Heat exchanger core, heat exchanger and method for manufacturing heat exchanger core

Abstract

Heat exchange core, which performs heat exchange between a first fluid and a second fluid, wherein the heat exchange core (10, 40) comprises: a circular first cross-section (C1) in which a first flow path group (G1) for the first fluid and a second flow path group (G2) for the second fluid are positioned, wherein first flow paths (101) contained in the first flow path group (G1) and second flow paths (102) contained in the second flow path group (G2) are arranged annularly in the first cross-section (C1), the first flow path group (G1) and the second flow path group (G2) are arranged concentrically in the first cross-section (C1), and each of the first flow paths (101) and second flow paths (102) is subdivided into a plurality of sections (S) in a circumferential direction of the heat exchange core (10, 40).wherein the sections (S) of each of the first flow paths (101) and the second flow paths (102) are formed in a spiral shape around an axis (A) of the heat exchange core (10, 40), the sections (S) of one of the first flow paths (101) or second flow paths (102) extend in a clockwise direction (R1) when viewed from one end face (D11) in an axial direction (D1) of the heat exchange core (10, 40), and the sections (S) of another of the first flow paths (101) and second flow paths (102) extend in a counterclockwise direction (R2) when viewed from one end face (D11) in the axial direction (D1).

Description

Technical field

[0001] The present disclosure relates to a heat exchanger core that performs heat exchange between a first fluid and a second fluid, a heat exchanger comprising the heat exchanger core and a housing, and a method for manufacturing the heat exchanger core. background

[0002] A heat exchanger is used in a wide range of industrial fields, for example in an air conditioning system, a freezer, a gas turbine, a chemical factory such as a CO2 recovery system, and transport machinery.

[0003] While various heat exchangers are used, a plate heat exchanger is known that comprises a stacked body of plates and alternates between a flow path for a first fluid and a flow path for a second fluid in the stacking direction of the plates. Each flow path is formed between two adjacent plates by a gasket made of a rubber material, which is located at a peripheral edge of each plate. The first fluid and the second fluid flow between the plates from a direction orthogonal to the plates. The first fluid flows sequentially through the flow path between the plates from one side to the other in the stacking direction of the plates. The first fluid and the second fluid exchange heat across the plates.

[0004] Additionally, a heat exchanger is known in which a heat exchange core, comprising a stacked body of plates, is housed in a cylindrical casing (Patent Reference 1). Patent Reference 1 specifies a cross-sectional shape of the heat exchange core that is circular, following the cross-sectional shape of the casing. The area of ​​each of the plates, arranged vertically such that it divides the cross-section of the heat exchange core, is large at its center in the vertical direction and small at its top and bottom ends.

[0005] In patent literature 1, the first and second fluids exchange heat as they flow through flow paths formed alternately between the plates in an up-down direction, along the plates in an axial direction of the housing. The second fluid flows between the plates from a first end in an axial direction of the heat exchanger core and flows out from a second end in the axial direction of the heat exchanger core to the outside of the heat exchanger core. On the other hand, both inlet and outlet passages for the third fluid are positioned on the side walls of the heat exchanger core. The first fluid flows between the plates from a direction orthogonal to the axial direction of the heat exchanger core through the inlet passages positioned near the second end of the heat exchanger core. The third fluid then flows out through the outlet passages, which are positioned near the first end of the heat exchanger core.

[0006] According to patent literature 1, the sizes of the inlet and outlet openings for the first fluid, which are arranged on the side walls of the heat exchanger core, are differentiated based on the surface areas of the plates. As a result, a constant flow rate of the first fluid per unit heat transfer area is achieved, enabling highly efficient heat exchange. List of citations, patent literature

[0007] Patent literature 1: JP 3406896 B2 Summary of the invention: Technical problem

[0008] The gaskets used in the plate heat exchanger described above seal the spaces between the plates.

[0009] Therefore, during maintenance performed to prevent fluid leakage, inspection, replacement, and similar tasks involving seals are particularly problematic. To reduce maintenance costs, it is desirable to avoid using seals altogether.

[0010] On the other hand, according to patent literature 1, since the plates which differ in their heat transfer surface are arranged asymmetrically around an axial center, stress concentration easily occurs in the heat exchange core.

[0011] One purpose of the present disclosure is to achieve the balancing of stress in the heat exchange core. Problem solving

[0012] A heat exchanger core according to the present disclosure performs heat exchange between a first fluid and a second fluid and includes a circular first cross-section in which a first flow path group for the first fluid and a second flow path group for the second fluid are positioned. The first flow paths contained in the first flow path group and the second flow paths contained in the second flow path group are arranged annularly in the first cross-section. The first flow path group and the second flow path group are arranged concentrically in the first cross-section. Each of the first and second flow paths is subdivided into a plurality of sections in the circumferential direction of the heat exchanger core.

[0013] A heat exchanger according to the present disclosure comprises the heat exchanger core described above and a housing with a circular cross-section that accommodates the heat exchanger core. Two or more transverse paths are distributed in the circumferential direction of the heat exchanger core. A communication space, which allows the two or more transverse paths outside the heat exchanger core to communicate, is provided around the heat exchanger core within the housing.

[0014] In a method for manufacturing a heat exchanger core that performs heat exchange between a first fluid and a second fluid according to the present disclosure, the heat exchanger core comprises a circular first cross-section in which a first flow path group for the first fluid and a second flow path group for the second fluid are positioned, the first flow paths contained in the first flow path group and the second flow paths contained in the second flow path group are arranged annularly in the first cross-section, and the first and second flow path groups as a whole are arranged concentrically in the first cross-section. The method includes forming the first and second flow path groups by additive manufacturing using a metal material. Advantageous effects of the invention

[0015] According to the present disclosure, based on the configuration of the heat exchanger core, which includes the first and second flow path groups arranged concentrically, the stress can be uniformly distributed across the entire heat exchanger core. Additionally, the flow state of the first fluid and the flow state of the second fluid are made uniform across the entire heat exchanger core, while the heat transfer surface area of ​​the first and second fluids is largely ensured. Therefore, the heat exchange can be carried out efficiently.

[0016] Accordingly, it is possible to improve reliability by preventing damage to the heat exchanger core caused by stress concentration, and to achieve the same heat exchange performance with a smaller heat exchanger core. List of characters Fig. Figure 1 is a perspective exploded view illustrating a heat exchanger core and a housing contained in a heat exchanger according to an embodiment of the present disclosure. Fig. 2 is a partial cross-sectional view showing the housing of the in Fig. 1 illustrated heat exchanger and the heat exchanger core which is included in the housing. Fig. 3A is a cross-sectional view along line IIIa-IIIa in Fig. 2 (first cross-section of the heat exchanger core), and illustrates a first flow path group and a second flow path group. Fig. 3B is a partially enlarged view of Fig. 3A and illustrations of partitions (W2) are shown in other drawings than Fig. 3B omitted. Fig. 4 is a cross-sectional view along line IV-IV in Fig. 2 (second cross-section of heat exchanger core). Fig. 5 is a cross-sectional view along line VV in Fig. 2 and Fig. 6 (third cross-section of heat exchanger core). Fig. Figure 6 is a schematic diagram illustrating the flow of both a first fluid and a second fluid. Fig. Figure 7 is a cross-sectional view illustrating part of a heat exchanger core according to a modification of the present disclosure. Fig. Figure 8 is a perspective view illustrating a heat exchanger core according to another modification of the present disclosure. Fig. 9A is a diagram showing a cross-sectional view along line IXA-IXA of the Fig. 8 illustrated heat exchanger core, and shapes of sections of the second flow paths illustrated. Fig. 9B is a diagram showing the interior of an alternating long and short dashed line in which Fig. 9A illustrated cross-sections and shapes of sections of the first river paths. Fig. Figure 10 is a diagram illustrating a modification relating to the arrangement of partitions.

[0017] One embodiment is described below with reference to the attached drawings. (Schematic configuration of heat exchanger)

[0018] A heat exchanger 1, which is in Fig. 1 and Fig. Figure 2 illustrates a heat exchanger core 10 and a housing 20 which accommodates the heat exchanger core 10.

[0019] The heat exchanger 1 can be installed, for example, in a gas turbine, a chemical plant such as a CO2 recovery unit, and a device not illustrated, such as an air conditioning unit and a freezer, and performs heat exchange between a first fluid and a second fluid. The temperature of the first fluid is relatively high, while the temperature of the second fluid is relatively low. Conversely, the temperature of the first fluid can be relatively low and the temperature of the second fluid can be relatively high. (Configuration of heat exchanger core)

[0020] As in Fig. 1 and Fig. 3A, which shows a cross-sectional view along line IIIa-IIIa in Fig. Figure 2 illustrates that the heat exchanger core 10 includes a first flow path group G1 and a second flow path group G2, which are arranged concentrically.

[0021] The heat exchanger 1 includes a first cross-section C1, which is in Fig. Figure 3A illustrates a second cross-section C2, which is in Fig. 4 is illustrated, and a third cross-section C3, which is in Fig. Figure 5 illustrates this. Each of these cross-sections C1 to C3 has a circular shape. The overall outer shape of the heat exchanger core 10 is cylindrical. The heat exchanger core 10 includes partitions W1, arranged concentrically to divide the first flow path group G1 and the second flow path group G2, and a side wall W0, located at an outer periphery of the heat exchanger core 10.

[0022] The heat exchanger core 10 has a shape symmetrical around a center point of each of the cross-sections C1 to C3, not only in its external shape but also in its overall shape. This can efficiently contribute to stress balancing and heat exchange compensation.

[0023] The first flow path group G1 is for the third fluid, and the second flow path group G2 is for the second fluid. In each of the drawings, the first flow path group G1 is illustrated with a hatching pattern.

[0024] The second river trail group G2 extends from one end 10A ( Fig. 1) to the other end 10B ( Fig. 1) in an axial direction D1 of the heat exchanger core 10. The axial direction D1 is orthogonal to the cross-sections C1 to C3.

[0025] In each of the drawings, a flow of the first fluid is illustrated by a solid arrow, and a flow of the second fluid is illustrated by a dashed arrow.

[0026] The first river paths 101, which are contained in the first river path group G1, are arranged in a ring in the Fig. The first cross-section C1 is illustrated in Figure 3A. Second flow paths 102, which are contained in the second flow path group G2, are arranged similarly. The first fluid, which flows through the first flow path group G1, and the second fluid, which flows through the second flow path group G2, exchange heat by indirect contact through the dividing walls W1, which are shown by the thick line in Figure 3A. Fig. 3A are illustrated.

[0027] As in Fig. Figure 3A illustrates that the plurality of first flow paths 101 and the plurality of second flow paths 102 are preferably stacked alternately over, for example, several ten layers in a radial direction of the heat exchange core 10.

[0028] The first flow paths 101 and the second flow paths 102 are preferably arranged over the entire radial direction of the heat exchange core 10, namely up to the vicinity of an axial center of the heat exchange core 10.

[0029] In Fig. 3A, Fig. 3B, Fig. 4 and Fig. Figure 5 illustrates only some of the first river paths 101 and the second river paths 102. Illustrations of the first river paths 101 and the second river paths 102 in an area marked by a symbol “…” are omitted.

[0030] As in the present embodiment, the arrangement of the first flow paths 101 and the second flow paths 102 across the entirety of the heat exchange core 10 in the radial direction enables the entire heat exchange core 10 to contribute to heat exchange.

[0031] The heat exchanger core 10 can have a constant cross-sectional shape corresponding to the first cross-section C1 ( Fig. 3A) in an area between line IV-IV and line IVx-IVx, illustrated in Fig. 2, corresponds. In the present embodiment, the first fluid and the second fluid flow in opposite directions along the axial direction D1 within this region, namely within the region from the vicinity of one end 10A to the vicinity of the other end 10B of the heat exchanger core 10. In other words, the first fluid and the second fluid form counterflows (full counterflows) over substantially the entire axial direction D1 of the heat exchanger core 10, except with respect to both ends.

[0032] The first fluid and the second fluid can flow in the same direction along the axial direction D1. In this case, the first fluid and the second fluid form parallel current flows.

[0033] The heat exchanger core 10 has a suitable dimension in both the axial direction D1 and the radial direction, a flow path cross-sectional area, the stacked number of flow paths 101 and 102 and the like, taking into account necessary heat exchange capacity, stress and the like.

[0034] As in Fig. As illustrated in Figure 3B, each of the first flow paths 101 and the second flow paths 102 is preferably subdivided into a plurality of sections S by partitions W2 in a circumferential direction D2 of the heat exchanger core 10. The installation of the partitions W2 makes it possible to improve the rigidity and strength, particularly in the radial direction, against the pressure of the fluids.

[0035] Furthermore, if each of the first flow paths 101 and the second flow paths 102 is subdivided into sections S by the partitions W2, the surface areas of the flow paths coming into contact with the fluids are increased, so that heat transfer efficiency can be improved.

[0036] The reduction in diameter of each of the flow paths 101 and 102 by the partitions W2 makes it possible to reduce the stress generated in the circumferential direction of the flow paths 101 and 102 and to reduce the thickness of the partitions W1 between the respective flow paths 101 and 102. Accordingly, it is possible to reduce thermal resistance through the partitions W1 and to achieve an improvement in heat transfer efficiency as well as a smaller and lighter heat exchanger 1.

[0037] The sections S preferably all have the same flow path diameter and are preferably arranged around the entire circumference of the heat exchanger core 10. Furthermore, all sections S arranged from the outermost periphery of the axial center of the heat exchanger core 10 have the same flow path diameter. As a result, a flow condition such as frictional loss is made uniform between all sections S, and the heat transfer coefficient can be made uniform accordingly between all sections S. In addition, the stress acting on the heat exchanger core 10 is uniformly distributed in the entire plane direction of the cross-section of the heat exchanger core 10, which makes it possible to equalize the stress.

[0038] It should be noted that the heights (dimension in the radial direction) of the sections S are not necessarily the same in the layers of the heat exchanger core 10.

[0039] The “flow path diameter” in the present specification corresponds to an equivalent diameter D derived from the following expression (1), D=4A / L where A is a cross-sectional area of ​​each of the sections S, and L is a length (perimeter) of each of the sections S in the circumferential direction D2.

[0040] The heat transfer coefficient is the inverse of the flow path diameter. Therefore, it is desirable to assign the appropriate flow path diameter to each of the sections S based on this.

[0041] A required thickness is assigned to each of the partitions W2 depending on the pressure resistance of the flow paths. If the flow path diameter of each of the sections S is increased towards the outside in the radial direction of the heat exchanger core 10 and the flow path cross-sectional area is increased towards the outside in the radial direction, unlike the arrangement of the Fig. In section 3B, illustrated in section S, it is necessary to increase the thickness of each of the partition walls W2 towards the outside in the radial direction with regard to the relationship with pressure resistance. The heat transfer coefficient is reduced with an increased flow path diameter. This necessitates an enlargement of heat exchanger 1.

[0042] Accordingly, if the heat exchanger core 10 is designed such that the flow path cross-sectional areas of the sections S in the layers of the heat exchanger core 10 are made equal, it is possible to ensure a predetermined heat transfer performance and pressure resistance while avoiding the enlargement of the heat exchanger 1.

[0043] The heat exchanger core 10, together with the partitions W2, can be integrally formed by additive manufacturing or similar processes, using a metal material with characteristics suitable for the fluids, such as stainless steel or an aluminum alloy. Additive manufacturing can produce a product in which two-dimensional shapes are stacked by repeatedly, for example, feeding metal powder into a formation area in a device, irradiating it with a light beam or an electron beam based on two-dimensional data representing a three-dimensional cross-section, melting the metal powder, and solidifying the metal powder.

[0044] The thickness of each of the walls W1 and the like of the heat exchanger core 10, which is obtained by additive manufacturing using the metal material, is, for example, 0.3 mm to 3 mm.

[0045] The heat exchanger core 10 according to the present embodiment is manufactured by additively forming the first flow path group G1 and the second flow path group G2 using the metal material. Polishing and similar processes can be performed on the product obtained by the additive manufacturing step, as necessary.

[0046] The heat exchanger core 10 can be formed integrally, by cutting or the like, without being limited to additive manufacturing.

[0047] The heat exchanger core 10 can be configured by combining the plurality of partition walls W1 formed by bending metal plates; however, the heat exchanger core 10 is preferably formed integrally. In the case where the heat exchanger core 10 is formed integrally, the heat exchanger core 10 does not require a seal to prevent fluids from leaking out of a gap between components.

[0048] In one application, the gasket must possess sufficient elastic deformation to reliably seal the gap between the components. To prevent fluid leakage, maintenance is required, such as disassembling the heat exchanger core components and reattaching the gasket. To prevent damage to the gasket due to factors such as changes in deformation caused by gasket tolerances, assembly tolerances, fluid pressure changes, gasket deformation over time, or thermal stress, regular maintenance is crucial.

[0049] In contrast, since the integrally formed heat exchanger core 10 according to the present embodiment does not contain the seal, it is possible to greatly reduce the time and effort required for maintenance. Housing and head

[0050] As in Fig. 1 and Fig. As illustrated in Figure 2, the housing 20 is formed in an essentially cylindrical shape. The housing 20 is manufactured, for example, from stainless steel or an aluminum alloy with characteristics suitable for the fluids.

[0051] The housing 20 comprises a main housing body 21, which has an inner diameter corresponding to the outer diameter of the heat exchanger core 10 and a circular cross-section, and large-diameter sections 22, each with a diameter larger than the diameter of the main housing body 21. The large-diameter sections 22 are provided at respective ends of the main housing body 21 in the axial direction D1. These large-diameter sections 22 function as a first inlet head 221 and a first outlet head 222.

[0052] These heads 221 and 222 each contain annular interiors 221A and 222A ( Fig. 2) as communication spaces around the side wall W0 of the heat exchanger core 10.

[0053] The first inlet head 221 includes an inlet passage 22A through which the first fluid flows in from the outside. The first inlet head 221 includes an outlet passage 22B through which the first fluid flows out to the outside.

[0054] The inlet opening 22A can be provided not only at one position, but at any of a multitude of positions in the circumferential direction D2. For example, two inlet openings 22A can be arranged point-symmetrically around the center of the second cross-section C2. This applies to the outlet opening 22B.

[0055] In each of the interior spaces 221A and 222A of the heads 221 and 222, a flow path cross-sectional area is sufficiently ensured in one direction (radial direction) that intersects the circumferential direction. Therefore, the resistance of the first fluid in each of the interior spaces 221A and 222A is less than the resistance of the first fluid in each of the transverse paths 14 described below. Thus, the first fluid flows equally into the first flow path group G1 from the first inlet head 221 through the transverse paths 14, and the first fluid flowing equally through the first flow path group G1 from the first outlet head 222 flows out through the transverse paths 14.

[0056] At one end 10A of the spectroscopy detector 20 in the axial direction D1, a second inlet head 31 is provided. At the other end 10B of the housing 20 in the axial direction D1, a second outlet head 32 is provided.

[0057] A gap between a flange 31A of the second inlet head 31 and a flange 231 of the housing 20 is sealed by an annular sealing element (not illustrated). A gap between a flange 32A of the second outlet head 32 and a flange 232 of the housing 20 is also sealed in a similar manner.

[0058] The first river path group G1 is connected to an inside of the first inlet head 221 and an inside of the first outlet head 222.

[0059] The second flow path group G2 is connected to an inner side of the second inlet head 31 and an inner side of the second outlet head 32. A starting end of each of the second flow paths 102 opens within the second inlet head 31. A terminal end of each of the second flow paths 102 opens within the second outlet head 32.

[0060] Of the concentrically arranged flow paths 101 and 102, the flow path located at the outermost periphery is preferably a flow path into which the second fluid flows from the second inlet head 31 in the axial direction D1, and from which the second fluid flows out to the second outlet head 32 in the axial direction D1, as is the case for each of the second flow paths 102 according to the present embodiment. As a result, even if a short passage occurs, in which the first fluid, flowing from the first inlet head 221 in the radial direction of the heat exchanger core 10, flows into a gap between the heat exchanger core 10 and the housing 20, heat can be exchanged between the first fluid flowing through the gap and the fluid flowing through the second flow path 102 at the outermost periphery. Therefore, a deterioration in heat exchange efficiency caused by the short passage can be prevented.

[0061] The directions of influence and outflow of the first fluid and the second fluid into / out of the heat exchanger core 10 can be appropriately determined taking into account the layout of the inflow paths and outflow paths, interference of the heads with the first and second fluid, and the like.

[0062] For example, in contrast to the present embodiment, the heat exchanger core 10 can be configured such that at one end 10A of the heat exchanger core 10, the first fluid flows in the first axial direction D1 along the axial direction D1, and the second fluid flows in the second flow path group G2 along the radial direction of the heat exchanger core 10. In this case, the transverse paths 14 described below can be configured to communicate only with the second flow path group G2 from the first flow path group G2 and the second flow path group G2. (Definition of circular shape, ring shape and concentric shape)

[0063] The cross-section of the housing 20 is not strictly limited to a circular shape and may be formed in an essentially circular shape. In this specification, the essentially circular shape is included in the "circular shape". Additionally, the "circular shape" is permitted to have a tolerance from a true circle.

[0064] The “circular shape” includes, for example, a polygonal shape containing a number of vertices (e.g., decagonal to icosagonal), and a shape with n-fold rotational symmetry, where n is, for example, 10 to 20. Additionally, a shape in which arcs are continuous over substantially the entire circumferential direction D2 and irregularities are present on a portion of the circumference is also included in the “circular shape”.

[0065] As described above, each of the cross-sections C1 to C3 of the heat exchanger core 10 is not strictly restricted to a circular shape and may be substantially circular. As described above, the substantially circular shape is included in the "circular shape". In the first cross-section C1, it is sufficient that each of the first flow paths 101 and the second flow paths 102 is formed in a substantially annular shape. Likewise, it is sufficient that the first flow path group G1 and the second flow path group G2 are arranged substantially concentrically. Similar to the definition of the circular shape described above, the substantially annular shape is included in the "annular shape", and the substantially concentric shape is included in the "concentric shape" in the present specification.

[0066] To increase the heat transfer area, each of the partition walls W1 can include a plurality of projections 103 that rise from each of the partition walls W1 to at least one of the first flow path 101 and the second flange area 102, as shown in Fig. Figure 7 illustrates. The projections 103 are preferably provided on each of the dividing walls W1 except at both ends of each of the first flow paths 101 in the axial direction D1 to cause the first fluid to flow smoothly from the transverse paths 14, which are described below, into the first flow path 101, with reduction of pressure loss, and to cause the first fluid to flow smoothly out of the first driving assistance devices 101 to the transverse paths 14.

[0067] The heat exchanger core 10 containing the projections 103 can be integrally formed by additive manufacturing.

[0068] The "concentric form," in which a multitude of circular shapes differing in diameter are arranged concentrically, is permitted to have tolerances to coincide with the centers of the respective circular shapes (concentricity). In other words, the "essentially concentric form" involves a form in which the circular shapes are arranged essentially concentrically. The circular elements that form the concentric circles follow the meaning of the essentially circular form described above. The multitude of polygon shapes can be arranged "essentially concentrically" while making the centers of the respective polygon shapes coincident with each other, or while making the centers of the polygon shape and the rotationally symmetric form coincident with each other.

[0069] A case in which the cross-sections of the casing 20 and the heat exchanger core 10 are circular shapes, the cross-sections of the first flow paths 101 and the second flow paths 102 are annular shapes, and the first flow path group G1 and the second flow path group G2 are arranged concentrically, is most preferred with regard to the balance of stress, heat transfer area and flow state.

[0070] However, in a case where the cross-sections of the housing 20 and the heat exchanger core 10 are substantially circular shapes, the first flow paths 101 and the second flow paths 102 have substantially ring-shaped forms in the first cross-section C1, or the first flow path group G1 and the second flow path group G2 are substantially concentric overall, it is also possible to achieve effects equivalent to those described below by the present embodiment. (Description of Second Cross Section and Cross Path)

[0071] As in Fig. 4 illustrates the length IV-IV in Fig. The cross-section 2 corresponds to the heat exchanger core 10, which includes the cross paths 14 that cross the first flow path group G1 and the second flow path group G2 and communicate only with the first flow path group G1. In the Fig. In the second cross-section C2, illustrated in Figure 4, the transverse paths 14 extend radially along the heat exchanger core 10 and communicate with the interior 221A of the first inlet head 221. As shown in Figure 4, the transverse paths 14 extend radially along the heat exchanger core 10 and communicate with the interior 221A of the first inlet head 221. Fig. 1 and Fig. Figure 2 illustrates that the cross paths 14 penetrate the side wall W0 and the subdivision walls W1 in the thickness direction.

[0072] Although not illustrated, a longitudinal line IVx-IVx in Fig. 2. Cross-sectional view of the cross-sectional view in Fig. 4. The longitudinal line IVx-IVx in Fig. The cross-section taken along the line IVx-IVx corresponds to the second cross-section C2. The cross-section taken along the line IVx-IVx is referred to as a second cross-section C2x. The transverse paths 14, which are positioned in the second cross-section C2x, communicate with the interior 222A of the first outlet head 222. In both the second cross-section C2 and the second cross-section C2x, the plurality of (eight in the present embodiment) transverse paths 14 is distributed in the circumferential direction D2. Since the plurality of transverse paths 14 is distributed in the circumferential direction D2, the rigidity and strength of the heat exchanger core 10 can be made uniform in the circumferential direction D2, and the flow state of the first fluid can be made uniform in the circumferential direction D2. The flow rate of the first fluid flowing in each of the transverse paths 14 is easily balanced because the number of transverse paths 14 is large.As a result, sufficient heat is exchanged between the first fluid and the second fluid, which flows uniformly along the entire circumferential direction D2. Taking this into account, four or more transverse paths 14 are preferably distributed in each of the second cross-sections C2 and C2x. However, the number of transverse paths 14 in each of the second cross-sections C2 and C2x can be three or fewer (including one).

[0073] To help balance the flow rate of the first fluid flowing through each of the transverse paths 14, the plurality of transverse paths 14 is preferably distributed at equal intervals in the circumferential direction D2. In other words, the heat exchanger core 10 is preferably formed symmetrically around the center of each of the second cross-sections C2 and C2x.

[0074] Furthermore, the cross-sectional areas of the respective cross-paths 14 are preferably equal to each other. This makes it possible to ensure a length of a section where the first fluid and the second fluid flow countercurrently along the axial direction D1 in the circumferential direction D2 of the first flow paths 101 and the second flow paths 102. The tolerance of the cross-sectional area of ​​each of the cross-paths 14 is permitted.

[0075] The cross-sectional shape and opening shapes in the side wall W0 of the cross paths 14 are rectangular shapes in the Fig. 1 and Fig. The two illustrated examples can be suitable shapes, such as circular shapes. The openings of the transverse paths 14 are distributed in the side wall W0 in the circumferential direction D2.

[0076] Additionally, to help balance the flow rate of the first fluid flowing through each of the transverse paths 14 as described above, the inlet passage 22A and the transverse paths 14 are preferably shifted in phase with each other, namely, the inlet passage 22A and the transverse paths 14 are preferably arranged at different positions in the circumferential direction D2, as shown in Fig. Figure 4 illustrates that if the inlet passage 22A and the cross paths 14 are out of phase, it is possible to more reliably prevent the occurrence of a disproportion in the flow rate of the fluid flowing through each of the cross paths 14, compared to a case where the inlet passage 22A and the cross paths 14 are not out of phase (inlet passage 22A and all cross paths 14 are positioned at the same position in the circumferential direction D2).

[0077] Each of the cross paths 14 includes a set of tubular cross walls W3 positioned in the area of ​​the second flow paths 102. Each of the cross paths 14 is separated from the second flow path group G2 by the cross walls W3. Each of the cross walls W3 is integral with the partition walls W1 between any two partition walls W1 adjacent radially to the heat exchanger core 10. The axes of the corresponding cross walls W3 are positioned on the same straight line. Each of the first flow paths 101 communicates with the inside of the cross walls W3.

[0078] All of the first flow paths 101 from the first flow path 101, which is positioned on an outer peripheral side of the heat exchanger core 10, to the (not illustrated) first flow path, which is positioned near the axial center of the heat exchanger core 10, communicate with the interior 221A of the first inlet head 221 and the interior 221A of the first outlet head 222 through the plurality of transverse paths 14, which extend radially from the vicinity of the axial center of the heat exchanger core 10, and further communicate with the outside of the heat exchanger 1. (Description of third cross-section)

[0079] Fig. 5, which follows the longitudinal line VV in Fig. 2 and Fig. The cross-section shown in section 6 illustrates the third cross-section C3, which is positioned on the outside of the second cross-section C2 in the axial direction D1.

[0080] As in Fig. Figure 6 illustrates that the first flow path group G1, communicating with the cross paths 14 described above, includes barrier walls W4 positioned on the outside of the second cross-section C2 in the axial direction D1. The first fluid flowing through the first flow path group G1 does not flow in the axial direction D1 over the barrier walls W4, which intersect the axial direction D1. Each of the barrier walls W4 closes a gap between each pair of adjacent partition walls W1.

[0081] The first river path group G1 is in the third cross-section C3 ( Fig. 5) closed by the barrier walls W4. Accordingly, only the second river path group G2 is present in the third cross-section C3. In an area marked with a grid pattern in Fig. As illustrated in section 5, the first river path group G1 is not present.

[0082] The second flow path group G2 is open to the second inlet head 31 and the second outlet head 32 at the respective ends of the heat exchanger core 10.

[0083] Although not illustrated, one along the line Vx-Vx resembles Fig. 2. Cross-sectional view of the cross-sectional view in Fig. 5. The one along the line Vx-Vx in Fig. The second cross-section taken corresponds to a third cross-section C3x, which is positioned on the outside of the second cross-section C2x in the axial direction D1. The cross-section taken along the line Vx-Vx is referred to as the third cross-section C3x.

[0084] As in Fig. As illustrated in Figure 6, the first river path group G1 in the third cross-section C3x is closed off by the dam walls W4. Accordingly, only the second river path group G2 is present in the third cross-section C3x. (Flow of first fluid and flow of second fluid)

[0085] A flow of the first fluid and a flow of the second fluid in the heat exchanger core 10 are described with reference to Fig. 2, Fig. 4 and Fig. 6 described. Fig. Figure 6 illustrates part of a vertical cross-section of the heat exchanger core 10.

[0086] As indicated by dashed arrows in Fig. As illustrated in Figure 6, the second fluid, flowing into the second inlet head 31 via an inlet opening (not illustrated), flows into the starting ends of the second flow paths 102 of the second flow path group G2. At this time, since the second flow path group G2 is formed symmetrically around the center of the third cross-section C3, the second fluid flows uniformly into the second flow paths 102 along the entire circumference in the direction D2 and flows through the second flow paths 102 in the axial direction D1. The second fluid flows from the terminal ends of the second flow paths 102 to the inside of the second outlet head 32 and continues to the outside of the heat exchanger 1 via an outlet opening (not illustrated).

[0087] As indicated by solid arrows in Fig. As illustrated in Figure 6, the first fluid flowing into the interior 221A of the first inlet head 221 from the inlet passage 22A flows uniformly into the first flow path group G1 in the circumferential direction D2 through the transverse paths 14 that open into the side wall W0.

[0088] At this time, the first fluid is distributed from within the first inlet head 221 to the multitude of transverse paths 14, without being distributed disproportionately to any of the transverse paths 14 near the inlet passage 22A. In each of the transverse paths 14, the first fluid passes the interior of the transverse walls W3, which are defined by alternating long and two short dashed lines in Fig. 6 are illustrated and is distributed to the first flow paths 101 to the inside in the radial direction of the heat exchanger core 10.

[0089] Subsequently, the flow rate of the first fluid flowing through each of the first flow paths 101 in the axial direction D1 is maintained uniformly over the entire area in the circumferential direction D2, based on the symmetry of the heat exchanger core 10 in the second cross-section C2, where the transverse paths 14 are positioned. Accordingly, sufficient heat can be exchanged between the second fluid flowing through the second flow paths 102 and the first fluid over the entire area where the first cross-section C1 continues, under the condition of countercurrent flow, which easily ensures a large temperature difference between the first and second fluids as they flow through flow paths 101 and 102.

[0090] After reaching the terminal ends of the first flow paths 101, the first fluid flowing through the first flow paths 101 in the axial direction D1 is changed in the flow direction from the axial direction D1 to the radial direction, passes through the interior of the transverse paths 14, which are arranged radially from the axial center of the heat exchanger core 10, and flows through the transverse paths 14 to the outside in the radial direction of the heat exchanger core 10, while being merged. Subsequently, the first fluid flowing from the transverse paths 14 to the inside of the first outlet head 222 flows out of the outlet passage 22B to the outside of the heat exchanger 1. (Main effects of the present embodiment)

[0091] According to the heat exchanger 1 of the present embodiment described above, based on the configuration of the heat exchanger core 10, in which the housing 20 has a shape symmetrical about the axial center and the first flow path group G1 and the second flow path group G2 are symmetrical concentric stacks, heat exchange can be efficiently carried out over the entirety of the heat exchanger core 10, through which the first fluid and the second fluid flow equally, while the stress caused by pressure of the fluids and the like is uniformly distributed over the entire heat exchanger core 10, and the heat transfer surface of the first fluid and the second fluid is largely ensured.

[0092] From the above, it is possible to improve reliability by preventing the heat exchanger core 10 from being damaged and to achieve the same heat exchange performance with a smaller heat exchanger core 10. (Modification)

[0093] A heat exchanger according to a modification of the present disclosure is described with reference to Fig. 8, Fig. 9A and Fig. 9B described.

[0094] The heat exchanger according to the modification includes a heat exchanger core 40, which is in Fig. Figure 8 is illustrated, and a housing is not illustrated. The housing, which accommodates the heat exchanger core 40, is preferably configured in a manner similar to the housing 20 ( Fig. 1, Fig. 2, Fig. 4 and Fig. 6) according to the embodiment described above.

[0095] Fig. Figure 9A illustrates a cross-section (first cross-section C1) of the heat exchanger core 40, which runs along line IXA-IXA in Fig. 8 is taken. As in Fig. As illustrated in Figure 9A, the heat exchanger core 40 includes the first flow path group G1 and the second flow path group G2, which are arranged concentrically, as in the heat exchanger core 10 according to the embodiment described above. The heat exchanger core 40 can also be formed by additive manufacturing using a metal material.

[0096] The following describes the configuration and effects of the heat exchanger core 40, focusing on aspects other than those of the heat exchanger core 10 according to the embodiment described above. Components in the heat exchanger core 40 that are similar to those in the heat exchanger core 10 are designated by the same reference numerals.

[0097] As in Fig. 9A and Fig. As illustrated in Figure 9B, each of the first river paths 101 and the second river paths 102 is subdivided into a multitude of sections S by partitions W5.

[0098] To compensate for the heat transfer coefficients in the circumferential direction D2, the sections S preferably all have the same flow path diameter and are preferably arranged over the entire circumference of the heat exchanger core 40.

[0099] As in Fig. Figure 9A illustrates that the sections S (S2) forming the second flow paths 102 are arranged in a spiral shape around an axis A of the heat exchanger core 40. Further, as shown in Fig. As illustrated in 9B, the sections S (S1) forming the first river paths 101 are also formed in a spiral shape around the axis A.

[0100] The spiral drawn through each of the sections S1 and the spiral drawn through each of the sections S2 are opposite in direction. When the sections S1 of the first flow path 101 and the sections S2 of the second flange area 102 are viewed from an end face D11 ( Fig. 8), in the axial direction D1, the sections S2 all extend in a spiral shape in a clockwise direction R1, as in Fig. 9A illustrates this, and the sections S1 all extend in a spiral shape in a counterclockwise direction R2, as shown in Fig. 9B illustrated.

[0101] In Fig. 9A illustrates an area of ​​section S2 with a diagonal line pattern. Fig. 9B similarly illustrates an area of ​​section S1 with a diagonal line pattern.

[0102] The partition walls W2 ( Fig. 3B) according to the embodiment described above, all are formed parallel to the axial direction D1 of the heat exchanger core 10, while the partition walls W5, which partition the sections S2 in the circumferential direction D2, are formed in a spiral shape in the counterclockwise direction R1, when viewed from an end side D11 ( Fig. 8) in the axial direction D1, as in Fig. 9A illustrates. Continue as in Fig. Figure 9B illustrates that the partition walls W5, which divide sections S1 in the circumferential direction D2, are formed in a spiral shape in the counterclockwise direction R2 when viewed from one end side D11 in the axial direction D1.

[0103] After the second fluid flows into sections S2 of the second flow paths 102 from one end side D11 in the axial direction D1, as indicated by dashed arrows in Fig. As illustrated in Figure 8, the second fluid flows from one end side D11 to the other end side D12 in a spiral shape in the clockwise direction R1 around the axis of the heat exchanger core 40 along the sections S2.

[0104] In contrast, after the first fluid flows into sections S1 of the first flow paths 101 from the other end D12 in the axial direction D1, as indicated by solid arrows in Fig. As illustrated in Figure 8, the first fluid flows in a spiral shape in one direction (counterclockwise direction R2) opposite to the flow direction of the second fluid along sections S1 and crosses the flow of the second fluid. At this time, the first fluid flows in a spiral shape in a clockwise direction when viewed from the other end D12.

[0105] In the case where sections S1 and S2 are both formed parallel to the axial direction D1, as in the embodiment described above, the positional relationship between a specific section S1 (optionally a section S1, the same applies below) and a specific section S2 (optionally a section S2, the same applies below) in the cross-section C1 of the heat exchanger core 40 is not changed in the other cross-section C4 ( Fig. 8), which is separated from the cross-section C1 in the axial direction D1.

[0106] In contrast, if sections S1 and S2 are both formed in a spiral shape in opposite directions when viewed from one end face D11 of the heat exchanger core 40, the positional relationship between specific section S1 and specific section S2 in the axial direction D1 is changed. In other words, if specific section S1 is adjacent to specific section S2 (for example, the one in Fig. 9A (black section S2) in cross-section C1, with the position of the specific section S2 as a reference, another section S1 is adjacent to the specific section S2 in cross-section C4. The section S1 adjacent to the black section S2 in cross-section C1 is separated from the black section S2 in the counterclockwise direction R2, when viewed from one end face D11 in cross-section C4.

[0107] Due to the non-uniformity of the flow rates of the first fluid and the second fluid, which flow into the first flow paths 101 and the second flow paths 102 respectively, a place where the temperature is locally high, or a place where the temperature is locally low, may exist in the first flow paths 101 and the second flow paths 102 of the heat exchanger core 40.

[0108] For example, even if the place where the temperature is locally high (in Fig. 9A (in black section S2) in one of the second flow paths 102 in cross-section C1 of the heat exchanger core 40, section S2, where the temperature is locally high, sequentially exchanges heat with each of the sections S1 arranged in the circumferential direction D2, because the second fluid flows along sections S2 in the clockwise direction R1 and the first fluid flows along sections S1 in the counterclockwise direction R2. Therefore, it is possible to suppress non-uniformity of the heat transfer quantity in the heat exchanger core 40.

[0109] In the present modification, the example in which the first fluid and the second fluid form countercurrent flows is described. However, in a case where the first fluid and the second fluid form parallel flow flows, effects similar to the operating effects described above can be achieved because the second fluid, flowing in the clockwise direction R1, and the first fluid, flowing in the counterclockwise direction R2, cross each other when viewed from one end D11.

[0110] In the Fig. 9A and Fig. In the illustrated example 9B, sections S1 and S2 are positioned to divide the first flow path group G1 and the second flow path group G2 with equal center angles within the same cross-section of the heat exchanger core 40. In this case, the partitions W5 of the first flow paths 101 and the partitions W5 of the second flow paths 102 are formed radially from the axial center of the heat exchanger core 40, while being continuous in the radial direction of the heat exchanger core 40.

[0111] In contrast, as in Fig. Figure 10 illustrates that the positions of the partitions W5 of each first flow path 101 and the positions of the partitions W5 of each second flange area 102 differ in the circumferential direction D2, and between the adjacent first and second flow paths 101 and 102 in the radial direction. This is preferred because the stress acting on the heat exchanger core 40 is distributed uniformly in the circumferential direction D2. It should be noted that the arrangement of the Fig. 10 illustrated partitions W5 onto the partitions W2 ( Fig. 3B) is applicable, which extend parallel to the axial direction D1 of the heat exchanger core 10, without being limited to the partitions W5, each of which is formed in the spiral shape.

[0112] As in Fig.Figure 3B, described above, illustrates that even when the flow path diameters of the sections S are made equal, the positions of the partitions W2 of each first flow path 101 in the circumferential direction D2 and the positions of the partitions W2 of each second flange area 102 in the circumferential direction D2 between the adjacent first and second flow paths 101 and 102 in the radial direction differ. This is preferred with regard to the stress distribution.

[0113] Furthermore, unlike the case where the partitions W5 are formed radially from the axial center of the heat exchanger core 40, if the heat exchanger core 10 is designed such that the flow path cross-sectional areas of the sections S in the layers of the heat exchanger core 10 are made equal, by arranging the partitions W2 (or W5) in such a way that the positions of the partitions W2 (or W5) in the circumferential direction D2 differ between the adjacent first and second flow paths 101 and 102 in the radial direction of the heat exchanger core 10 (or 40), it is possible to ensure the predetermined transfer efficiency and pressure resistance while avoiding an enlargement of the heat exchanger 1, as described above. (Additional note)

[0114] The heat exchanger core, the heat exchanger and the method for manufacturing the heat exchanger core according to the embodiments described above are understood as follows.

[0115] (1) A heat exchanger core according to a first aspect is a heat exchanger core 10 or 40 that performs heat exchange between a first fluid and a second fluid and includes a circular first cross-section C1 in which a first flow path group G1 for the first fluid and a second flow path group G2 for the second fluid are positioned. First flow paths 101 contained in the first flow path group G1 and second flow paths 102 contained in the second flow path group G2 are arranged annularly in the first cross-section C1. The first flow path group G1 and the second flow path group G2 are arranged concentrically in the first cross-section C1. Each of the first flow paths 101 and second flow paths 102 is subdivided into a plurality of sections S (or S1 and S2) in a circumferential direction D2 of the heat exchanger core 10.

[0116] Based on the configuration in which the first flow path group G1 and the second flow path group G2 are stacked symmetrically and concentrically, heat exchange can be efficiently carried out over the entire heat exchange core, through which the first fluid and the second fluid flow equally, while stress caused by pressure of the fluids and the like is uniformly distributed overall over the heat exchange core and the heat transfer surface of the first fluid and the second fluid is largely ensured.

[0117] Additionally, since each of the flow paths (101 and 102) is subdivided into sections S, the heat transfer efficiency can be improved. Furthermore, the rigidity and strength of the heat exchanger core, particularly in the radial direction, can be improved by walls (W2 and W5) that subdivide the flow paths into sections S.

[0118] As described above, the “circular shape” includes the essentially circular shape, the “ring-shaped shape” includes the essentially ring-shaped shape, and the “concentric shape” includes the essentially concentric shape.

[0119] (2) A heat exchanger core according to a second aspect further comprises a second cross-section C2 in which transverse paths 14, which cross the first flow path group G1 and the second flow path group G2, are positioned. The transverse paths 14 communicate with either the first flow path group G1 or the second flow path group G2, are separated from the other first flow path group G1 and the second flow path group G2, and extend along a radial direction of the heat exchanger core 10 in the second cross-section C2.

[0120] Either the first fluid or the second fluid flows from cross-path 14 into each of the flow paths (101 or 102) by repeatedly branching, or flows from each of the flow paths (101 and 102) to the cross-paths 14 by repeatedly merging. In other words, it is possible to connect each of the flow paths of the flow path group (G1 or G2) to the outside of the heat exchanger core via simple paths, by having the cross-paths 14 intersect the flow path group.

[0121] (3) In a heat exchanger core according to a third aspect, two or more transverse paths 14 are distributed in the circumferential direction D2 of the heat exchanger core 10.

[0122] As a result, the rigidity and strength of the heat exchanger core can be made uniform in the circumferential direction D2. Additionally, the fluid flows uniformly into each of the transverse paths 14 distributed in the circumferential direction D2, and then flows uniformly from these transverse paths 14 into each of the flow paths (101 or 102). Alternatively, the fluid flows uniformly from each of the flow paths (101 or 102) to the transverse paths 14 and then flows uniformly from these transverse paths 14 outside the heat exchanger core. Therefore, it is possible to equalize the flow state of the fluid in the circumferential direction D2.

[0123] (4) In a heat exchanger core according to a fourth aspect, each of the two or more cross paths 14 has the same flow path cross-sectional area.

[0124] This makes it possible to ensure a uniform length of a section where the first fluid and the second fluid flow in the axial direction D1 and in the circumferential direction D2 of the first flow paths 101 and the second flow paths 102.

[0125] (5) A heat exchanger core according to a fifth aspect further includes a third cross-section C3, which is positioned on the outside of the second cross-section C2 in an axial direction D1 orthogonal to a cross-section of the heat exchanger core 10. A flow path group of the first flow path group G1 and the second flow path group G2, which communicates with the outside of the heat exchanger core 10 via the transverse paths 14, is closed in the third cross-section C3.

[0126] With this configuration, one flow path group, which communicates with the transverse paths 14, is separated from the other flow path group in the axial direction D1 of the first flow path group G1 and the second flow path group G2. Therefore, it is possible to avoid interference and complications of the inflow and outflow paths in both the first and second fluids. As a result, it is possible to configure the heat exchanger, which includes the heat exchanger core, housing, and heads, to fit together well.

[0127] (6) In a heat exchanger core according to a sixth aspect, the flow direction of the first fluid flowing through the first flow path group G1 along an axial direction D1 orthogonal to a cross-section of the heat exchanger core 10 is opposite to the flow direction of the second fluid flowing through the second flow path group G2 along the axial direction D1. In this case, the first fluid and the second fluid form countercurrent flows.

[0128] As a result, the first fluid and the second fluid maintain a slight temperature difference as they flow through the flow paths (101 and 102). Therefore, heat exchange is carried out efficiently.

[0129] (7) In a heat exchanger core according to a seventh aspect, partition walls W1, which divide the first flow path group G1 and the second flow path group G2, all include a projection 103 that rises to at least one of the first flow path 101 and the second flange area 102. The projection 103 can increase the heat transfer area.

[0130] (8) In a heat exchanger core according to an eighth aspect, the plurality of sections S all have the same flow path diameter over the entire first flow path group G1 and the second flow path group G2.

[0131] As a result, a flux state, such as frictional loss, is made uniform across all sections S, so that the heat transfer coefficients of all sections S can be made uniform. Additionally, since the stress is uniformly distributed overall in a plane direction across the cross-section of the heat exchanger core 10, the stress can be made uniform.

[0132] (9) In a heat exchanger core according to a ninth aspect, the positions of the partition walls W2 (or W5), which divide the sections S (or S1 and S2) in the circumferential direction D2 of the heat exchanger core, differ in the circumferential direction D2 between the adjacent first and second flow paths 101 and 102 in a radial direction of the heat exchanger core. In this configuration, stress can be distributed uniformly in the circumferential direction D2 of the heat exchanger core.

[0133] Additionally, unlike the case where the partition walls W2 (or W5) are radially formed in the axial center of the heat exchanger core 40, if the heat exchanger core 10 is designed so that the flow path cross-sectional areas of the sections in the layers of the heat exchanger core 10 are made equal, it is possible to ensure a predetermined heat transfer efficiency and pressure resistance while avoiding the enlargement of the heat exchanger 1.

[0134] (10) In a heat exchanger core according to a tenth aspect, sections S1 and S2 of the first flow paths 101 and the second flow paths 102 are formed in a spiral shape around an axis of the heat exchanger core. In this configuration, even if a location where the temperature is locally high or a location where the temperature is locally low exists in the first flow paths 101 and the second flow paths 102 due to non-uniformity of the flow rate or the like, the non-uniformity of the amount of heat transfer in the circumferential direction D2 can be suppressed by heat exchange between the first fluid and the second fluid flowing through sections S1 and S2.

[0135] (11) In a heat exchanger core according to an eleventh aspect, the sections (S1 or S2) of one of the first flow paths 101 or second flow paths 102 extend in a clockwise direction R1 when viewed from an end face D11 in the axial direction D1 of the heat exchanger core 40, and the sections (S1 or S2) of another of the first flow paths 101 and second flow paths 102 extend in a counterclockwise direction R2 when viewed from one end face D11 in the axial direction D1. With this configuration, the first fluid and the second fluid exchange heat as they flow in the spiral shapes over the entire circumference of the heat exchanger core 10. Therefore, it is possible to suppress non-uniformity of the heat transfer quantity over the entire circumference of the heat exchanger core 10.

[0136] (12) A heat exchanger according to the first aspect comprises the heat exchange core 10 or 40 described above and a housing 20 having a circular cross-section and accommodating the heat exchange core 10 or 40.

[0137] The heat exchanger core 10 or 40 and the housing 20 are both symmetrically formed around a center point of the cross-section. As a result, stress caused by fluid pressure and the like is uniformly distributed in the heat exchanger core 10 or 40 and the housing 20, thus ensuring uniform heat exchange efficiency.

[0138] This makes it possible to improve the reliability and performance of the heat exchanger.

[0139] (13) A heat exchanger according to the second aspect comprises a heat exchanger core 10 or 40, which includes transverse paths 14, and a housing 20 with a circular cross-section, and accommodating the heat exchanger core. A communication space (internal spaces 221A and 222A of heads), which allows the transverse paths 14 to communicate with the outside of the heat exchanger core 10, is provided around the heat exchanger core 10 within the housing 20.

[0140] By using part of the casing as the interior spaces 221A and 222A of the heads, the configuration of the heat exchanger containing the heads can be simplified.

[0141] (14) A method of manufacturing the heat exchanger core according to any one of the first to eleven aspects is a method for manufacturing the heat exchanger core 10, which performs heat exchange between the first fluid and the second fluid. The heat exchanger core includes a circular first cross-section in which a first flow path group for the first fluid and a second flow path group for the second fluid are positioned. First flow paths contained in the first flow path group and second flow paths contained in the second flow path group are arranged annularly in the first cross-section. The first flow path group and the second flow path group are arranged concentrically in the first cross-section. The method involves forming the first flow path group G1 and the second flow path group G2 by additive manufacturing using a metal material.

[0142] Since the heat exchanger core can be integrally formed through additive manufacturing, it is not necessary to assemble components and seal any gaps between them with a gasket. Therefore, maintenance time and effort can be significantly reduced.

[0143] Unlike the description above, the configurations described in the embodiment described above can be selected or appropriately modified to other configurations. Reference symbol list 1 heat exchanger 10, 40 heat exchanger core 10A one end 10B other end 14 Cross path 20 cases 21 Main housing body 22 Large diameter range 22A Inlet passage 22B Outlet Passage 31 second inlet head 31A flange 32 second outlet head 32A flange 101 first river trail 102 second river path 103 lead 221 first inlet head 221A Interior (Communication Room) 222 first exhaust head 222A Interior (Communication Room) 231, 232 flange Axis C1 first cross-section C2, C2x second cross-section C3, C3x third cross-section C4 cross-section D1 Axis direction D11 an end page D12 another end page D2 circumferential direction G1 first river trail group G2 second river trail group L Perimeter R1 Clockwise direction R2 Counterclockwise direction Section S W0 side wall W1 Partition wall W2, W5 partition wall W3 Cross wall W4 partition wall QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] JP 3406896 B2

[0007]

Claims

[1] Heat exchange core that performs heat exchange between a first fluid and a second fluid, wherein the heat exchange core comprises a circular first cross-section in which a first flow path group for the first fluid and a second flow path group for the second fluid are positioned, wherein First river paths, which are contained in the first river path group, and second river paths, which are contained in the second river path group, are arranged in a ring shape in the first cross-section, the first river path group and the second river path group are arranged concentrically in the first cross-section, and Each of the first and second flow paths is subdivided into a multitude of sections in a circumferential direction of the heat exchanger core, wherein the sections of each of the first flow paths and the second flow paths are formed in a spiral shape around an axis of the heat exchanger core, the sections extend from one of the first or second flow paths in a clockwise direction when viewed from an end face in an axial direction of the heat exchanger core, and The sections of another of the first and second river paths extend in a counterclockwise direction when viewed from one end in the axial direction. [2] Heat exchange core according to claim 1, further comprising a second cross-section in which a transverse path is positioned which crosses the first flow path group and the second flow path group, wherein the transverse path communicates with either the first flow path group or the second flow path group, is separated from the other from the first flow path group and the second flow path group, and extends along a radial direction of the heat exchange core in the second cross-section. [3] Heat exchange core according to claim 2, wherein the transverse path comprises two or more transverse paths distributed in the circumferential direction of the heat exchange core. [4] Heat exchange core according to claim 3, wherein each of the two or more cross paths has an equal flow path cross-sectional area. [5] Heat exchange core according to one of claims 2 to 4, further comprising a third cross-section which is positioned on the outside of the second cross-section in an axial direction orthogonal to a cross-section of the heat exchange core, wherein a flow path group which communicates with the outside of the heat exchange core through the transverse paths is closed in the third cross-section by the first flow path group and the second flow path group. [6] Heat exchange core according to any one of claims 1 to 5, wherein a flow direction of the first fluid flowing through the first flow path group in a spiral shape around the axis of the heat exchange core is opposite to a flow direction of the second fluid flowing through the second flow path group in a spiral shape around the axis of the heat exchange core. [7] Heat exchanger core according to claim 1, wherein a partition wall, which divides the first flow path group and the second flow path group, includes a projection that rises to at least one of the first flow path and the second flange area. The projection can increase the heat transfer area. [8] Heat exchanger core according to any one of claims 1 to 7, wherein the plurality of sections all have the same flow path diameter over the entirety of the first flow path group and the second flow path group. [9] Heat exchange core according to any one of claims 1 to 8, wherein positions of partition walls that divide the sections in the circumferential direction of the heat exchange core differ in the circumferential direction between the adjacent first and second flow paths in a radial direction of the heat exchange core. [10] Heat exchangers, comprising: the heat exchanger core according to any one of claims 1 to 9, and a housing with a circular cross-section and accommodating the heat exchanger core. [11] Heat exchangers, comprising: a heat exchanger core according to any one of claims 2 to 5, and a housing with a circular cross-section, and accommodating the heat exchanger core, wherein a communication space that allows the cross path to communicate with the outside of the heat exchanger core, around the heat exchanger core within the housing. [12] Method of manufacturing the heat exchanger core according to any one of claims 1 to 9, comprising: Formation of the first flow path group and the second flow path group by additive manufacturing using a metal material.