JP2021134983A - 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 each of the radial flow channels. Each of the radial flow channels has a flow passage area in a second position inside the first position in the radial direction smaller than a flow passage area in a first position but.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 each of the radial flow paths and communicate with one or more of the axial flow paths, respectively.
Including
Each of the radial flow paths has a smaller flow path area at the second position inside the radial direction than the first position than the flow path area at the first position.

(2) 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 each of the radial flow paths and communicate with one or more of the axial flow paths, respectively.
Including
At least one opening by the at least one radial flow path is formed on the outer peripheral surface of the heat exchange core in the header portion.
The opening dimension along the axial direction in each of the openings is at least one times the opening dimension along the circumferential direction in each of the openings.

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

(4) 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
In the step of forming the header portion, each of the radial directions is such that the flow path area at the second position inside the radial direction is smaller than the flow path area at the first position. Form a flow path.

(5) 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
The header portion is formed so that at least one opening by the at least one radial flow path is formed on the outer peripheral surface of the heat exchange core in the header portion.
The header portion is formed so that the opening dimension along the axial direction in each of the openings is at least one time the opening dimension along the circumferential direction in each of the openings.

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 figure which shows typically a part in the vicinity of a header part among the side surface of the heat exchange core which concerns on some embodiments, and shows an example of the shape of an opening part. It is a figure which shows typically a part in the vicinity of a header part among the side surface of the heat exchange core which concerns on some embodiments, and shows another example of the shape of an opening part. It is a schematic diagram for demonstrating the change of the flow path area of a radial flow path with respect to the change of a radial position. It is a schematic diagram for demonstrating the change of the flow path area of a radial flow path with respect to the change of a radial position. 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 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 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.

The shape of the opening in the side wall W0 of each radial flow path 61 is rectangular in the examples shown in FIGS. 1 and 2. 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. 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)
Hereinafter, details of the radial flow path according to some embodiments will be described.
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 11B have the same structure. 2 When it is not necessary to distinguish the header portion 1B from the header portion 1B, the description will be given simply by referring to the header portion 11 without adding the letters A and B to the reference numerals.

(About the flow path area of the radial flow path)
In the heat exchange core 10 according to some embodiments, 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 each radial flow path 61 and communicate with one or more axial flow paths 3, respectively.
Each radial flow path 61 has a smaller flow path area Ca2 at the second position P2 inside the first position than the flow path area Ca1 at the first position P1.

Here, the flow path area Ca of the radial flow path 61 is a disconnection of the radial flow path 61 that appears when the radial flow path 61 is cut along a plane orthogonal to its extending direction (that is, the radial direction). It is the area.
Further, the first position P1 and the second position P2 are positions assumed to represent the relative positional relationship in the radial direction in the radial flow path 61, and do not refer to a specific radial position. For example, in the radial flow path 61, when a certain radial position Pa is set as the first position P1, any position radially inside the radial position Pa can be the second position.

In the heat exchange core 10 according to some embodiments, the circumferential dimension of the radial flow path 61 at the second position P2 is larger than the circumferential dimension Lc1 (see FIG. 4) of the radial flow path 61 at the first position P1. By making Lc2 smaller, the flow path area Ca2 at the second position P2 may be smaller than the flow path area Ca1 at the first position P1. Further, by making the axial dimension La2 of the radial flow path 61 at the second position P2 smaller than the axial dimension La1 of the radial flow path 61 at the first position P1 (see FIG. 6), the axial dimension La2 at the first position P1 The flow path area Ca2 at the second position P2 may be smaller than the flow path area Ca1.
That is, if at least one of the circumferential dimension Lc1 or the axial dimension La1 of the radial flow path 61 at the first position P1 is different from the circumferential dimension Lc2 or the axial dimension La2 of the radial flow path 61 at the second position P2. The flow path area Ca2 at the second position P2 may be smaller than the flow path area Ca1 at the first position P1.

In the radial flow path 61, the flow rate of the fluid tends to increase toward the outer region in the radial direction and the pressure loss tends to increase. Therefore, reducing the pressure loss in this region contributes to reducing the pressure loss of the entire heat exchange core 10. ..
According to the above configuration, the flow path area Ca2 at the second position P2 is smaller than the flow path area Ca1 at the first position P1. That is, according to the above configuration, the flow path area Ca1 at the first position P1 is larger than the flow path area Ca2 at the second position P2. As a result, the pressure loss in the radial outer region of the radial flow path 61 can be suppressed, so that the pressure loss of the entire heat exchange core 10 can be suppressed. Therefore, in the axial flow path 3 connected to the radial flow path 61 via the circumferential flow path 66, the difference in the flow rate depending on the radial position can be suppressed, and the heat exchange efficiency in the heat exchange core 10 can be improved. ..

As described above, each radial flow path 61 may have a smaller circumferential dimension Lc2 at the second position P2 than the circumferential dimension Lc1 at the first position P1.
As a result, the flow path area Ca1 at the first position P1 can be made larger than the flow path area Ca2 at the second position P2.
In order to make the flow path area Ca1 at the first position P1 larger than the flow path area Ca2 at the second position P2, as described above, the circumferential direction at the first position P1 is larger than the circumferential dimension Lc2 at the second position P2. There are a method of increasing the dimension Lc1 and a method of increasing the axial dimension La1 at the first position P1 than the axial dimension La2 at the second position P2.
In this case, if the flow path area Ca is changed by mainly changing the circumferential dimension Lc between the first position P1 and the second position P2, the axial dimension La in each radial flow path 61 is changed. Can be suppressed over the entire radial direction. As a result, the axial dimension of the header portion 11 can be suppressed.

As described above, each radial flow path 61 may have an axial dimension La2 at the second position P2 smaller than the axial dimension La1 at the first position P1.
As a result, the flow path area Ca1 at the first position P1 can be made larger than the flow path area Ca2 at the second position P2.
Further, if the flow path area Ca is changed by mainly changing the axial dimension La at the first position P1 and the second position P2, the circumferential dimension Lc in each radial flow path 61 can be obtained. It can be suppressed over the entire radial direction. 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 D1 is suppressed, and the proportion of the region occupied by the circumferential flow path 66 is increased. be able to.

In the header portion 11 according to some embodiments, the flow path area Ca may be configured to gradually decrease toward the inside in the radial direction.
As a result, the radial flow path 61 is formed so that the flow path area Ca gradually increases toward the outside in the radial direction, so that it is possible to avoid the formation of a sudden change portion of the flow path cross-sectional area Ca, and the radial flow can be prevented. The pressure loss on the road 61 can be suppressed.

(About the opening by the radial flow path)
As shown in FIG. 1, in the heat exchange core 10 according to some embodiments, at least one opening 63 by at least one radial flow path 61 is provided on the outer peripheral surface of the heat exchange core 10 in the header portion 11. Is formed. In the heat exchange core 10 according to some embodiments, the total area ΣOa of the opening area Oa of each opening 63 is the total area Sc of the areas Sc of the plurality of circumferential flow paths 66 when viewed from the axial direction D1. It is preferable that it is ΣSc or less.

In the heat exchange core 10 according to some embodiments, the total area ΣOa of the opening area Oa of each opening 63 is the total area ΣSc of the areas Sc of the plurality of circumferential flow paths 66 when viewed from the axial direction D1. When the radial flow path 61 is formed so as to exceed the above, the pressure loss of the fluid flowing through the radial flow path 61 and the circumferential flow path 66 is more affected by the pressure loss in the circumferential flow path 66. Therefore, even if the total area ΣOa of the opening area Oa of each opening 63 is increased so as to exceed the total area ΣSc of the areas Sc of the plurality of circumferential flow paths 66 when viewed from the axial direction D1, the axial direction Compared with the case where the total area ΣSc of the areas Sc of the plurality of circumferential flow paths 66 when viewed from D1 and the total area ΣOa of the opening area Oa of each opening 63 are the same, the radial flow path 61 The effect of suppressing pressure loss in the radial outer region is not so increased.
On the contrary, by increasing the total area ΣOa of the opening area Oa of each opening 63 so as to exceed the total area ΣSc of the areas Sc of the plurality of circumferential flow paths 66 when viewed from the axial direction D1, the radial direction The circumferential dimension Lc and the axial dimension La of the flow path 61 become large. The following effects may occur.
That is, as the circumferential dimension Lc of the radial flow path 61 becomes large, the ratio of the region occupied by the radial flow path 61 in the cross section (second cross section C2) of the header portion 11 when viewed from the axial direction D1 becomes large. As the number increases, the proportion of the region occupied by the circumferential flow path 66 may decrease.
Further, as the axial dimension La of the radial flow path 61 becomes larger, the axial dimension of the header portion 11 may become larger.
According to the heat exchange core 10 according to some embodiments, the influence on the region occupied by the circumferential flow path 66 in the cross section (second cross section C2) of the header portion 11 when viewed from the axial direction D1 and the header. It is possible to effectively suppress the pressure loss in the radial outer region of the radial flow path 61 while suppressing the influence on the axial dimension of the portion 11.

(About the shape of the opening)
FIG. 8 is a diagram schematically showing a part of the side surface of the heat exchange core 10 according to some embodiments in the vicinity of the header portion 11, and shows an example of the shape of the opening 63.
FIG. 9 is a diagram schematically showing a part of the side surface of the heat exchange core 10 according to some embodiments in the vicinity of the header portion 11, and shows another example of the shape of the opening 63. ..

In the heat exchange core 10 according to some embodiments, the flow rate of the fluid is relatively large in the vicinity of the opening 63 of the radial flow path 61, and the pressure loss tends to be relatively large. It is desirable to increase the opening area. However, if the radial flow path 61 is widened in the circumferential direction D2, it may affect the flow of the fluid in the axial flow path 3, so it is desirable to suppress the expansion of the flow path width in the circumferential direction D2. Therefore, in the radial flow path 61, it is preferable to widen the flow path width in the axial direction D1.
Therefore, in the heat exchange core 10 according to some embodiments, the shape of the opening 63 is set as follows.
That is, in the heat exchange core 10 according to some embodiments, as shown in FIGS. 8 and 9, the opening dimension AL1 along the axial direction D1 at each opening 63 is the circumferential direction at each opening 63. The opening size along D2 is at least one times the opening size AL2 (1.0 × AL2 ≦ AL1).
As a result, the opening dimension AL2 along the circumferential direction D2 at each opening 63 can be suppressed. Therefore, since the dimension of the radial flow path 61 along the circumferential direction D2 can be suppressed, the area occupied by the radial flow path 61 in the cross section (second cross section C2) of the header portion 11 when viewed from the axial direction D1. The ratio can be suppressed and the ratio of the region occupied by the circumferential flow path 66 can be increased.

For example, in the heat exchange core 10 shown in FIG. 8, the opening 63 has a rectangular shape when viewed from the outside in the radial direction. Further, for example, in the heat exchange core 10 shown in FIG. 9, the end portion 64 of the opening 63 along the axial direction is located outside the radial flow path 61 along the axial direction D1 when viewed from the outside in the radial direction. It is formed so that the dimension in the circumferential direction D2 becomes smaller as it goes toward it. That is, in the heat exchange core 10 according to some embodiments, the radial flow path 61 is radially along the axial direction D1 at at least one of the two end portions 64 along the axial direction D1. It may be formed so that the dimension AL2 in the circumferential direction D2 becomes smaller toward the outside of the flow path 61.
As a result, for example, as will be described later, when the heat exchange core 10 is modeled by laminated modeling, the end 64 along the axial direction D1 in the radial flow path 61 overhangs when the axial direction D1 is the laminated direction. It becomes difficult to become an area. This makes it possible to simplify or eliminate the step of shaping the support for shaping the overhang region and the step of removing the shaped support.

(About the change in the flow path area of the radial flow path with respect to the change in the radial position)
FIG. 10 is a schematic view for explaining a change in the flow path area Ca of the radial flow path 61 with respect to a change in the radial position, and is a view of the heat exchange core 10 viewed along the axial direction D1. ..
For convenience of explanation, FIG. 10 shows a schematic shape of the first radial flow path 61A, which is the radial flow path 61 in the first header portion 11A, and a second radial flow path 61 in the second header portion 11B. The schematic shape of the radial flow path 61B is superimposed along the axial direction D1. For convenience of illustration, in FIG. 10, the schematic shape of the first radial flow path 61A is shown by a broken line, and the schematic shape of the second radial flow path 61B is shown by a two-dot chain line.
FIG. 11 is a schematic view for explaining a change in the flow path area Ca of the radial flow path 61 with respect to a change in the radial position, and is a view of the heat exchange core 10 viewed along the radial direction. In FIG. 11, the schematic shape of the first radial flow path 61A and the typical shape of the second radial flow path 61B are shown by a two-dot chain line.

In the heat exchange core 10 according to some embodiments, as described above, the flow rate of the fluid is relatively large in the vicinity of the opening 63 of the radial flow path 61, so that the dynamic pressure is relatively large. On the other hand, in the vicinity of the center of the cylinder of the radial flow path 61, the flow rate is smaller than that in the vicinity of the opening 63, so that the dynamic pressure is much smaller than that in the vicinity of the opening 63.
When the difference in dynamic pressure due to the difference in the radial position becomes large to some extent or more, the deviation between the axial flow path 3 near the opening 63 (that is, the outside in the radial direction) and the axial flow path 3 near the center becomes large, and heat becomes large. There is a risk that the performance of the replacement core 10 will deteriorate.
Since the deviation tends to increase as the dynamic pressure increases, the deviation tends to increase in a fluid having a high density.
Therefore, it is preferable that the higher the density of the fluid, the lower the flow velocity in the vicinity of the opening 63 by increasing the area increase rate Rca described later.

Also, in general, the density of the fluid depends on the temperature. Further, in general, the change in density with temperature is larger in gas than in liquid.
Therefore, when the temperature of the fluid changes due to the circulation of the heat exchange core 10, the radial flow path 61 in the header portion 11 located on the upstream side of the fluid flow and the header portion located on the downstream side of the fluid flow. In some cases, it may be preferable to make the area increase rate Rca, which will be described later, different from that of the radial flow path 61 in 11.

Therefore, in the heat exchange core 10 according to some embodiments, the shape of the radial flow path 61 is set as follows.
That is, in the heat exchange core 10 according to some embodiments, the area increase rate Rca for the flow path area Ca that increases from the inside to the outside in the radial direction in at least one radial flow path 61 is the first. At least one radial flow path 61 (first radial flow path 61A) in the header portion 11A and at least one radial flow path 61 (second radial flow path 61B) in the second header portion 11B are different. ..
Here, the area increase rate Rca determines the difference (Ca1-Ca2) between the flow path area Ca1 at the first position P1 and the flow path area Ca2 at the second position P2 in the radial direction between the first position P1 and the second position P2. It is the value divided by the difference in the position of.

In order to make the area increase rate Rca different between the first radial flow path 61A and the second radial flow path 61B, for example, as shown in FIG. 10, the circumference increases from the inside to the outside in the radial direction. The dimensional increase rate Rlc for the directional dimension Lc may be different between the first radial flow path 61A and the second radial flow path 61B. Further, in order to make the area increase rate Rca different between the first radial flow path 61A and the second radial flow path 61B, for example, as shown in FIG. 11, an axis that increases from the inside to the outside in the radial direction. The dimension increase rate Rla for the directional dimension La may be different between the first radial flow path 61A and the second radial flow path 61B.
That is, by making at least one of the dimension increase rate Rlc for the circumferential dimension Lc and the dimension increase rate Rla for the axial dimension La different between the first radial flow path 61A and the second radial flow path 61B. The area increase rate Rca may be different between the first radial flow path 61A and the second radial flow path 61B.

In the heat exchange core 10 according to some embodiments, the difference in static pressure between the first header portion 11A and the second header portion 11B at an arbitrary radial position of the radial flow path 61 is set to the radial position. It is desirable to keep it constant regardless.
When the fluid flowing through the heat exchange core 10 is, for example, a gas, as described above, the rate of change in density due to a change in temperature tends to be larger than that in the case of a liquid. Therefore, if the area increase rate Rca is the same in the first radial flow path 61A and the second radial flow path 61B, the above-mentioned difference in static pressure may be significantly different depending on the radial position.
According to the above configuration, since the area increase Rca rate differs between the first radial flow path 61A and the second radial flow path 61B, it is possible to suppress the difference in static pressure described above depending on the radial position. ..

(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. 12 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 of manufacturing the heat exchange core 10 according to some of the above-described embodiments, the core main body portion 13 including a plurality of axial flow paths 3 extending along the axial direction D1 is formed by laminated molding. A header that forms 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 D1 and communicating with a plurality of axial flow paths 3 by the forming step S1 and laminating molding. A portion forming step S3 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 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, in the header portion forming step S3, the flow path area Ca2 at the second position P2 inside the first position P1 is smaller than the flow path area Ca1 at the first position P1. The radial flow path 61 may be formed.
Further, in the header portion forming step S3, the header portion 11 is formed so that at least one opening 63 by at least one radial flow path 61 is formed on the outer peripheral surface of the heat exchange core 10 in the header portion 11. At the same time, the header portion 11 may be formed so that the opening size AL1 along the axial direction D1 in each opening 63 is at least one times the opening size AL2 along the circumferential direction in each opening 63. ..
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 main body 13 includes a plurality of axial flow paths 3 extending along the axial direction D1. 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 D1 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 each radial flow path 61 and communicate with one or more axial flow paths 3, respectively.
Each of the radial flow paths 61 has a smaller flow path area Ca2 at the second position P2 inside the first position P1 than the flow path area Ca1 at the first position P1.

In the radial flow path 61, the flow rate of the fluid tends to increase toward the outer region in the radial direction and the pressure loss tends to increase. Therefore, reducing the pressure loss in this region contributes to the reduction of the pressure loss of the entire heat exchange core 10. do.
According to the configuration of (1) above, the flow path area Ca2 at the second position P2 inside the first position P1 is smaller than the flow path area Ca1 at the first position P1. That is, according to the configuration of (1) above, the flow path area Ca1 at the first position P1 on the outer side in the radial direction is larger than the flow path area Ca2 at the second position P2. As a result, the pressure loss in the radial outer region of the radial flow path 61 can be suppressed, so that the pressure loss of the entire heat exchange core 10 can be suppressed. Therefore, in the axial flow path 3 connected to the radial flow path 61 via the circumferential flow path 66, the difference in the flow rate depending on the radial position can be suppressed, and the heat exchange efficiency in the heat exchange core 10 can be improved. ..

(2) In some embodiments, in the configuration of (1) above, each radial flow path 61 has a circumferential dimension Lc2 at the second position P2 rather than a circumferential dimension Lc1 at the first position P1. Is small.

According to the configuration of (2) above, in each radial flow path 61, the circumferential dimension Lc2 at the second position P2 is made smaller than the circumferential dimension Lc1 at the first position P1, that is, the second position P2. By making the circumferential dimension LC1 at the first position P1 larger than the circumferential dimension LC2 in the above position, the flow path area Ca1 at the first position P1 can be made larger than the flow path area Ca2 at the second position P2.
If the flow path area Ca is changed by mainly changing the circumferential dimension Lc between the first position P1 and the second position P2, the diameter La of the axial direction D1 in each radial flow path 61 can be changed. It can be suppressed throughout the direction. As a result, the axial dimension of the header portion 11 can be suppressed.

(3) In some embodiments, in the configuration of (1) or (2) above, each radial flow path 61 is in the axial direction at the second position P2 rather than the axial dimension La1 at the first position P1. The dimension La2 is smaller.

According to the configuration of (3) above, in each radial flow path 61, the axial dimension La2 at the second position P2 is made smaller than the axial dimension La1 at the first position P1, that is, the second position P2. By making the axial dimension La1 at the first position P1 larger than the axial dimension La2 in the above position, the flow path area Ca1 at the first position P1 can be made larger than the flow path area Ca2 at the second position P2.
If the flow path area Ca is changed by mainly changing the axial dimension La between the first position P1 and the second position P2, the circumferential dimension Lc in each radial flow path 61 can be changed in the radial direction. It can be suppressed throughout along. 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 D1 is suppressed, and the proportion of the region occupied by the circumferential flow path 66 is increased. be able to.

(4) In some embodiments, in any of the configurations (1) to (3), the flow path area Ca gradually decreases toward the inside in the radial direction.

According to the configuration of (4) above, the radial flow path 61 is formed so that the flow path area Ca gradually increases toward the outside in the radial direction, so that a sudden change portion of the flow path cross-sectional area Ca is formed. Can be avoided, and pressure loss in the radial flow path 61 can be suppressed.

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

According to the configuration of (5) above, the influence on the area occupied by the circumferential flow path 66 in the cross section (second cross section C2) of the header portion 11 when viewed from the axial direction D1 and the axial direction of the header portion 11 It is possible to effectively suppress the pressure loss in the radial outer region of the radial flow path 61 while suppressing the influence on the dimensions.

(6) In some embodiments, in any of the configurations (1) to (5) above, at least one radial flow path 61 is formed on the outer peripheral surface of the heat exchange core 10 in the header portion 11. One opening 63 is formed. The opening size AL1 along the axial direction D1 at each opening 63 is at least one times the opening size AL2 along the circumferential direction D2 at each opening 63.

According to the configuration of (6) above, the opening dimension AL2 along the circumferential direction D2 in each opening 63 can be suppressed. As a result, the dimensions of the radial flow path 61 along the circumferential direction D2 can be suppressed, so that the area occupied by the radial flow path 61 in the cross section (second cross section C2) of the header portion 11 when viewed from the axial direction D1. It is possible to suppress the ratio of the above and increase the ratio of the region occupied by the circumferential flow path 66.

(7) In some embodiments, in any of the configurations (1) to (6) above, at least one radial flow path 61 is at least one of the two ends 64 along the axial direction D1. One end 64 is formed so that the dimension of the circumferential direction D2 becomes smaller toward the outside of the radial flow path 61 along the axial direction D1.

According to the configuration of (7) above, for example, when the heat exchange core 10 is modeled by laminated modeling, the end portion 64 along the axial direction D1 in the radial flow path 61 when the axial direction D1 is the laminated direction. Is less likely to become an overhang area. This makes it possible to simplify or eliminate the step of shaping the support for shaping the overhang region and the step of removing the shaped support.

(8) In some embodiments, in any of the configurations (1) to (7) above, the header portion 11 is a first header portion adjacent to one end of the core body portion 13 in the axial direction D1. Includes 11A and a second header 11B adjacent to the other end of the core body 13 in the axial direction D1. The area increase rate Rca for the flow path area Ca that increases from the inside to the outside in the radial direction in at least one radial flow path 61 is the at least one radial flow path 61 and the first in the first header portion 11A. It is different from at least one radial flow path 61 in the 2 header portion 11B.

According to the configuration of (8) above, the area increase rate Rca is different between the radial flow path 61 in the first header portion 11A and the radial flow path 61 in the second header portion 11B, so that the above-mentioned difference in static pressure is obtained. Can be suppressed from being different depending on the radial position.

(9) 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 main body 13 includes a plurality of axial flow paths 3 extending along the axial direction D1. 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 D1 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 each radial flow path 61 and communicate with one or more axial flow paths 3, respectively.
At least one opening 63 is formed on the outer peripheral surface of the heat exchange core 10 in the header portion 11 by at least one radial flow path 61.
The opening size AL1 along the axial direction D1 at each opening 63 is at least one times the opening size AL2 along the circumferential direction D2 at each opening 63.

According to the configuration of (9) above, the opening dimension AL2 along the circumferential direction D2 in each opening 63 can be suppressed. As a result, the dimensions of the radial flow path 61 along the circumferential direction D2 can be suppressed, so that the area occupied by the radial flow path 61 in the cross section (second cross section C2) of the header portion 11 when viewed from the axial direction D1. It is possible to suppress the ratio of the above and increase the ratio of the region occupied by the circumferential flow path 66.

(10) In some embodiments, in the configuration of (9) above, the total area ΣOa of the opening area Oa of each opening 63 is the plurality of circumferential flow paths 66 when viewed from the axial direction D1. The total area of the area Sc is ΣSc or less.

According to the configuration of (10) above, the influence on the area occupied by the circumferential flow path 66 in the cross section (second cross section C2) of the header portion 11 when viewed from the axial direction D1 and the axial direction of the header portion 11 It is possible to effectively suppress the pressure loss in the radial outer region of the radial flow path 61 while suppressing the influence on the dimensions.

(11) In some embodiments, in the configuration of (9) or (10) above, at least one radial flow path 61 is at least one end of two ends 64 along axial D1. The portion 64 is formed so that the dimension of the circumferential direction D2 becomes smaller toward the outside of the radial flow path 61 along the axial direction D1.

According to the configuration of (11) above, for example, when the heat exchange core 10 is modeled by laminated modeling, the end portion 64 along the axial direction D1 in the radial flow path 61 when the axial direction D1 is the laminated direction. Is less likely to become an overhang area. This makes it possible to simplify or eliminate the step of shaping the support for shaping the overhang region and the step of removing the shaped support.

(12) In some embodiments, in any of the configurations (1) to (11) above, the plurality of axial flow paths 3 are arranged in an annular shape when viewed from the axial direction D1.

According to the configuration of (12) above, the stress acting by the pressure of the fluid or the like can be uniformly dispersed throughout the heat exchange core 10.

(13) In some embodiments, in any of the configurations (1) to (12) above, the plurality of axial flow paths 3 are each divided into a plurality of compartments S in the circumferential direction D2.

According to the configuration of (13) above, the heat transfer efficiency can be improved by the existence of the wall that divides the axial flow path 3. The wall can improve the rigidity and strength of the heat exchange core 10, especially in the radial direction.

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

According to the configuration of (14) 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.

(15) 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 (14) above, and a casing 20 accommodating the heat exchange core 10. Be prepared.

According to the configuration of (15) above, the heat exchanger 1 can be made relatively small and the heat exchange efficiency can be improved.

(16) The method for manufacturing the heat exchange core 10 according to at least one embodiment of the present disclosure is the method for manufacturing the heat exchange core 10, and a plurality of axial flows extending along the axial direction D1 by laminated molding. By the core main body forming step S1 for forming the core main body 13 including the path 3 and the laminated molding, the core main body 13 is adjacent to at least one end in the axial direction D1 and communicates with a plurality of axial flow paths 3. The header portion forming step S3 for forming the header portion 11 having the header flow path 6 to be formed 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 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. In the header portion forming step S3, each radial direction is such that the flow path area Ca2 at the second position P2 inside the first position P1 is smaller than the flow path area Ca1 at the first position P1. The flow path 61 is formed.

According to the method (16) 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.

(17) The method for manufacturing the heat exchange core 10 according to at least one embodiment of the present disclosure is the method for manufacturing the heat exchange core 10, and a plurality of axial flows extending along the axial direction D1 by laminated molding. By the core main body forming step S1 for forming the core main body 13 including the path 3 and the laminated molding, the core main body 13 is adjacent to at least one end in the axial direction D1 and communicates with a plurality of axial flow paths 3. The header portion forming step S3 for forming the header portion 11 having the header flow path 6 to be formed 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 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. In the header portion forming step S3, the header portion 11 is formed on the outer peripheral surface of the heat exchange core 10 in the header portion 11 so that at least one opening 63 by at least one radial flow path 61 is formed. The header portion 11 is formed so that the opening size AL1 along the axial direction D1 in each opening 63 is at least one times the opening size AL2 along the circumferential direction D2 in each opening 63.

According to the method (17) 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 1st header part 11B 2nd header part 13 Core body part 61 Radial flow path 63 Opening 66 Circumferential flow path

Claims (17)

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 each of the radial flow paths and communicate with one or more of the axial flow paths, respectively.
Including
Each of the radial flow paths is a heat exchange core in which the flow path area at the second position inside the radial direction is smaller than the flow path area at the first position. The heat exchange core according to claim 1, wherein each of the radial flow paths has a smaller circumferential dimension at the second position than a circumferential dimension at the first position. The heat exchange core according to claim 1 or 2, wherein each of the radial flow paths has a smaller axial dimension in the second position than an axial dimension in the first position. The heat exchange core according to any one of claims 1 to 3, wherein the flow path area gradually decreases toward the inside in the radial direction. At least one opening by the at least one radial flow path is formed on the outer peripheral surface of the heat exchange core in the header portion.
The method according to any one of claims 1 to 4, wherein the total area of the opening area of each of the openings is equal to or less than the total area of the areas of the plurality of circumferential flow paths when viewed from the axial direction. Heat exchange core. At least one opening by the at least one radial flow path is formed on the outer peripheral surface of the heat exchange core in the header portion.
The aspect of any one of claims 1 to 5, wherein the opening dimension along the axial direction in each of the openings is at least one times the opening dimension along the circumferential direction in each of the openings. Heat exchange core. The at least one radial flow path has a circumferential dimension toward the outside of the radial flow path along the axial direction at at least one end of two ends along the axial direction. The heat exchange core according to any one of claims 1 to 6, which is formed so as to be small. The header portion includes a first header portion adjacent to the one end portion of the core main body portion in the axial direction and a second header portion adjacent to the other end portion of the core main body portion in the axial direction. Including
The area increase rate for the flow path area that increases from the inside to the outside in the radial direction in the at least one radial flow path is the same as that of the at least one radial flow path in the first header portion. The heat exchange core according to any one of claims 1 to 7, which is different from the at least one radial flow path in the second header portion. 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 each of the radial flow paths and communicate with one or more of the axial flow paths, respectively.
Including
At least one opening by the at least one radial flow path is formed on the outer peripheral surface of the heat exchange core in the header portion.
A heat exchange core in which the opening dimension along the axial direction in each of the openings is at least one time the opening dimension along the circumferential direction in each of the openings. The heat exchange core according to claim 9, wherein the total area of the opening area of each of the openings is equal to or less than the total area of the areas of the plurality of circumferential flow paths when viewed from the axial direction. The at least one radial flow path has a circumferential dimension toward the outside of the radial flow path along the axial direction at at least one end of two ends along the axial direction. The heat exchange core according to claim 9 or 10, which is formed so as to be small. The heat exchange core according to any one of claims 1 to 11, wherein the plurality of axial flow paths are arranged in an annular shape when viewed from the axial direction. The heat exchange core according to any one of claims 1 to 12, wherein each of the plurality of axial flow paths is divided into a plurality of compartments 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 13. The heat exchange core according to any one of claims 1 to 14.
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 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
In the step of forming the header portion, each of the radial directions is such that the flow path area at the second position inside the radial direction is smaller than the flow path area at the first position. A method for manufacturing a heat exchange core that forms a flow path. 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
The header portion is formed so that at least one opening by the at least one radial flow path is formed on the outer peripheral surface of the heat exchange core in the header portion.
Manufacture of a heat exchange core that forms the header portion so that the opening dimension along the axial direction in each of the openings is at least one time the opening dimension along the circumferential direction in each of the openings. Method.

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