with one or more of the axial flow paths, respectively.
The header flow path is formed so as to include
The step of forming the header portion is
1st circumferential flow path and
A second circumferential flow path located radially inside the first circumferential flow path and arranged in the circumferential direction over a total angular range larger than the first circumferential flow path.
A method for manufacturing a heat exchange core that forms the plurality of circumferential flow paths so as to include the above.

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