Heat exchanger and method for manufacturing heat exchanger

Abstract

This heat exchanger (1A) comprises: a main body (4A) that has heat transfer properties; and a plurality of flow paths (3A) that each have a spiral shape and cause a fluid to flow through the inside of the main body (4A), thereby transmitting the heat of the fluid to the main body (4A). The plurality of flow paths (3A) are arranged in a first direction orthogonal to the central axis of the spiral and in a second direction perpendicular to the central axis of the spiral and the first direction. Among the plurality of flow paths (3A), the flow paths (3A) in which the central axes of the spirals are adjacent to each other in at least one among the first direction and the second direction are intertwined.

Description

Heat exchanger and method for manufacturing a heat exchanger

[0001] This disclosure relates to a heat exchanger and a method for manufacturing a heat exchanger.

[0002] Some heat exchangers have a labyrinthine network of fluid channels to improve heat exchange efficiency.

[0003] For example, Patent Document 1 discloses a plate-type heat exchanger in which multiple plates surrounded by upright walls are stacked on top of each other to allow fluid to flow, and in which multiple openings arranged in a matrix are formed on the plates to allow fluid to flow between the plates.

[0004] Japanese Patent Publication No. 2001-174096

[0005] In the heat exchanger described in Patent Document 1, the heat exchange efficiency is increased by the fluid passing through the opening colliding with the surface of adjacent plates, mixing and stirring it.

[0006] However, in the heat exchanger described in Patent Document 1, the surface area of ​​the plate in contact with the fluid is not very large, and as a result, the heat exchange efficiency is not very high.

[0007] This disclosure was made to solve the above-mentioned problems and aims to provide a heat exchanger with high heat exchange efficiency and a method for manufacturing a heat exchanger.

[0008] To achieve the above objective, the heat exchanger according to this disclosure comprises a heat-conducting body and a plurality of flow channels, each having a helical shape, through which a fluid flows, thereby transferring heat from the fluid to the body. The plurality of flow channels are arranged in a first direction perpendicular to the central axis of the helix and in a second direction perpendicular to the central axis of the helix and the first direction, and in the plurality of flow channels, flow channels adjacent to each other in at least one of the first and second directions with respect to the central axis of the helix are intertwined with each other.

[0009] According to the configuration of this disclosure, in the multiple flow channels, the flow channels whose helical central axes are adjacent to each other in at least one of the first and second directions are intertwined with each other. As a result, the surface area of ​​the flow channels in contact with the fluid is large, and consequently, the heat exchange efficiency of the heat exchanger is high.

[0010] Perspective view of a heat exchanger according to Embodiment 1 of this disclosure Perspective view showing the internal structure of the heat exchanger according to Embodiment 1 of this disclosure Front view showing the internal structure of the heat exchanger according to Embodiment 1 of this disclosure Top view showing the internal structure of the heat exchanger according to Embodiment 1 of this disclosure Right side view showing the internal structure of the heat exchanger according to Embodiment 1 of this disclosure Enlarged top view of a part of the flow path of the heat exchanger according to Embodiment 1 of this disclosure (A) Top view showing how the flow paths of the heat exchanger according to Embodiment 1 of this disclosure are intertwined, (B) Front view showing how the flow paths of the heat exchanger are intertwined (A) A top view showing how the numerous flow paths of the heat exchanger according to Embodiment 1 are intertwined. (B) A cross-sectional view of the A-A cutting line shown in Figure 8. (C) A cross-sectional view of the B-B cutting line shown in Figure 8. (D) A cross-sectional view of the D-D cutting line shown in Figure 8. (E) A cross-sectional view of the E-E cutting line shown in Figure 8. (F) A cross-sectional view of the F-F cutting line shown in Figure 8. (G) A cross-sectional view of the G-G cutting line shown in Figure 8. (A) A top view of the numerous flow paths of the heat exchanger according to Embodiment 1 of this disclosure. (B) An enlarged view of the XB region shown in (A). (A) The right side of the numerous flow paths of the heat exchanger according to Embodiment 1 of this disclosure. (A) Front view of the numerous flow channels in the heat exchanger according to Embodiment 1 of the present disclosure, enlarged view of the XIB region shown in (B)(A) (A) Top view of the numerous flow channels in a modified example of the heat exchanger according to Embodiment 1 of the present disclosure, enlarged view of the XIIIB region shown in (B)(A) (A) Right side view of the numerous flow channels in a modified example of the heat exchanger according to Embodiment 1 of the present disclosure, enlarged view of the XIVB region shown in (B)(A) (A) Front view of the numerous flow channels in a modified example of the heat exchanger according to Embodiment 1 of the present disclosure, enlarged view of the XVB region shown in (B)(A) Front view showing the internal structure of the heat exchanger according to Embodiment 2 of the present disclosure Top view showing the internal structure of the heat exchanger according to Embodiment 2 of the present disclosure Right side view showing the internal structure of the heat exchanger according to Embodiment 2 of the present disclosure Top view showing how the numerous flow paths of the heat exchanger according to Embodiment 2 of the present disclosure are intertwined (A) Cross-sectional view of the A-A line shown in Figure 19, (B) Cross-sectional view of the B-B line shown in Figure 19, (C) Cross-sectional view of the C-C line shown in Figure 19, (D) Cross-sectional view of the D-D line shown in Figure 19, (E) Cross-sectional view of the E-E line shown in Figure 19, (F) Cross-sectional view of the F-F line shown in Figure 19,(G) Cross-sectional view of the G-G cutting line shown in Figure 19 Perspective view of the heat exchanger according to Embodiment 3 of the present disclosure Exploded perspective view of the heat exchanger according to Embodiment 3 of the present disclosure Exploded perspective view of the flow path unit provided in the heat exchanger according to Embodiment 3 of the present disclosure Plan view of the flow path plate constituting the flow path unit provided in the heat exchanger according to Embodiment 3 of the present disclosure (A) Plan view of the heat exchanger according to Embodiment 3 of the present disclosure, (B) Cross-sectional view of the B-B cutting line shown in (A), (C) Cross-sectional view of the C-C cutting line shown in (A) (A (A) A top view of the flow path formed in the flow path unit of the heat exchanger according to Embodiment 3 of the present disclosure, (B) An enlarged view of the XXVIB region shown in (A), a top view showing how the numerous flow paths are intertwined in a modified example of the heat exchanger according to Embodiment 3 of the present disclosure, (A) A cross-sectional view of the A-A line shown in Figure 27, (B) A cross-sectional view of the B-B line shown in Figure 27, (C) A cross-sectional view of the C-C line shown in Figure 27, (D) A cross-sectional view of the D-D line shown in Figure 27, (E) A cross-sectional view of the E-E line shown in Figure 27, (F) (G) Cross-sectional view of the F-F cutting line shown in Figure 27, (A) Cross-sectional view of the G-G cutting line shown in Figure 27, (B) Cross-sectional view of the B-B cutting line shown in (A), (C) Cross-sectional view of the C-C cutting line shown in (A), exploded perspective view of the flow path unit of the heat exchanger according to Embodiment 4 of the present disclosure, plan view of the flow path plate constituting the flow path unit of the heat exchanger according to Embodiment 4 of the present disclosure, entanglement of numerous flow paths of the heat exchanger according to Embodiment 4 of the present disclosure (A) A top view showing the direction of the heat exchanger according to Embodiment 5 of the present disclosure. (B) A cross-sectional view of the section line A-A shown in Figure 32. (C) A cross-sectional view of the section line C-C shown in Figure 32. (D) A cross-sectional view of the section line D-D shown in Figure 32. (E) A cross-sectional view of the section line E-E shown in Figure 32. (F) A cross-sectional view of the section line F-F shown in Figure 32. (G) A cross-sectional view of the section line G-G shown in Figure 32. An exploded perspective view of the heat exchanger according to Embodiment 5 of the present disclosure. (A) A plan view of the partition plate provided in the heat exchanger according to Embodiment 5 of the present disclosure.(B) Plan view of the discharge plate of the heat exchanger Exploded perspective view of the heat exchanger according to Embodiment 6 of the present disclosure Exploded perspective view of the heat exchanger according to Embodiment 7 of the present disclosure Plan view of the distribution component and flow path component of the heat exchanger according to Embodiment 7 of the present disclosure Enlarged view of the XXXIX region shown in Figure 38 Plan view showing a part of a modified example of the distribution component of the heat exchanger according to Embodiment 7 of the present disclosure Enlarged view of a part of the modified example of the distribution component of the heat exchanger according to Embodiment 7 of the present disclosure Right side view of the heat exchanger when the brazing material is removed from the heat exchanger according to Embodiment 8 of the present disclosure Right side view of the distribution component, flow path component and brazing material of the heat exchanger according to Embodiment 8 of the present disclosure Top view of the brazing material of the heat exchanger according to Embodiment 8 of the present disclosure Right side view of the heat exchanger according to Embodiment 8 of the present disclosure Schematic diagram showing a part of the area of ​​Figure 28(E)

[0011] Hereinafter, a heat exchanger and a method for manufacturing a heat exchanger according to the embodiments of this disclosure will be described in detail with reference to the drawings. In the drawings, the same or equivalent parts are denoted by the same reference numerals. In the Cartesian coordinate system XYZ shown in the drawings, the direction in which the multiple helical flow channels of the heat exchanger extend is the front-to-back direction, and the direction in which these flow channels are arranged is the left-to-right direction and the up-and-down direction, respectively. The left-to-right direction is the X direction, the front-to-back direction is the Y direction, and the up-and-down direction is the Z direction. Hereafter, this coordinate system will be referenced as appropriate in the explanation.

[0012] (Embodiment 1) The heat exchanger according to Embodiment 1 is a heat exchanger in which a block-shaped body has a plurality of spiral channels through which the fluid to be heat exchanged flows, for example, water, a refrigerant, etc. First, the overall configuration of the heat exchanger will be described with reference to Figures 1 to 5. In the following description, the configuration of the heat exchanger will be described using as an example a configuration in which two fluids, a high-temperature fluid and a fluid with the same composition as the high-temperature fluid but at a lower temperature, exchange heat with each other.

[0013] Figure 1 is a perspective view of the heat exchanger 1A according to Embodiment 1. Figures 2-5 are a perspective view, front view, top view, and right side view showing the internal structure of the heat exchanger 1A according to Embodiment 1. In Figures 1-5, the -Y direction is the front and the +Y direction is the back. Figures 2-5 also show a transparent view of the main body 4A of the heat exchanger 1A.

[0014] As shown in Figures 1-5, the heat exchanger 1A comprises a distributor 2A that distributes the high-temperature fluid P and the low-temperature fluid Q to be heat exchanged, and a main body 4A having a plurality of flow channels 3A through which the fluids P and Q distributed to the distributor 2A flow.

[0015] The distributor 2A is a component that distributes fluids P and Q to multiple flow paths 3A formed in the main body 4A, or a component that aggregates the fluids P and Q flowing from the multiple flow paths 3A.

[0016] In detail, the main body 4A has a rectangular parallelepiped shape, as shown in Figures 1 and 2. The main body 4A has its faces oriented in the directions of +X, -X, +Y, -Y, +Z, and -Z. Of the faces of the main body 4A, the ends of the flow path 3A are located on the -Y and +Y faces, as shown in Figure 5. The distributor 2A is provided to distribute fluids P and Q to these ends of the flow path 3A, or to collect fluids P and Q from the ends of the flow path 3A.

[0017] To describe the configuration in more detail, the distributor 2A, in order to distribute the fluid P, has an inlet 21P into which the fluid P flows, and a piping section 22P extending from the inlet 21P, as shown in Figures 1, 2, and 4. The inlet 21P has a fitting and is connected to an external device to which the fluid P to be heat exchanged is supplied. The inlet 21P is located at the -Y end of the +Z plane of the main body 4A. The piping section 22P is provided on the +Z plane of the main body 4A and extends in the X direction along the -Y end of the main body 4A. When fluid P is supplied to the inlet 21P, the piping section 22P causes the fluid P to flow in the X direction along the -Y end of the main body 4A.

[0018] As shown in Figures 3 and 5, the distributor 2A has a plurality of branch pipes 221 arranged in the X direction and extending from the piping section 22P in the -Z direction. These branch pipes 221 are arranged at a pitch twice the pitch of the flow path 3A in the X direction. Furthermore, as shown in Figure 5, each branch pipe 221 is provided with a plurality of joints 31 arranged at the same pitch as the flow path 3A in the Z direction and connected to the flow path 3A. When fluid P is supplied to the inlet section 21P, the distributor 2A alternately distributes the fluid P to the flow paths 3A arranged in the X direction via the branch pipes 221 and joints 31. In this way, the distributor 2A distributes the fluid P flowing in from the inlet section 21P to each of the flow paths 3A.

[0019] Furthermore, the distributor 2A, in order to collect the fluid P flowing out of the flow path 3A, has a piping section 23P and an outlet section 24P connected to the piping section 23P for discharging the fluid P, as shown in Figures 1, 2, and 4. The piping section 23P is provided near the +Y end of the +Z plane of the main body 4A and extends in the X direction along its +Y end. In addition, as shown in Figure 5, the distributor 2A has a branch pipe section 231 that extends in the +Z direction and whose tip is connected to the piping section 23P.

[0020] Although not shown in the diagram, multiple branch pipe sections 231 are provided and arranged in the X direction. The pitch of these branch pipe sections 231 is twice the pitch of the flow path 3A in the X direction, just like the branch pipe section 221. Each branch pipe section 221 has a joint section 32 as shown in Figure 5, and the joint section 32 connects to the flow path 3A from which the fluid P is supplied from the inlet section 21P mentioned above. With this configuration, the distributor 2A collects the fluid P flowing out from each of the flow paths 3A. On the other hand, the outlet section 24P mentioned above has a joint and is connected to an external device by that joint. As a result, the distributor 2A discharges the collected fluid P to the external device.

[0021] Furthermore, the distributor 2A is equipped with a configuration for distributing and consolidating the fluid Q. Specifically, in order to distribute the fluid Q, the distributor 2A has, as shown in Figures 1, 2, and 4, an inlet portion 21Q into which the fluid Q flows, located at the -Y end of the +Z plane of the main body 4A, and a piping portion 22Q that extends from the inlet portion 21Q and extends in the X direction along the aforementioned piping portion 22P.

[0022] Although a detailed explanation is omitted, the inlet section 21Q and the piping section 22Q have the same configuration as the inlet section 21P and the piping section 22P described above. For example, the piping section 22Q includes a branch pipe section and a joint section with the same configuration as the branch pipe section 221 and the joint section 31 described above. As a result, when fluid Q is supplied to the inlet section 21Q, the distributor 2A alternately flows the fluid Q through the flow paths 3A arranged in the X direction. With this configuration, in the heat exchanger 1A, the flow paths 3A through which fluid P flows and the flow paths 3A through which fluid Q flows are arranged alternately in the X direction.

[0023] Furthermore, in order to collect the fluid Q, the distributor 2A is located at the +Y end of the +Z plane of the main body 4A, as shown in Figures 1, 2, and 4, and has a piping section 23Q that extends in the X direction along the aforementioned piping section 23P, and an outlet section 24Q connected to the piping section 23Q for discharging the fluid Q.

[0024] Although a detailed explanation of the piping section 23Q and the outlet section 24Q will be omitted, they have the same configuration as the piping section 23P and the outlet section 24P described above. For example, the piping section 23Q includes a branch pipe section and a joint section with the same configuration as the branch pipe section 231 and the joint section 32 described above. As a result, the distributor 2A collects the fluid Q flowing out from each of the flow paths 3A. The distributor 2A then discharges the collected fluid Q to an external device.

[0025] The distributor 2A, with this configuration, supplies fluids P and Q to the respective flow paths 3A. Flow path 3A has a helical shape to exchange heat between the supplied fluids P and Q with high efficiency. Next, the configuration of flow path 3A will be described with reference to Figures 6-12.

[0026] Figure 6 is an enlarged top view of a portion of the flow path 3A provided in the heat exchanger 1A according to Embodiment 1. Figures 7(A) and (B) are a top view and a front view showing how the flow paths 3A are intertwined. Figure 8 is a top view showing how multiple flow paths 3A are intertwined. Figures 9(A) to 9(G) are cross-sectional views of the cutting lines from A-A to G-G shown in Figure 8. Figures 10(A) and (B) are top views of multiple flow paths 3A and an enlarged view of the XB region shown in (A). Figures 11(A) and (B) are right side views of multiple flow paths 3A and an enlarged view of the XIB region shown in (A). Figures 12(A) and (B) are front views of multiple flow paths 3A and an enlarged view of the XIIB region shown in (A). Note that the main body 4A is omitted in Figures 6-8 and 10-12 for ease of understanding.

[0027] As shown in Figures 6, 7(A), and 7(B), each of the flow channels 3A has a spiral shape that extends in the Y direction while rotating in a circular motion around a central axis C that extends in the Y direction. The spiral shape is that of a wound wire with a constant diameter and a constant pitch p. Such flow channels 3A are formed by a circular tube.

[0028] In detail, the circular pipe forming the flow path 3A is made of a material with high thermal conductivity, such as aluminum, copper, iron, carbon composite material, or engineering plastic, in order to facilitate the transfer of heat from the fluid P or Q flowing inside. Specifically, the iron should be stainless steel, mild steel with high thermal conductivity, or medium carbon steel. The flow path 3A is formed by bending the circular pipe made of such material into a spiral shape.

[0029] Due to its shape, when fluid P or Q flows through the channel 3A, the fluid P or Q undergoes a helical motion and collides with the inner wall of the channel 3A. In particular, due to the centrifugal force of the helical motion, the flow velocity of fluid P or Q is high near the outer, radially oriented portion of the inner wall of the channel 3A. As a result, fluid P or Q collides strongly with that portion of the wall. Furthermore, the thermal boundary layer becomes thinner, and the heat transfer coefficient of that portion of the wall increases.

[0030] Furthermore, due to the shape described above, the surface area of ​​the inner wall of channel 3A is increased. As a result, heat from the fluid P or Q is easily transferred to the inner wall of channel 3A. Also, the thermal resistance between a solid and a liquid is expressed as the reciprocal of the product of the surface area and the heat transfer coefficient. In channel 3A, since the surface area is large and the heat transfer coefficient is large, the thermal resistance between the inner wall of channel 3A and the fluid P or Q is small. This configuration enhances the heat exchange efficiency in channel 3A.

[0031] Furthermore, multiple flow channels 3A are formed in the main body 4A. As shown in Figures 8, 10(A), 11(A), and 12(A), these flow channels 3A are arranged in the X direction and also in the Y direction. Moreover, among these flow channels 3A, those flow channels 3A arranged in the X direction are intertwined with each other if their helical central axis C is adjacent to each other.

[0032] In detail, in the flow channels 3A arranged in the X direction, as shown in Figure 7(A), the phase difference between adjacent flow channels 3A with their central axes C in the helix is ​​nearly 180°. That is, if the pitch of the helix in the flow channel 3A is p, then the flow channel 3A with its central axis C in the X direction is shifted by half a pitch, or p / 2, in the Y direction where the central axis C extends, relative to the flow channel 3A with its central axis C in the X direction. Furthermore, the flow channels 3A arranged in the X direction satisfy the relationship 0 < d < 2A ... (Equation 1), where A is the amplitude of the helix shown in Figure 6, and d is the distance between the central axes C of adjacent flow channels 3A with their central axes C in the X direction, as shown in Figure 7(A).

[0033] The amplitude of the spiral, as used here, is the distance from the central axis C of the spiral to the center line of the circular pipe. More precisely, the amplitude of the spiral is the distance from the central axis C of the spiral to the center line C1 of the circular pipe in the direction in which the flow paths 3A are adjacent, that is, the distance in the X direction in Embodiment 1.

[0034] The flow channels 3A, which are arranged in the X direction, are closely intertwined with each other due to the positional relationship described above. As a result, the flow channels 3A are intertwined in a fibrous manner and are densely arranged inside the main body 4A. Consequently, the flow channels 3A increase the surface area of ​​the inner wall of the flow channels 3A per unit volume of the main body 4A, making it easier to transfer heat from the fluid P or B. This increases the heat exchange efficiency of the flow channels 3A.

[0035] Furthermore, fluids P and Q are alternately distributed to the flow paths 3A arranged in the X direction by the distributor 2A described above. As a result, fluids P and Q are supplied to each of the two flow paths 3A whose central axis C of the helix is ​​adjacent in the X direction. In the heat exchanger 1A, focusing on a specific flow path 3A, (1) that specific flow path 3A, (2) a flow path 3A adjacent to that specific flow path 3A in the +X direction along the central axis C of the helix, and (3) another flow path 3A adjacent to that specific flow path 3A in the -X direction along the central axis C of the helix are intertwined. That is, in the flow paths 3A arranged in the X direction, two flow paths 3A are intertwined in one flow path 3A. In these intertwined flow paths 3A, as shown in Figures 9(A)-9(G), 10(B), 11(B), and 12(B), fluids P and Q flow in close proximity. As a result, heat exchange occurs between fluids P and Q with high efficiency.

[0036] Returning to Figure 2, this flow path 3A is routed through the main body 4A. That is, the flow path 3A penetrates and traverses the main body 4A in the Y direction.

[0037] The main body 4A is formed from a material with high thermal conductivity, similar to the circular tubes of the flow channels 3A. This material is the same as that used for the circular tubes of the flow channels 3A, for example, aluminum, copper, iron, carbon composite materials, or engineering plastics. The main body 4A is formed from such a material into the rectangular parallelepiped shape described above. The main body 4A has multiple flow channels 3A inside, for example, by casting multiple circular tubes of the flow channels 3A with the shape described above. Because the main body 4A is formed from the aforementioned material with high thermal conductivity, the heat exchange efficiency between the flow channels 3A is high.

[0038] For example, although the inner walls of the intertwined flow channels 3A are close together, they are separated to some extent. That is, the inner walls are separated from each other in the radial direction of the spiral. However, as a result of the main body 4A being formed of the aforementioned material with high thermal conductivity, the heat transfer between the inner wall of flow channel 3A and the inner walls of the other two flow channels 3A that are intertwined with flow channel 3A from the X direction is high. This results in high efficiency in the heat exchange between the fluids P and Q that takes place between the intertwined flow channels 3A.

[0039] Furthermore, in the main body 4A, as shown in Figure 5, adjacent flow channels 3A with the central axis C of the helix in the Z direction are spaced apart, and the inner walls of the flow channels 3A are spaced apart to some extent. However, as a result of the main body 4A being formed from the aforementioned material with high thermal conductivity, heat transfer is high even between adjacent flow channels 3A in the Z direction. This increases the heat exchange efficiency of the heat exchanger 1A.

[0040] The orientation of the heat exchanger 1A described above is such that the X and Z directions are examples of the first and second directions as defined in this disclosure. Furthermore, the inlet section 21P and piping section 22P, which are the parts of the distributor 2A that distribute the high-temperature fluid P, are an example of the first distributor as defined in this disclosure. The inlet section 21Q and piping section 22Q, which are the parts of the distributor 2A that distribute the low-temperature fluid Q, are an example of the second distributor as defined in this disclosure.

[0041] Furthermore, the heat exchanger 1A can reverse the flow direction of fluids P and Q by changing the connection relationship with external equipment. In that case, the piping section 23P and outlet section 24P that were collecting fluid P will distribute fluid P due to the reversal of the flow of fluids P and Q. As is clear from this, the piping section 23P and outlet section 24P are also examples of the first distributor as referred to in this disclosure. Similarly, the piping section 23Q and outlet section 24Q that were collecting fluid Q will distribute fluid Q due to the reversal of the flow of fluids P and Q. These piping sections 23Q and outlet section 24Q are also examples of the second distributor. The distributor 2A may also be called a distribution manifold, header, or the like.

[0042] As described above, in the heat exchanger 1A according to Embodiment 1, each of the multiple flow paths 3A has a helical shape, and the fluids P and Q flow through the inside of the main body 4A, thereby transferring the heat of the fluids P and Q to the main body 4A. For this reason, the surface area of ​​the inner wall of each flow path 3A is large, resulting in high heat transfer efficiency. As a result, the heat exchange efficiency of the heat exchanger 1A is high.

[0043] Furthermore, each of the flow channels 3A is arranged in the X direction perpendicular to the central axis C of the helix, and in the Z direction perpendicular to both the central axis C and the X direction, and the flow channels 3A adjacent to each other in the X direction are intertwined. As a result, the proportion of the interior space occupied by the flow channels 3A is high. In other words, the surface area of ​​the inner wall of the flow channels 3A per unit volume of the main body 4A is large. Consequently, the heat exchange efficiency of the heat exchanger 1A is high.

[0044] Furthermore, because each of the flow channels 3A has a helical shape, the curvature of the inner wall bend is constant in the direction of the helix's extension. For this reason, compared to the heat exchanger described in Patent Document 1, foreign matter is less likely to clog the flow channels 3A.

[0045] (Modification) In the heat exchanger 1A according to Embodiment 1, fluids P and Q are each directed towards the +Y direction in the flow path 3A by the distributor 2A. As a result, fluids P and Q flow in the same direction. However, the heat exchanger 1A is not limited to this. In the heat exchanger 1A, fluids P and Q may flow in opposite directions.

[0046] Figures 13(A) and (B) are top views of the numerous flow channels 3A in a modified example of the heat exchanger 1A and an enlarged view of the XIIIB region shown in (A). Figures 14(A) and (B) are right side views of the flow channel 3A and an enlarged view of the XIVB region shown in (A). Figures 15(A) and (B) are front views of the flow channel 3A and an enlarged view of the XVB region shown in (A).

[0047] As shown in Figures 13(A), 14(A), and 15(A), a modified version of the heat exchanger 1A has multiple flow channels 3A with the same shape as the heat exchanger 1A according to Embodiment 1. In this modified version of the heat exchanger 1A, the connection relationship with external equipment is changed so that fluid Q is supplied from the outlet section 24Q of the distributor 2A and discharged from the inlet section 21Q. That is, the outlet section 24Q is used as the inlet and the inlet section 21Q is used as the outlet. As a result, as shown in Figures 13(B), 14(B), and 15(B), the direction of the fluid Q flow is opposite to the direction described in Embodiment 1. That is, fluid Q flows in the opposite direction to fluid P.

[0048] In flow path 3A, when fluid P flows, its temperature decreases due to heat exchange as it moves towards its destination. Conversely, when fluid Q flows, its temperature increases due to heat exchange as it moves towards its destination. Therefore, in Embodiment 1, as fluids P and Q flow in the same direction, the temperature difference between fluids P and Q decreases at their destinations, resulting in a decrease in heat exchange efficiency.

[0049] However, in the modified heat exchanger 1A, fluids P and Q flow in opposite directions, so heat exchange occurs relatively uniformly throughout the entire flow path 3A. As a result, the modified heat exchanger 1A has a high heat exchange efficiency. Thus, in the heat exchanger 1A, fluids P and Q may flow in opposite directions.

[0050] (Other Modifications) In Embodiment 1, the flow path 3A is formed as a circular pipe and has a circular cross-section, but the cross-sectional shape of the flow path 3A is not limited to this. The flow path 3A may have a helical shape and the fluids P and Q will flow through it, thereby transferring heat from the fluids P and Q to the main body 4A. For this reason, the cross-sectional shape of the flow path 3A may be, for example, a rectangle, a square, or other quadrilateral, or a polygon such as a triangle or hexagon, or an ellipse, star, or other shape.

[0051] Furthermore, in Embodiment 1, the flow path 3A is formed as a circular pipe. However, the flow path 3A is not limited to this. The flow path 3A may have a helical shape and transfer heat from the fluids P and Q to the main body 4A by passing through the inside of the main body 4A. For this reason, the flow path 3A does not have to be formed as a circular pipe, i.e., as a pipe member. For example, the flow path 3A may be an integral part of the main body 4A. The flow path 3A may also be formed at the same time as the manufacturing of the main body 4A. For example, the flow path 3A may be formed by casting or 3D (three dimensions) printing. Here, casting may be, for example, lost-wax casting.

[0052] Furthermore, in Embodiment 1, as shown in Figures 8, 10(A), 11(A), and 12(A), the flow paths 3A whose helical central axes C are adjacent only in the X direction are intertwined with each other. However, the flow paths 3A are not limited to this. For example, the flow paths 3A whose helical central axes C are adjacent only in the Z direction may be intertwined with each other. Moreover, not only are the flow paths 3A whose helical central axes C are adjacent in the Z direction intertwined with each other, but the flow paths 3A whose helical central axes C are adjacent in the X direction may also be intertwined with each other.

[0053] (Embodiment 2) In the heat exchanger 1A according to Embodiment 1, the inner walls of the intertwined flow paths 3A are formed separately from each other, and as a result, the intertwined flow paths 3A are independent of each other. That is, the intertwined flow paths 3A are not connected to each other from the tip to the base. Fluids P and Q are flowed through each of the intertwined flow paths 3A. However, the flow paths 3A are not limited to this form. The flow paths 3A are arranged in a first direction perpendicular to the central axis C of the helix and a second direction perpendicular to the central axis C of the helix and the first direction, and furthermore, the flow paths 3A that are adjacent to the central axis C of the helix in at least one of the first and second directions are intertwined with each other. For this reason, the intertwined flow paths 3A may be in communication and carry the same fluid P or Q.

[0054] In the heat exchanger 1B according to Embodiment 2, the flow channels 3A arranged in the X direction are connected from the tip to the base to form a large flow channel.

[0055] The heat exchanger 1B according to Embodiment 2 will be described below with reference to Figures 16-20. Embodiment 2 will be described primarily for its configuration, which differs from that of Embodiment 1.

[0056] Figures 16-18 are a front view, a top view, and a right side view showing the internal structure of the heat exchanger 1B according to Embodiment 2.

[0057] As shown in Figures 16 and 17, the heat exchanger 1B includes a distributor 2B, which has an inlet 21P through which fluid P flows in, an outlet 24P through which fluid P flows out, an inlet 21Q through which fluid Q flows in, and an outlet 24Q through which fluid Q flows out.

[0058] As shown in Figure 16, the inlet section 21P has a piping section 22P extending in the -Z direction from the inlet section 21P. On the other hand, the heat exchanger 1B includes a main body 4B having flow paths 3B arranged in the same way as the flow paths 3A described in Embodiment 1. As a result, in the main body 4B, groups of flow paths 3B arranged in the X direction are stacked in the Z direction. The inlet section 21P is provided with branch pipes 222, each branching from the piping section 22P and connected to the even-numbered layers counted from the +Z side of a plurality of layers formed by such groups of flow paths 3B. The number of branch pipes 222 is the same as the number of even-numbered layers. Here, when a branch pipe 222 is connected to a layer, it means that the branch pipe 222 is connected to each of the flow paths 3B of the group of flow paths 3B that form that layer. With this configuration, when fluid P flows into the inlet section 21P, the fluid P is supplied to the flow paths 3B that form the even-numbered layers.

[0059] Furthermore, the outlet section 24P has a piping section (not shown) extending in the Z direction, and branch pipes 232, shown in Figure 17, each extending from the piping section. Although not shown, multiple branch pipes 232 are provided, each branching from the piping section and connecting to the even-numbered layers of the group of layers of flow paths 3B, counting from the +Z side. As a result, when fluid P is supplied to the flow paths 3B forming the even-numbered layers, the outlet section 24P discharges the fluid P from the flow paths 3B forming the even-numbered layers.

[0060] Furthermore, as shown in Figure 16, the inlet section 21Q has a piping section 22Q extending in the -Z direction from the inlet section 21Q, and a plurality of branch pipes 223, each extending from the piping section 22Q and connected to the odd-numbered layers of the group of layers of the flow path 3B, counting from the +Z side. As a result, when fluid Q flows into the inlet section 21Q, the fluid Q is supplied to the flow path 3B that forms the odd-numbered layers.

[0061] Furthermore, although not shown, the outlet section 24Q has a piping section and multiple branch pipes, similar to the outlet section 24P. Unlike the case of the outlet section 24P, the multiple branch pipes of the outlet section 24Q are each connected to the odd-numbered layers of the group of layers of the flow path 3B, counting from the +Z side. As a result, when fluid Q is supplied to the flow path 3B forming the odd-numbered layers, the outlet section 24Q discharges the fluid Q from the flow path 3B forming the odd-numbered layers.

[0062] Thus, in the heat exchanger 1B, in the multiple layers formed by groups of flow channels 3B in the main body 4B shown in Figure 18, fluid P flows through the flow channels 3B of the even-numbered layers counted from the +Z side, and fluid Q flows through the flow channels 3B of the odd-numbered layers counted from the +Z side. In order to widely diffuse the fluid P or Q in these layers of groups of flow channels 3B, in each layer, as shown in Figure 17, the flow channels 3B are more tightly intertwined with each other than in the first embodiment. Furthermore, the internal spaces of the intertwined flow channels 3B are in communication with each other. Next, the way the flow channels 3B are intertwined and the state of communication will be explained with reference to Figures 19 and 20.

[0063] Figure 19 is a top view showing how the numerous flow paths 3B in the heat exchanger 1B are intertwined. Figures 20(A) to 20(G) are cross-sectional views of the lines from A-A to G-G shown in Figure 19.

[0064] In each layer of the group of flow channels 3B stacked in the Z direction, as shown in Figure 19, the central axis C of the spiral extends in the Y direction, and adjacent flow channels 3A with the central axis C of the spiral in the X direction are intertwined with each other. This intertwining is more dense than the intertwining described in Embodiment 1. As a result, the circular tubes of the flow channels 3A are in contact with each other in the parts where they are intertwined.

[0065] Furthermore, as shown in Figures 20(A), 20(B), 20(F), and 20(G), in each layer of the group of flow channels 3B stacked in the Z direction, in the portion where a specific flow channel 3A and another flow channel 3A adjacent to it in the X direction with the central axis C of the spiral are intertwined, and in the vicinity thereof, the circular pipes of the specific flow channel 3A and the other flow channel 3A are attached to each other, and their internal spaces are in communication.

[0066] On the other hand, as shown in Figures 20(C)-(E), in the area where the specific flow path 3A and another flow path 3A are intertwined, and in its vicinity, the circular pipes of the specific flow path 3A and the other flow path 3A are separated, and their internal spaces are not in communication.

[0067] Thus, in each layer of the group of flow channels 3B stacked in the Z direction, the internal spaces of the intertwined flow channels 3A are partially connected. As a result, fluid P or Q can flow between the intertwined flow channels 3A. In this way, in each layer of the group of flow channels 3B stacked in the Z direction, the group of flow channels 3B forms a large flow channel connected to the main body 4B in the X direction. As a result, in each layer, fluid P or Q diffuses easily, the heat becomes uniform, and the heat exchange efficiency is high. Furthermore, as a result of the group of flow channels 3B forming a large flow channel, it is possible to increase the flow rate of fluid P or Q. This makes it possible to save energy in the pumps that deliver fluids P and Q from external equipment.

[0068] As described above, in the heat exchanger 1B according to Embodiment 2, the intertwined flow paths 3B communicate with each other at the intertwined portions, allowing fluid P or Q to flow between them. Therefore, fluid P or Q diffuses between the intertwined flow paths 3B, making it easier for heat to become uniform and resulting in high heat exchange efficiency. Furthermore, in the heat exchanger 1B, it is possible to increase the flow rate of fluid P or Q, thereby achieving energy savings for external equipment supplying fluid P or Q.

[0069] Furthermore, the portion where two intertwined flow channels 3B intersect is the portion where, in the top view shown in Figure 19, the peak portion of one flow channel 3B protruding in the +X direction meets the valley portion of the other flow channel 3B protruding in the -X direction.

[0070] (Embodiment 3) In the heat exchangers 1A and 1B according to Embodiments 1 and 2, the main bodies 4A and 4B are block-shaped and are integral parts. However, the main bodies 4A and 4B are not limited to these. The main bodies 4A and 4B each have flow paths 3A and 3B and may be composed of a plurality of stacked flow path units.

[0071] The heat exchanger 1C according to Embodiment 3 is formed by stacking a plurality of plate-shaped flow path units.

[0072] The heat exchanger 1C according to Embodiment 3 will be described below with reference to Figures 21-28. Embodiment 3 will be described primarily for its configuration, which differs from that of Embodiments 1 and 2.

[0073] Figure 21 is a perspective view of the heat exchanger 1C according to Embodiment 3. Figure 22 is an exploded perspective view of the heat exchanger 1C. Figure 23 is an exploded perspective view of the flow path unit 43P provided in the heat exchanger 1C. Figure 24 shows the flow path plate 43P that constitutes the flow path unit 43P. １ -43P １１This is a plan view. Figure 25(A) is a plan view of the heat exchanger 1C, and Figures 25(B) and (C) are cross-sectional views of the B-B and C-C cutting lines shown in Figure 25(A). Figures 26(A) and (B) are top views of the flow channels 3C formed in the flow channel units 43P and 44Q, and an enlarged view of the XXVIB region shown in (A). Note that the B-B and C-C cutting lines shown in Figure 25(A) are cutting lines cut along the connecting passages 435 and 436 shown in Figure 23. Also, for ease of understanding, Figure 25 shows the direction of fluid flow P and Q in some configurations with arrows. Also, Figure 25 shows the flow channels 3C in only some configurations.

[0074] As shown in Figures 21 and 22, the main body 4C of the heat exchanger 1C comprises outer plates 41 and 42, and a laminate 46 formed by stacking a plurality of flow path units 43P and 44Q and partition plates 45, the laminate 46 being sandwiched between the outer plates 41 and 42.

[0075] The outer plates 41 and 42 are plates provided to protect the flow path units 43P and 44Q. The outer plates 41 and 42 are formed as flat plates of the same size and shape as the flow path units 43P and 44Q when viewed from above, in order to protect the flow path units 43P and 44Q, which are formed as rectangular shapes with rounded corners when viewed from above.

[0076] Of these outer plates 41 and 42, the outer plate 41 is provided with an inlet portion 21P and an outlet portion 24P, which have a cylindrical shape surrounding a circular hole, in order to allow the fluid P to be heat-exchanged to flow in and out of the flow path units 43P and 44Q. The inlet portion 21P and the outlet portion 24P are located on the diagonal corners of the top-view rectangle of the outer plate 41.

[0077] Furthermore, the outer plate 41 is provided with inlet sections 21Q and 24Q, which are the same shape and size as the inlet section 21P and outlet section 24P, in order to allow the fluid Q to be heat-exchanged to flow into and out of the flow path unit 44Q. The inlet section 21Q and outlet section 24Q are located on a diagonal of the top-view rectangle of the outer plate 41 that is different from the diagonal where the aforementioned inlet section 21P and outlet section 24P are located, and are positioned at the corners.

[0078] Furthermore, the outer plate 41 is positioned in contact with the +Z surface of the laminate 46 of the flow path units 43P, 44Q and partition plate 45 shown in Figure 22. In this way, the outer plate 41 protects the +Z surface of the laminate 46. The outer plate 41 supplies fluids P and Q into the laminate 46 when external equipment is connected to the inlet portions 21P, 21Q and outlet portions 24P, 24Q described above. The outer plate 41 also discharges fluids P and Q from the laminate 46.

[0079] In contrast, the outer plate 42 is formed from a single flat plate without any irregularities, holes, or other structures. The outer plate 42 is positioned in contact with the -Z plane of the laminate 46. As a result, the outer plate 42 sandwiches the laminate 46 between itself and the outer plate 41. The outer plate 42 protects the -Z plane of the laminate 46 and also seals the -Z plane of the laminate 46.

[0080] On the other hand, in the laminated body 46, the flow path unit 43P through which the fluid P flows, the partition plate 45, and the flow path unit 44Q through which the fluid Q flows are stacked in the order of flow path unit 43P, partition plate 45, flow path unit 44Q, partition plate 45, etc. from the +Z side.

[0081] As shown in Figure 22, the flow channel unit 43P is formed in the shape of a thick rectangular flat plate with rounded corners. Furthermore, the flow channel unit 43P is made of the same material as the main body 4A described in Embodiment 1, that is, a material with high thermal conductivity. For example, it is made of a metal such as aluminum, copper, or iron. The plate surface portion of the flow channel unit 43P has inlet and outlet holes 431 and 432 through which the fluid P flows in and out, and communication holes 433 and 434 that allow the fluid Q to flow in the stacking direction, i.e., the Z direction.

[0082] The inlet and outlet holes 431 and 432 are located on the diagonal and corner portions of the top-view rectangle of the flow path unit 43P. As a result, the inlet and outlet holes 431 and 432 overlap with the inlet portion 21P and outlet portion 24P of the outer plate 41 in the Z direction. This allows the inlet and outlet holes 431 and 432 to communicate with the inlet portion 21P and outlet portion 24P of the outer plate 41.

[0083] Furthermore, the inlet and outlet holes 431 and 432 are connected to connecting passages 435 and 436, which extend in a groove-like manner along the long side of the top-view rectangle of the flow path unit 43P. These connecting passages 435 and 436 are connected to a plurality of spiral flow paths 3C formed in the central part of the top-view rectangle of the flow path unit 43P. As a result, when external equipment is connected to the inlet and outlet portions 21P and 24P of the outer plate 41 and fluid P is flowing, the inlet and outlet hole 431 allows fluid P to flow into the spiral flow path 3C via the connecting passage 435. The inlet and outlet hole 431 also allows fluid P to flow out to another flow path unit 43P within the laminate 46. On the other hand, the inlet and outlet hole 432 allows fluid P to flow in from the spiral flow path 3C via the connecting passage 436. The inlet and outlet hole 431 also allows this fluid P to flow out to the outlet portion 24P of the outer plate 41.

[0084] Each of the spiral-shaped flow channels 3C has the same shape as the flow channel 3A described in Embodiment 1. As a result, although not shown in Figure 22, the multiple flow channels 3C are arranged in the X direction with the central axis C of the spiral oriented in the Y direction. The flow channels 3C adjacent to each other in the X direction are intertwined. Furthermore, when the multiple flow channels 3C arranged in the X direction are considered as one row, the flow channel unit 43P is provided with at least one row of multiple flow channels 3C. As a result, when the fluid P flows through the multiple flow channels 3C, the heat of the fluid P is transferred to the flow channel unit 43P itself.

[0085] In contrast, the communication holes 433 and 434 are arranged at the corners above the diagonal line of the rectangle in the top view of the flow path unit 43P, which is different from the diagonal line where the above-described inflow and outflow holes 431 and 432 are arranged. As a result, the communication holes 433 and 434 overlap with the inflow portion 21Q and the outflow portion 24Q of the outer plate 41 in the Z direction. Thereby, the communication holes 433 and 434 communicate with the inflow portion 21Q and the outflow portion 24Q of the outer plate 41. When an external device is connected to the inflow portion 21Q and the outflow portion 24Q of the outer plate 41 and the fluid Q flows, the communication holes 433 and 434 allow the fluid Q to pass through and send the fluid Q to the flow path unit 44Q in the laminate 46. Or, the fluid Q sent from the flow path unit 44Q in the laminate 46 is sent to the outflow portion 24Q of the outer plate 41. Thereby, the communication holes 433 and 434 allow the fluid Q to flow in the laminate 46.

[0086] The flow path unit 43P having such a configuration is a thin flat plate flow path plate 43P having the same outer shape shown in FIGS. 23 and 24 １ -43P １１ is formed by stacking a plurality of sheets, for example, 11 sheets in the case of Embodiment 3. The flow path plate 43P １ -43P １１ Each of them has formed thereon a part of the inflow and outflow holes 431 and 432, the communication holes 433 and 434, and the plurality of spiral flow paths 3C included in the flow path unit 43P. The flow path plate 43P １ -43P １１ is stacked in the order of the flow path plates 43P １ , 43P ２ , 43P ３ …43P １１ from above, so that the above parts are combined to form the configurations of the inflow and outflow holes 431 and 432, the communication holes 433 and 434, and the plurality of spiral flow paths 3C. The flow path unit 43P is manufactured by joining the flow path plates 43P １ -43P １１ to each other after they are stacked. As a result, although the flow path unit 43P has a complex shape including a plurality of spiral flow paths 3C, it is easy to manufacture.

[0087] Returning to Figure 22, a partition plate 45 is positioned below the flow path unit 43P.

[0088] The partition plate 45 is formed in the same rectangular shape with rounded corners as the flow channel unit 43P when viewed from above. Its material is the same as that of the flow channel unit 43P, with high thermal conductivity. The plate surface of the partition plate 45 has communication holes 451-454 that communicate with the communication holes 433, 434 and the inlet / outlet holes 431, 432 of the flow channel unit 43P. As a result, the partition plate 45 allows the fluids P and Q to flow within the laminate 46.

[0089] Furthermore, the partition plate 45 is formed from a single continuous plate in which no holes other than the communication holes 451-454 are formed. The partition plate 45 is in close contact with the flow path unit 43P from below and with the flow path unit 44Q from above. As a result, the partition plate 45 allows fluids P and Q to flow only through the communication holes 451-454, and does not allow fluids P and Q to flow from any other location. In this way, the partition plate 45 prevents leakage of fluids P and Q from between itself and the flow path unit 43P or 44Q, and prevents mixing of fluids P and Q between them. The partition plate 45 may be formed from multiple parts, and may also be called a partition unit.

[0090] The flow channel unit 44Q is formed to have the same shape and size as the flow channel unit 43P. Furthermore, like the flow channel unit 43P, the flow channel unit 44Q is made of a material with high thermal conductivity, such as aluminum, copper, or iron. The plate surface portion of the flow channel unit 44Q has communication holes 441 and 442 for allowing the fluid P to flow in the stacking direction, and inlet and outlet holes 443 and 444 for the fluid Q to enter and exit. In addition, the flow channel unit 44Q has flow channels 445 and 446 that extend in a groove-like manner along the long side of the top-view rectangle of the flow channel unit 44Q and connect to the inlet and outlet holes 443 and 444, and a plurality of spiral flow channels 3C formed in the central portion of the top-view rectangle of the flow channel unit 44Q and connecting to the communication passages 435 and 436.

[0091] The flow path unit 44Q is formed by inverting a unit of the same size and shape as the flow path unit 43P in the X or Y direction. Therefore, the flow path unit 44Q is identical to the flow path unit 43P except that it is symmetrical with respect to the Y axis or the X axis. For this reason, a detailed explanation of the flow path unit 44Q is omitted.

[0092] In the flow path unit 44Q, when external equipment is connected to the inlet 21P and outlet 24P of the outer plate 41 and fluid P is flowing, the communication holes 441 and 442 allow the fluid P to pass through and send it to the flow path unit 43P inside the laminate 46, and then send the fluid P sent from the flow path unit 43P inside the laminate 46 to the outlet 24P of the outer plate 41. In this way, the communication holes 441 and 442 cause the fluid P to circulate within the laminate 46.

[0093] Furthermore, when external equipment is connected to the inlet 21Q and outlet 24Q of the outer plate 41 and fluid Q is flowing, the inlet / outlet hole 443 allows fluid Q to flow into the flow path 445, and further allows fluid Q to flow into the spiral flow path 3C. The inlet / outlet hole 443 also allows fluid Q to flow out into another flow path unit 44Q within the laminate 46. On the other hand, the inlet / outlet hole 444 allows fluid P from the spiral flow path 3C to flow in via the flow path 446. The inlet / outlet hole 444 also allows the fluid Q to flow out into the outlet 24Q of the outer plate 41.

[0094] The partition plate 45 described above is also in close contact with the underside of the flow path unit 44Q. This prevents leakage of fluids P and Q from between the flow path unit 44Q and the partition plate 45, and prevents mixing of fluids P and Q between them.

[0095] These flow path units 43P, partition plate 45, and flow path unit 44Q form a laminate 46. As a result, in the laminate 46 shown in Figure 25(A), the spiral flow paths 3C within flow path units 43P and 44Q form layers stacked in the Z direction, as shown in Figures 25(B) and (C). In each layer, fluid P flows through the layer formed by the flow path 3C within flow path unit 43P. Fluid Q flows through the layer formed by the flow path 3C within flow path unit 44Q. Furthermore, in the laminate 46, the layers through which fluid P flows and the layers through which fluid Q flows are stacked alternately. As a result, fluids P and Q exchange heat in the laminate 46. As described above, the flow path units 43P, partition plate 45, and flow path unit 44Q are made of a material with high heat transfer properties, for example, the same material as the main body 4A described in Embodiment 1. Furthermore, the flow paths 3C are spiral in shape, and adjacent flow paths 3C are intertwined in the X direction, with the central axis C of the spirals clashing with each other. Therefore, the heat exchange efficiency of the laminate 46 is high, and consequently, the heat exchange efficiency of the heat exchanger 1C is also high.

[0096] Furthermore, as described above, the flow path units 43P and 44Q are connected to the flow path plate 43P １ -43P １１ However, it is formed by stacking multiple sheets. As a result, the inner walls of the flow channels 3C of the flow channel units 43P and 44Q are not sufficiently smooth, and as shown in Figures 26(A) and 26(B), multiple discontinuous portions 33 are formed. In detail, the flow channel plate 43P １ -43P １１ At the boundary between them, the inner walls of each channel 3C are uneven, resulting in the formation of discontinuous sections 33 where the inner walls are not continuous. The discontinuous sections 33 are located on the channel plate 43P １ -43P １１ As a result of being formed at the boundaries between them, a discontinuity layer is formed at each of those boundaries. When such discontinuity layers 33 are formed in the flow channel 3C, a phenomenon called the leading-edge effect occurs when the fluids P and Q flow through the flow channel 3C, inhibiting the development of the thermal boundary layer. As a result, heat is more easily transferred through the discontinuity layers 33 in the flow channel 3C, increasing the heat transfer coefficient. This increases the heat exchange efficiency in the flow channel units 43P and 44Q.

[0097] Furthermore, among the multiple spiral channels 3C formed in the channel units 43P and 44Q, the channels 3C that are intertwined with each other are in communication with one another. Figures 27 and 28 show the state in which the channels 3C are in communication with each other.

[0098] Figure 27 is a top view showing how the numerous flow paths 3C in a modified example of the heat exchanger 1C are intertwined. Figures 28(A) to 28(G) are cross-sectional views of the cutting lines from A-A to G-G shown in Figure 27. Note that Figure 27 shows the numerous flow paths 3C within the flow path units 43P and 44Q.

[0099] As shown in Figure 27, in intertwined flow channels 3C, the flow channels 3C are in contact with each other at the same points where the flow channels 3A are intertwined. Furthermore, as shown in Figures 28(A), 28(B), 28(F), and 28(G), in the portion where a particular flow channel 3C is intertwined with another flow channel 3C adjacent to it in the X direction along the central axis C of the spiral, and in its vicinity, the particular flow channel 3C and the other flow channel 3C are attached to each other, and their internal spaces are in communication.

[0100] On the other hand, as shown in Figures 28(C) to 28(E), in the portion where that particular channel 3C and another channel 3C are separated, the internal spaces of the two channels 3Cs are not in communication.

[0101] In this way, the intertwined flow channels 3C are attached to each other, and their internal spaces are partially connected. As a result, the intertwined flow channels 3C diffuse fluid P or Q between them, homogenizing the heat. Consequently, the flow channels 3C enhance the heat exchange efficiency of the heat exchanger 1C.

[0102] As described above, the heat exchanger 1C according to Embodiment 3 has a helical shape and comprises a plurality of flow channels 3C, each having a plurality of flow channel units 43P and 44Q arranged in a stacked configuration, through which fluids P and Q flow and which transmit heat from the fluids P and Q. In each of the flow channel units 43P and 44Q, the flow channels 3C adjacent to each other along the central axis C of the helix are intertwined. As a result, the heat transfer from the flow channels 3C to the flow channel units 43P and 44Q themselves is high, and the heat exchange efficiency of the heat exchanger 1C is high.

[0103] Furthermore, the heat exchanger 1C is constructed by alternately stacking flow path units 43P, which have flow path 3C through which fluid P flows, and flow path units 44Q, which have flow path 3C through which fluid Q flows. As a result, the heat exchanger 1C has high heat exchange efficiency between fluids P and Q.

[0104] Each of the flow channel units 43P and 44Q, when stacked, aligns the central axis C of the spiral and forms the entire flow channel plate 43P, which consists of multiple intertwined flow channels 3C. １ -43P １１ It is equipped with a flow path unit 43P and 44Q, respectively, and a flow path plate 43P １ -43P １１ Since it can be manufactured by stacking these components, its production is easy. For example, it is easier to manufacture than if the flow path units 43P and 44Q were each manufactured as a single unit using methods such as 3D printing or casting.

[0105] Note that the flow path units 43P and 44Q are each connected to the flow path plate 43P １ -43P １１ Rather than being manufactured by simply stacking them, the flow path plate 43P １ -43P １１ The contact surfaces of the stacked components may be joined together, for example, by brazing. Similarly, the components of the heat exchanger 1C, for example, the flow path units 43P and 44Q, may each be brazed together. In this configuration, the components of the heat exchanger 1C are joined together and integrated, thereby increasing the rigidity of the heat exchanger 1C. As a result, the heat exchanger 1C can be installed in locations where vibrations are easily transmitted or where loads are easily applied.

[0106] Furthermore, since discontinuities 33 are formed at the boundary between the stacked flow channel plates 43P1-43P11, the development of the thermal boundary layer is inhibited when the fluids P and Q flow through the flow channel 3C. As a result, the heat exchange efficiency of the heat exchanger 1C is high.

[0107] (Modification) In Embodiment 3, a partition plate 45 is placed between the flow path units 43P and 44Q. However, if the flow path units 43P and 44Q themselves can prevent leakage of fluids P and Q, the partition plate 45 is unnecessary. In other words, the partition plate 45 can have any configuration. For example, if the flow path 3C and the connecting passages 435 and 436 are formed only inside the flow path units 43P and 44Q and are not exposed on the outer surfaces of the flow path units 43P and 44Q, then fluids P and Q will not leak out, and the partition plate 45 can be any component.

[0108] Furthermore, in Embodiment 3, as shown in Figure 25(A), fluids P and Q flow in the same direction inside the flow path units 43P and 44Q, but the flow path units 43P and 44Q are not limited to this. The direction in which fluid P flows in flow path unit 43P may be the same direction as the direction in which fluid Q flows in flow path unit 44Q, or it may be in the opposite direction.

[0109] (Embodiment 4) In the heat exchanger 1C according to Embodiment 3, only fluid P flows through the flow path unit 43P, and only fluid Q flows through the flow path unit 44Q. However, the flow path units 43P and 44Q are not limited to these. Both fluids P and Q may flow through a single flow path unit 43P or 44Q.

[0110] In the flow path unit 47 of the heat exchanger according to Embodiment 4, two fluids, P and Q, are flowed, and heat exchange takes place between these fluids P and Q.

[0111] The heat exchanger 1D according to Embodiment 4 will be described below with reference to Figures 29-33. Embodiment 3 will be described mainly for its configuration which differs from that of Embodiments 1-3.

[0112] Figure 29(A) is a plan view of the heat exchanger 1D, and Figures 29(B) and (C) are cross-sectional views taken along the B-B and C-C cutting lines shown in Figure 29(A). Figure 30 is an exploded perspective view of the flow path unit 47 provided in the heat exchanger 1D according to Embodiment 4. Figure 31 shows the flow path plate 47R constituting the flow path unit 47. １ -47R １１This is a plan view. Note that the B-B and C-C cutting lines shown in Figure 29(A) are cutting lines that are made along the connecting passages 475 and 476 shown in Figures 30 and 31. Also, for ease of understanding, Figure 29 shows the flow direction of fluids P and Q with arrows in some configurations. Furthermore, Figure 29 shows the flow path 3D in only some configurations.

[0113] In the heat exchanger 1D, although not shown, a group of intertwined flow channels 3D arranged in the X direction are stacked in the Z direction, similar to the first embodiment. To realize such a stacked structure of flow channels 3D, the flow channel units 47 are stacked in the Z direction, as shown in Figures 29(B) and 29(C).

[0114] Each of the flow channel units 47 forms one of the multiple layers that make up the group of flow channels 3D described above. To form the group of flow channels 3D in one layer, the flow channel unit 47 forms the flow channel plate 47R shown in Figures 30 and 31. １ -47R １１ It holds.

[0115] Flow channel plate 47R １ -47R １１ In order to form a rectangular flow channel unit 47 with rounded corners when viewed from above, it has the shape of a flat plate that is the same shape and size as the rectangular flow channel unit 47 when viewed from above. And the flow channel plate 47R １ -47R １１ The flow path plate 47R is formed from a material with high thermal conductivity, such as aluminum, copper, or iron, similar to the flow path units 43P and 44Q described in Embodiment 3. １ -47R １１ Each of these has rectangular through holes 471-474 formed at the four corners and a flow path plate 47R １ -47R １１ It has a partial channel 34 formed in the central region of the rectangular shape when viewed from above.

[0116] The through-holes 471-474 are positioned to allow fluids P and Q to flow within the flow path unit 47, and are located at positions corresponding to the inlet 21P, outlet 24P, inlet 21Q, and outlet 24P of the outer plate 41 shown in Figure 29(A).

[0117] In detail, in the outer plate 41, the inlet portion 21P, outlet portion 24P, inlet portion 21Q, and outlet portion 24P are arranged in different positions than in Embodiment 3. As a result, the inlet portion 21P and outlet portion 24P are provided adjacent to the same short side of the top-view rectangle of the outer plate 41 and face each other in the short direction. Also, the inlet portion 21Q and outlet portion 24Q are provided adjacent to the other short side of the top-view rectangle of the outer plate 41 and face each other in the short direction. Of the through holes 471-474 shown in Figures 30 and 31 above, the through holes 471 and 472 are positioned to overlap with the inlet portion 21P and outlet portion 24P in the Z direction. As a result, the through holes 471 and 472 communicate with the inlet portion 21P and outlet portion 24P, allowing the fluid P to flow into the flow path unit 47. Furthermore, the through holes 473 and 474 are positioned to overlap with the inlet portion 21Q and the outlet portion 24Q in the Z direction. As a result, the through holes 473 and 474 communicate with the inlet portion 21Q and the outlet portion 24Q, allowing the fluid Q to flow within the flow path unit 47.

[0118] In contrast, the partial flow channels 34 shown in Figures 30 and 31 are components that form a part of the flow channel 3D in order to exchange heat between the fluids P and Q flowing within the flow channel unit 47. As described above, each flow channel unit 47 forms one of the multiple layers that make up the group of flow channels 3D. The partial flow channel 34 is located on the flow channel plate 47R １ -47R １１ As these are stacked, a single layer of flow channels 3D is formed. In that single layer, a flow channel 3D for fluid P and a flow channel 3D for fluid Q are adjacent to each other in the X direction and intertwined. The partial flow channel 34 forms a part of the flow channel 3D for fluid P and a part of the flow channel 3D for fluid Q. As a result, the partial flow channel 34 forms a flow channel plate 47R １ -47R １１ By stacking these, two intertwined channels 3D are formed: one for the fluid P and another for the fluid Q.

[0119] To allow fluids P and Q to flow through this partial channel 34, a channel plate 47R is used. １ -47R １１ Of these, flow path plate 47R１ -47R ５ From the through hole 471 to the flow path plate 47R １ -47R ５ A connecting passage 475 is formed that extends linearly along the longer side of the top view rectangle. Also, the flow path plate 47R １ -47R ５ From the through hole 472, the flow path plate 47R １ -47R ５ A connecting passage 476 is formed that extends linearly along the other long side of the top-view rectangle. Although not shown, a flow path 3D for the fluid P formed by the partial flow path 34 is connected to these connecting passages 475 and 476. As a result, the fluid P can flow from the connecting passage 475 through the flow path 3D to the connecting passage 476.

[0120] Furthermore, as shown in Figures 30 and 31, the flow path plate 47R １ -47R １１ Of these, flow path plate 47R ７ -47R １１ From the through hole 473 to the flow path plate 47R ７ -47R １１ A connecting passage 477 is formed that extends linearly along the longer side of the top view rectangle. Also, the flow path plate 47R ７ -47R １１ From the through hole 474, the flow path plate 47R ７ -47R １１ A connecting passage 478 is formed that extends linearly along the other long side of the top-view rectangle. Although not shown, a flow path 3D for the fluid Q formed by the partial flow path 34 is connected to connecting passages 477 and 478. As a result, the fluid Q can flow from connecting passage 477 through the flow path 3D to connecting passage 478.

[0121] With this configuration, as shown in Figures 29(B) and 29(C), fluids P and Q flow through each of the flow path units 47. And in each of the flow path units 47, the flow path plate 47R １ -47R １１As these are stacked, the partial flow path 34 forms a flow path 3D for fluid P and a flow path 3D for fluid Q. These flow paths 3D for fluid P and flow paths 3D for fluid Q are arranged alternately in the X direction, and adjacent flow paths 3D in the X direction are intertwined with each other. As a result, in each flow path unit 47, the flow path plate 47R １ -47R １１ Heat exchange can occur between fluids P and Q via this medium.

[0122] Thus, the flow path unit 47 can perform heat exchange between fluids P and Q despite having the same number of plates as the flow path unit 43P or 44Q of Embodiment 3. The flow path unit 47 allows for miniaturization of both the flow path unit 47 itself and the heat exchanger according to Embodiment 4.

[0123] Furthermore, the intertwined flow channels 3D of each flow channel unit 47 are independent flow channels that do not communicate with one another. Figures 32 and 33 show the flow channels 3D.

[0124] Figure 32 is a top view showing how the numerous flow channels 3D in the heat exchanger 1D are intertwined. Figures 33(A) to 33(G) are cross-sectional views of the lines from A-A to G-G shown in Figure 32.

[0125] As shown in Figure 32, the flow channels 3D are intertwined with each other in the radial direction of the spiral. Furthermore, as shown in Figures 33(A) to 33(G), each flow channel 3D is independent and does not communicate with each other in the radial direction of the spiral. In detail, the inner walls of the intertwined flow channels 3D are formed separately. As a result, the intertwined flow channels 3D are independent of each other. Thus, similar to Embodiment 1, when the fluid P or Q flows through each flow channel 3D and undergoes helical motion, and collides with the inner wall of the flow channel 3D due to this helical motion, the heat exchanger according to Embodiment 4 increases the surface area of ​​the inner wall of the flow channel 3D into which the fluid P or Q collides, thereby increasing the heat exchange efficiency in the flow channel 3D. In addition, the material of the flow channel unit 47 is a material with high thermal conductivity, similar to Embodiment 3. Thus, in the heat exchanger according to Embodiment 4, heat transfer is enhanced between the intertwined flow channels 3D despite the fact that their inner walls are separated.

[0126] Furthermore, as shown in Figure 32, there are multiple flow path plates 47R １ -47R １１ The spiral channel 3D formed by this process includes a channel plate 47R, similar to the channel 3C in Embodiment 3. １ -47R １１ A discontinuous portion 33 is formed at each boundary. As a result, the development of the thermal boundary layer is inhibited even in the flow path 3D. Consequently, the heat exchange efficiency of the heat exchanger according to Embodiment 4 is high.

[0127] As described above, in the heat exchanger according to Embodiment 4, each flow path unit 47 is equipped with a plurality of flow path plates 47R1-47R11 that form a flow path 3D for the fluid P and a flow path 3D for the fluid Q. As a result, heat exchange between the fluids P and Q is possible in each flow path unit 47. Furthermore, in the heat exchanger according to Embodiment 4, the heat exchanger itself can be made smaller compared to Embodiment 3.

[0128] (Embodiment 5) The heat exchanger 1C according to Embodiment 3 and the heat exchanger according to Embodiment 4 may further be equipped with plates for discharging fluids P and Q in the event of device failure.

[0129] The heat exchanger 1E according to Embodiment 5 includes a discharge plate 57 in addition to the flow path units 43P and 44Q.

[0130] The heat exchanger 1E according to Embodiment 5 will be described below with reference to Figures 34 and 35. Embodiment 5 will be described mainly for its configuration which differs from that of Embodiments 1-4.

[0131] Figure 34 is an exploded perspective view of the heat exchanger 1E according to Embodiment 5. Figure 35(A) is a plan view of the partition plate 55 provided in the heat exchanger 1E. Figure 35(B) is a plan view of the discharge plate 57 provided in the heat exchanger 1E.

[0132] As shown in Figure 34, the heat exchanger 1E includes the outer plate 41, flow path units 43P and 44Q, and outer plate 42 described in Embodiment 3, as well as a discharge plate 57 sandwiched between two partition plates 55 and 56.

[0133] The outer plate 41, flow path units 43P, 44Q, and outer plate 42 have the same configuration as the outer plate 41, flow path units 43P, 44Q, and outer plate 42 described in Embodiment 3, except that (1) the shapes of the inlet and outlet holes 431, 432, 443, 444, communication holes 433, 434, 441, 442, etc. are circular when viewed from above, and (2) arc-shaped discharge grooves 51, 52 and 53, 54 are formed along the outer circumference of the communication holes 433, 434 of the flow path unit 43P and the communication holes 441, 442 of the flow path unit 44Q.

[0134] In contrast, the partition plates 55 and 56 have the same configuration as the partition plate 45 described in Embodiment 3, and also have discharge grooves 551, 552, 563, and 564 that connect to the arc-shaped discharge grooves 51, 52, 53, and 54 described above.

[0135] First, regarding the discharge grooves 51 and 52 of the flow path unit 43P connected to the discharge grooves 551 and 552 of the partition plates 55 and 56, the flow path unit 43P has discharge grooves 51 and 52 formed between the communication holes 433 and 434 and a number of spiral flow paths 3E. The discharge grooves 51 and 52 are formed in the shape of a circular arc, more specifically a semicircle, which is concentric with the communication holes 433 and 434 in a plan view. These discharge grooves 51 and 52 are provided to prevent fluid Q from leaking out of these communication holes 433 and 434 and mixing with the fluid P flowing through the flow paths 3E when the heat exchanger 1E is damaged.

[0136] The partition plate 55 also has discharge grooves 551 and 552 of a similar shape. Specifically, the partition plate 55 has through holes 501-504, of which through holes 503 and 504 are connected vertically to the communication holes 433 and 434 of the flow path unit 43P. Discharge grooves 51 and 52 are formed adjacent to these communication holes 433 and 434, and the partition plate 55 also has discharge grooves 551 and 552 formed adjacent to the through holes 503 and 504. The discharge grooves 551 and 552 have a semicircular shape that extends and bends along the outer circumference of the through holes 503 and 504. The discharge grooves 551 and 552 communicate with the semicircular discharge grooves 51 and 52 of the flow path unit 43P. This prevents fluid Q from leaking out of the through holes 503 and 504 and mixing with fluid P.

[0137] Furthermore, as shown in Figures 34 and 35, the partition plate 55 has discharge grooves 555 and 556 on the short side of the rectangular top view, extending a certain distance inward from the outer surface. This allows the partition plate 55 to discharge the fluid Q to the outside of the partition plate 55 when it leaks out.

[0138] Similar to the flow path unit 43P, the flow path unit 44Q also has discharge grooves 53 and 54 that have the same function as the discharge grooves 51 and 52, as shown in Figure 34. The discharge grooves 53 and 54 are positioned between the communication holes 441 and 442 and the numerous spiral flow paths 3E. Furthermore, the discharge grooves 53 and 54 have the same size and shape as the discharge grooves 51 and 52 of the flow path unit 43P. This prevents fluid P from leaking out of the communication holes 441 and 442 and mixing with fluid Q flowing through the flow paths 3E when the heat exchanger 1E is damaged.

[0139] To prevent fluid P from mixing with fluid Q by communicating with the discharge grooves 53 and 54 of the flow path unit 44Q, the partition plate 56 also has discharge grooves 561 and 562. The discharge grooves 561 and 562 have the same configuration and function as the discharge grooves 555 and 556 of the partition plate 55, except that (1) they have a semicircular shape that bends along the outer circumference of the through holes 502 and 503 of the partition plate 56, and (2) they communicate with the semicircular discharge grooves 53 and 54 of the flow path unit 44Q. For this reason, a detailed explanation is omitted. By having this configuration, the partition plate 56 prevents fluid P from mixing with fluid Q in the event of damage to the heat exchanger 1E.

[0140] Furthermore, the partition plate 56, like the partition plate 55, has discharge grooves 565 and 566. The discharge grooves 565 and 566 have the same configuration and function as the discharge grooves 555 and 556 of the partition plate 55. For this reason, a detailed explanation is omitted. By having this configuration, the partition plate 56 discharges the fluid P to the outside when the heat exchanger 1E is damaged. A discharge plate 57 is sandwiched between these partition plates 55 and 56.

[0141] As shown in Figure 35, the discharge plate 57 is formed to have the same outer shape as the partition plate 55. The discharge plate 57 has the same through holes 501-504 and discharge grooves 551 and 552 as the partition plate 55. The discharge plate 57 further has a discharge groove 579 connected to the discharge grooves 551 and 552. The discharge groove 579 extends in a matrix pattern on the plate surface of the discharge plate 57. Specifically, the discharge groove 579 has a shape in which a portion 577 extending linearly in the short direction and a portion 578 extending linearly in the long direction intersect and connect on the plate surface. Each end of portion 578 of the discharge groove 579 communicates with the discharge grooves 555 and 556 of the partition plate 55 adjacent to the discharge plate 57 on the +Z side as shown in Figure 34. Furthermore, each end of section 578 communicates with the discharge grooves 565 and 566 of the partition plate 56 adjacent to the discharge plate 57 and the -Z side, respectively. With this configuration, the discharge groove 579 collects fluid P or Q when the heat exchanger 1E is damaged, and further discharges the collected fluid P or Q to the outside of the heat exchanger 1E via the discharge grooves 555 and 556 of the partition plate 55 and the discharge grooves 565 and 566 of the partition plate 56.

[0142] As described above, the heat exchanger 1E according to Embodiment 5 is equipped with a discharge plate 57 positioned between the flow path units 43P and 44Q, which discharges the leaked fluids P and Q from the flow path units 43P and 44Q to the outside of the heat exchanger 1E itself. Therefore, the fluids P and Q that leak out in the heat exchanger 1E are less likely to mix with the fluids P and Q flowing through the flow path 3D. For example, if the fluids P and Q have an adverse effect on the human body when mixed, mixing is prevented, thus increasing safety.

[0143] Furthermore, since discharge grooves 51-54, 551, 552, 565, 566, etc. are formed in the flow path units 43P, 44Q and the partition plates 55, 56, even if fluids P and Q leak out within the heat exchanger 1E, these fluids P and Q can be quickly discharged. As a result, mixing of the leaked fluids P and Q can be prevented.

[0144] (Embodiment 6) In Embodiment 3-5, the flow path 3C-3E is integrated with the flow path units 43P and 44Q. However, the flow path 3C-3E is not limited to this. The flow path 3C-3E may be separate from the flow path units 43P and 44Q.

[0145] In the heat exchanger 1F according to Embodiment 6, the flow path units 43P and 44Q are formed by assembling the flow path component 438.

[0146] The heat exchanger 1F according to Embodiment 6 will be described below with reference to Figure 36. Embodiment 6 will be described mainly for its configuration which differs from that of Embodiments 1-5.

[0147] Figure 36 is an exploded perspective view of the heat exchanger 1F according to Embodiment 6.

[0148] As shown in Figure 36, the heat exchanger 1F is formed by stacking multiple flow path units 43P and 44Q alternately. These flow path units 43P and 44Q include a distribution component 437 and a flow path component 438 that is assembled to the distribution component 437.

[0149] In the flow path unit 43P, the distribution component 437 has the same external shape as the flow path units 43P and 44Q described in Embodiment 3. That is, the distribution component 437 is formed in the shape of a thick rectangular flat plate with rounded corners. The central region of the plate surface of the distribution component 437 is cut out in a rectangular shape, resulting in the shape of a square frame with rounded corners. The square frame of the distribution component 437 has inlet and outlet holes 431 and 432 and communication holes 433 and 434, as described in Embodiment 3. The inlet and outlet holes 431 and 432 communicate with the internal space of the square frame of the distribution component 437, while the communication holes 433 and 434 are separate from the internal space of the square frame. This allows the distribution component 437 to distribute or concentrate the fluid P and to allow the fluid Q to flow to the flow path unit 44Q.

[0150] Furthermore, the distribution component 437 of the flow path unit 44Q has a rectangular frame with communication holes 441 and 442, as described in Embodiment 3, and inlet and outlet holes 443 and 444. The communication holes 441 and 442 are separate from the internal space of the rectangular frame, while the inlet and outlet holes 443 and 444 communicate with the internal space of the rectangular frame of the distribution component 437. This allows the distribution component 437 of the flow path unit 44Q to distribute or concentrate the fluid Q, and further allows the fluid P to flow into the flow path unit 43P.

[0151] In contrast, the flow channel component 438 of the flow channel unit 43P is formed by the entanglement of metal pipes that form a flow channel 3F, which is the same shape as the spiral flow channel 3C described in Embodiment 3, as shown in Figure 36. The way in which the metal pipes of the flow channel 3F are entangled is the same as that of the flow channel 3C. Furthermore, the flow channel component 438 is shaped to fit into the internal space of the square frame of the distribution component 437. The flow channel component 438 is fitted into the square frame of the distribution component 437 of the flow channel unit 43P. As described above, the inlet and outlet holes 431 and 432 are in communication with the internal space of the square frame of the distribution component 437. Therefore, the fluid P distributed by the distribution component 437 flows through the flow channel component 438.

[0152] Although not shown in Figure 36, the flow channel component 438 of the flow channel unit 44Q is fitted into the square frame of the distribution component 437 of the flow channel unit 43Q. In addition, the flow channel component 438 has inlet and outlet holes 443 and 444 that communicate with the internal space of the square frame of the distribution component 437. As a result, the fluid Q distributed by the distribution component 437 flows through the flow channel component 438.

[0153] As described above, in the heat exchanger 1F according to Embodiment 6, the flow path units 43P and 44Q are formed by assembling the flow path component 438 to the distribution component 437. Since the flow path component 438 and the distribution component 437 are separate parts, the manufacturing of the flow path units 43P and 44Q is easy.

[0154] Furthermore, the flow channel component 438 only needs to have a helical flow channel 3F, and does not need to be formed by the entanglement of metal pipes. For example, the flow channel component 438 may be formed by stacking multiple plates, each having a hole. In this case, the holes in each plate can form a helical flow channel 3F through the stacking of the plates.

[0155] (Embodiment 7) In Embodiment 6, the flow path units 43P and 44Q are composed of a distribution component 437 and a flow path component 438 assembled to the distribution component 437. However, the flow path units 43P and 44Q are not limited to this. In addition to the distribution component 437 and the flow path component 438, the flow path units 43P and 44Q may also include other components.

[0156] In the heat exchanger 1G according to Embodiment 7, the flow path units 43P and 44Q include sealing members 439 and 440 in addition to the distribution component 437 and the flow path component 438.

[0157] The heat exchanger 1G according to Embodiment 7 will be described below with reference to Figures 37-39. Embodiment 7 will be described primarily for its configuration, which differs from that of Embodiments 1-6.

[0158] Figure 37 is an exploded perspective view of the heat exchanger 1G according to Embodiment 7. Figure 38 is a plan view of the distribution component 437 and the flow path component 438 of the heat exchanger 1G. Figure 39 is an enlarged view of the XXXIX region shown in Figure 38.

[0159] As shown in Figure 37, the heat exchanger 1G is equipped with sealing members 439 and 440 that close the gap between the distribution component 437 and the flow path component 438.

[0160] As described in Embodiment 6, the distribution component 437 is formed in the shape of a square frame with rounded corners. As a result, the distribution component 437 has an internal space in the shape of a square plate. A flow channel component 438, which is also formed in the shape of a square plate and has multiple flow channels 3G, is fitted into this internal space.

[0161] In the flow channel component 438, each flow channel 3G is the same shape as the helical flow channel 3C described in Embodiment 3. Although not shown in the diagram, each flow channel 3G extends its helical central axis C in the Y direction. Furthermore, multiple flow channels 3G are arranged in the X direction. Adjacent flow channels 3G in the X direction are intertwined with each other.

[0162] In a heat exchanger 1G with this configuration, tolerances can cause gaps between the distribution component 437 and the flow path component 438. Specifically, as shown in Figure 38, tolerances can cause a gap G1 between the wall surface on the +X side of the inner wall of the rectangular frame of the distribution component 437 and the +X surface of the flow path component 438. Also, a gap G2 can occur between the wall surface on the -X side of the same inner wall and the -X surface of the flow path component 438. On the other hand, the distribution component 437 has inlet and outlet holes 431, 432 or 443, 444 as described in Embodiment 3, allowing fluid P or Q to flow in the Y direction. Since the gaps G1 and G2 mentioned above extend in the Y direction, if the gaps G1 and G2 become large enough, the fluid P or Q that should flow into the flow path 3G of the flow path component 438 may flow into these gaps G1 and G2, reducing the flow rate of fluid P or Q into the flow path 3G. In that case, sufficient heat exchange cannot be performed in the flow path 3G.

[0163] Therefore, in order to solve these problems, the heat exchanger 1G is provided with sealing members 439 and 440 as shown in Figure 37. The sealing members 439 and 440 are installed between the distribution component 437 and the flow path component 438.

[0164] More specifically, as shown in Figure 37, the inner wall of the rectangular frame of the distribution component 437, on the +X side, has a recess C2 in the Y-direction center that is formed in the shape of a sinusoidal wave when viewed from above and is recessed in the +X direction. Also, on the -X side of the same inner wall, there is a recess C3 in the Y-direction center that is symmetrical to the recess C2, i.e., symmetrical along the Y axis, and is recessed in the -X direction. Furthermore, as shown in Figure 39, the -X surface of the flow channel component 438 has two minute recesses C4 and C5 arranged in the Y direction and recessed in the shape of a minute wave when viewed from above. Although not shown, the +X surface of the flow channel component 438 also has two minute recesses C4 and C5 of the same shape and arrangement.

[0165] As shown in Figure 37, the sealing members 439 and 440 have the shape of elongated strips, with the central portion bent into a sinusoidal wave shape and both ends bent into minute sinusoidal wave shapes. Of the respective parts of the sealing members 439 and 440, the central portion of the wave shape can be fitted into the recesses C2 and C3, and the ends of the wave shape can be fitted into the minute recesses C4 and C5. Furthermore, as shown in Figure 38, the sealing members 439 and 440 are fitted into the recesses C2 and C3, thereby sealing the gaps G1 and G2 described above. As a result, the sealing members 439 and 440 prevent the fluid P or Q from flowing through the gaps G1 and G2 and reducing the flow rate of the flow path 3G. In this way, the sealing members 439 and 440 suppress the gaps G1 and G2 from functioning as a bypass for the fluid P or Q. The sealing members 439 and 440 are also called bypass suppression members due to this function.

[0166] Furthermore, the sealing members 439 and 440 are formed from an elastic material such as resin or metal. In addition, the thickness of the sealing members 439 and 440 is greater than the gaps G1 and G2 to the extent that they can be fitted, and as a result, the sealing members 439 and 440 are compressed and elastically deformed inside the gaps G1 and G2. By elastically deforming in the gap G1, the sealing member 439 adheres tightly to the wall surface on the +X side of the inner wall of the square frame of the distribution component 437 and to the +X surface of the flow channel component 438. This allows the sealing member 439 to more effectively suppress the gap G1 from functioning as a bypass for the fluid P or Q. Similarly, the sealing member 440 adheres tightly to the wall surface on the -X side of the inner wall of the same gap G2 and to the -X surface of the flow channel component 438 by elastically deforming in the gap G2. This allows the sealing member 440 to more effectively suppress the gap G2 from functioning as a bypass for the fluid P or Q.

[0167] As described above, the heat exchanger 1G according to Embodiment 7 includes a sealing member 439 provided in the gap G1 between the wall surface on the +X side of the inner wall of the square frame of the distribution component 437 and the +X surface of the flow channel component 438. The heat exchanger 1G also includes a sealing member 440 provided in the gap G2 between the wall surface on the -X side of the same inner wall and the -X surface of the flow channel component 438. Therefore, in the heat exchanger 1G, it is prevented that the fluid P or Q flows through the gaps G1 and G2, and that the flow rate of the flow channel 3G decreases. As a result, the heat exchanger 1G has high heat exchange efficiency.

[0168] Furthermore, recesses C2 and C3 are formed in the inner wall surface on the +X side and the -X side of the square frame of the distribution component 437, and sealing members 439 and 440 are fitted into these recesses C2 and C3. As a result, sealing members 439 and 440 are less likely to shift, and are less likely to fall out of the gaps G1 and G2.

[0169] Furthermore, since the sealing members 439 and 440 are made of an elastic material, the gaps G1 and G2 can be sealed more reliably.

[0170] (Modification) In Embodiment 7, the recesses C2 and C3 formed in the distribution component 437 have a sinusoidal wave shape when viewed from above, but the shape of the recesses C2 and C3 is not limited to this. In the heat exchanger 1G, it is optional whether or not the distribution component 437 has recesses C2 and C3. Therefore, when the distribution component 437 has recesses C2 and C3, the shape of the recesses C2 and C3 is arbitrary.

[0171] Figure 40 is an enlarged plan view of a modified example of a distribution component 437 provided in the heat exchanger 1G according to Embodiment 7.

[0172] As shown in Figure 40, the distribution component 437 may have a recess C3 that is arc-shaped, or more specifically, semi-circular, when viewed from above. Although not shown, the distribution component 437 may also have a recess C2 that is symmetrical. This is because the sealing members 439 and 440 can be fitted into recesses C2 and C3 of this shape, and the positions of the sealing members 439 and 440 can be determined.

[0173] Furthermore, in Embodiment 7, the flow channel component 438 has minute recesses C4 and C5, but the presence or absence of these minute recesses C4 and C5 is optional. As a result, the shape of the minute recesses C4 and C5 when the flow channel component 438 has them is also optional. For example, the minute recesses C4 and C5 may be arc-shaped when viewed from above, or they may be triangular when viewed from above. Moreover, as shown in Figure 40, the flow channel component 438 does not have to have minute recesses C4 and C5.

[0174] (Embodiment 8) In the flow path units 43P and 44Q according to Embodiment 3, the flow path plate 43P １ -43P １１ Rather than simply being stacked, the flow path plate 43P １ -43P １１ It is explained that they may be brazed together. In the flow path units 43P and 44Q according to embodiments 6 and 7, the flow path units 43P and 44Q may be brazed together with the partition plates 45 adjacent to them in the stacking direction, i.e., in the stacking direction.

[0175] In the heat exchanger 1H according to embodiment 8, the distribution component 437 and the flow path component 438 of the flow path units 43P and 44Q are brazed to the partition plate 45.

[0176] The heat exchanger 1H according to Embodiment 8 will be described below with reference to Figures 41-44. Embodiment 8 will be described primarily for its configuration, which differs from that of Embodiments 1-7.

[0177] Figure 41 is a right side view of the heat exchanger 1H when the brazing materials 48 and 49 have been removed from the heat exchanger 1H according to Embodiment 8. Figure 42 is a right side view of the distribution component 437, the flow path component 438, and the brazing materials 48 and 49 provided in the heat exchanger 1H. Figure 43 is a top view of the brazing materials 48 and 49. Figure 44 is a right side view of the heat exchanger 1H. For ease of understanding, in Figure 42, the brazing materials 48 and 49 are shown with dotted lines and no hatching is applied.

[0178] In the heat exchanger 1H, the distribution component 437 and the flow path component 438 of the flow path units 43P and 44Q may have different thicknesses due to tolerances. For example, as shown in Figure 41, the thickness of the flow path component 438 may be greater than the thickness of the distribution component 437. In that case, the flow path component 438 will protrude more than the distribution component 437 on the upper and lower surfaces of the flow path units 43P and 44Q, resulting in uneven surfaces on the upper and lower surfaces of the flow path units 43P and 44Q. As a result, even if the partition plate 45 is attempted to be brazed to the flow path units 43P and 44Q, the unevenness of the upper and lower surfaces of the flow path units 43P and 44Q may cause a poor joint, resulting in leakage of fluid P or Q.

[0179] Therefore, in order to prevent joint defects, the heat exchanger 1H uses brazing materials 48 and 49 of a specific thickness during manufacturing. Specifically, as shown in Figure 42, during the manufacturing of the heat exchanger 1H, brazing materials 48 and 49 that satisfy the following equation 1 are used to braze the flow path units 43P and 44Q to the partition plate 45, respectively.

[0180] T １ -T ２ <T ３ +T ４ ...Equation 1 Here, T１ This is the thickness value of the flow channel component 438, and T ２ This is the thickness value of the distribution component 437. Also, T ３ This is the thickness value of the brazing material 48 shown in Figure 44, which is positioned below the flow path unit 43P or 44Q to be brazed, in order to braze it with the partition plate 45 positioned below the flow path unit 43P or 44Q to be brazed. ４ This value represents the thickness of the brazing material 49 that is placed above the flow path unit 43P or 44Q to be brazed, in order to braze the flow path unit 43P or 44Q to be brazed with the partition plate 45 that is placed above it.

[0181] In the manufacture of heat exchanger 1H, before the brazing process, a thickness T like this is applied. ３ , T ４ The brazing materials 48 and 49 are sandwiched between the flow channel unit 43P or 44Q and the partition plate 45. This forms a laminate 46 of the flow channel units 43P or 44Q and the partition plate 45. Next, the laminate 46 is heated to melt the brazing materials 48 and 49. Since the brazing materials 48 and 49 satisfy the relationship in Equation 1 described above, even if there is a difference in thickness between the flow channel component 438 and the distribution component 437, the molten brazing materials 48 and 49 fill in the irregularities caused by the difference in thickness, and these irregularities are filled. As a result, the occurrence of poor bonding between the flow channel unit 43P or 44Q and the partition plate 45 is suppressed.

[0182] The brazing materials 48 and 49 have a thickness that satisfies the relationship in formula 1 described above, but it is desirable that the planar shape of the brazing materials 48 and 49 is the same as the planar shape of the distribution component 437, as shown in Figure 43. Furthermore, the brazing materials 48 and 49 may be in the form of a paste or foil, or they may be clad materials in which the upper and lower surfaces of the distribution component 437 are covered with brazing material.

[0183] Furthermore, the flow path units 43P and 44Q and the partition plate 45 are examples of flow path units as defined in this disclosure. Also, the brazing materials 48 and 49 are examples of the first brazing material and the second brazing material as defined in this disclosure.

[0184] As described above, in the manufacturing method of the heat exchanger 1H according to Embodiment 8, the thickness of the flow path component 438 is T１ 、The thickness of the distribution component 437 is T ２ and the thicknesses of the brazing materials 48 and 49 that sandwich the flow path component 438 and the distribution component 437 in the stacking direction of the flow path units 43P and 44Q are T ３ 、T ４ When this is the case, the brazing materials 48 and 49 used in the brazing process satisfy the relationship of T １ -T ２ <T ３ +T ４ As a result, even when there is a difference in the thicknesses of the flow path component 438 and the distribution component 437, the brazing materials 48 and 49 that satisfy the above relationship melt in the brazing process, and the unevenness due to the difference in the thicknesses of the flow path component 438 and the distribution component 437 is filled. As a result, the occurrence of poor bonding between the flow path units 43P and 44Q and the partition plate 45 is suppressed. Thereby, in the manufactured heat exchanger 1H, leakage of the fluids P and Q is unlikely to occur.

[0185] As described above, the heat exchangers 1A - 1H and the method for manufacturing the heat exchangers 1A - 1H according to the embodiments of the present disclosure have been described, but the heat exchangers 1A - 1H and the method for manufacturing the heat exchangers 1A - 1H are not limited thereto.

[0186] For example, in Embodiments 1, 2, and 6, the flow paths 3A, 3B, and 3F are simply formed of metal pipes. As a result, the entire flow paths 3A, 3B, and 3F are made of the same metal material. However, the flow paths 3A - 3G are not limited thereto. The inner walls of the flow paths 3A - 3G may be coated with a corrosion - resistant material.

[0187] Also, the flow path plates 43P １ -43P １１ 、47R １ -47R １１ 、the partition plates 45, 55, 56, and the flow path units 43P and 44Q may also be coated with a corrosion - resistant material. Also, the brazing materials 48 and 49 may also be coated with a corrosion - resistant material.

[0188] FIG. 45 is an enlarged schematic view of a partial region of FIG. 28(E). In FIG. 45, the brazing materials 48 and 49 are shown by dotted lines.

[0189] Due to manufacturing variations, as shown in Figure 45, the flow path plate 43P forms the flow path units 43P and 44Q. １ -43P １１ The following is exposed in the channel 3C. Also, the brazing materials 48 and 49 are exposed in the channel 3C. Therefore, the channel plate 43P １ -43P １１ The brazing materials 48 and 49 may also be coated with corrosion-resistant material. Furthermore, the flow path units 43P and 44Q may also be coated with corrosion-resistant material.

[0190] The corrosion-resistant material should be coated with the following film. The conditions for this coating are described below.

[0191] Figure 46 is a graph showing the relationship between the film thickness of the corrosion-resistant material covering the inner wall of the flow path 3A in a modified example of heat exchanger 1A and the amount of heat exchange. The inventors formed a coating film of a corrosion-resistant material, specifically a resin material, on the inner wall of the flow path 3A, and simulated the heat exchange when a high-temperature fluid P and a low-temperature fluid Q were circulated through the modified example of heat exchanger 1A equipped with the flow path 3A. Figure 46 shows the results of that simulation. In Figure 46, the horizontal axis of the graph shows the value obtained by dividing the film thickness [μm] of the resin material coating film by the thermal conductivity [W / mK] of the coating film. The vertical axis of the graph shows the amount of heat exchange normalized to 1 when the film thickness of the coating film is 0, i.e., when there is no coating film.

[0192] As shown in Figure 46, the normalized heat exchange rate of the modified heat exchanger 1A shows a relationship similar to that obtained by dividing the film thickness of the coating film by the thermal conductivity of the coating film, inversely proportional to the value obtained. That is, as the value obtained by dividing the thermal conductivity of the coating film by the film thickness of the coating film increases, the normalized heat exchange rate decreases sharply. As a result, when the value obtained by dividing the film thickness of the coating film by the thermal conductivity of the coating film is 85 ([μm] / [W / mK]) or less, the normalized heat exchange rate becomes 0.6 or more, and the original performance of the heat exchanger 1A can be utilized. For this reason, in the modified heat exchanger 1A, it is desirable that the value obtained by dividing the film thickness of the coating film by the thermal conductivity of the coating film be 85 or less.

[0193] Thus, the inner wall of the flow path 3A-3G and the flow path plate 43P１ -43P １１ , 47R １ -47R １１ The outer surfaces of the partition plates 45, 55, 56, the flow path units 43P, 44Q, and the brazing materials 48, 49 may be coated with a corrosion-resistant material. In this case, it is desirable that the value obtained by dividing the thermal conductivity of the coating film by the thickness of the coating film is 85 or less.

[0194] Furthermore, in Embodiments 1-8, the fluids to be exchanged for heat are a high-temperature fluid P and a fluid Q that has the same composition as the high-temperature fluid P but is at a lower temperature. However, fluids P and Q are not limited to these. Fluids P and Q can be any fluids to be exchanged for heat. For this reason, fluids P and Q may have the same composition as each other, that is, the substances that make up each other and their proportions, or they may be different. For example, fluids P and Q may be hot water and water, steam and water, or a refrigerant and water.

[0195] In Embodiments 1-8, the helical shape of each channel 3A-3G has a constant diameter and a constant pitch p. However, the helical shape of the channels 3A-3G is not limited to this. The diameter and pitch p of the helix may change. In that case, for example, the diameter may increase and then decrease at a constant period. Also, the pitch p may increase and then decrease at a constant period.

[0196] Furthermore, the heat exchanger 1A-1H described in Embodiment 1-8 is applicable to air conditioners, water heaters, oil coolers, and the like.

[0197] As described above, the heat exchanger 1A-1H and the method for manufacturing the heat exchanger 1A-1H are not limited to the embodiments described above, and various modifications and substitutions can be made. Various forms of this disclosure are described below as appendices.

[0198] (Note 1) A heat exchanger comprising: a heat-conducting body; and a plurality of flow channels, each having a helical shape, through which a fluid flows, thereby transferring heat from the fluid to the body, wherein the plurality of flow channels are arranged in a first direction perpendicular to the central axis of the helix and a second direction perpendicular to the central axis of the helix and the first direction, and in the plurality of flow channels, the flow channels adjacent to each other in at least one of the first and second directions are intertwined with each other. (Note 2) The heat exchanger according to Note 1, wherein in the plurality of flow channels, the flow channels adjacent to each other in either the first or second direction are intertwined with each other. (Note 3) The heat exchanger according to Note 1 or 2, wherein the plurality of flow channels satisfy the relationship 0 < d < 2A, where d is the distance between the central axes of the helix of the intertwined flow channels and A is the amplitude of the helix in the direction in which the flow channels intertwine with each other. (Note 4) The heat exchanger according to any one of Notes 1 to 3, wherein the intertwined flow channels are formed with their inner walls separated, thereby allowing the fluid to flow separately. (Note 5) The heat exchanger according to any one of Notes 1 to 3, wherein the intertwined flow channels are connected at their intertwined portions, thereby allowing the fluid to flow between them. (Note 6) The heat exchanger according to any one of Notes 1 to 3, comprising: a first distributor that distributes the high-temperature fluid to some of the flow channels among the plurality of flow channels; and a second distributor that distributes the low-temperature fluid to the remaining portion of the plurality of flow channels. (Note 7) The heat exchanger according to Note 6, wherein the first distributor supplies the high-temperature fluid from one end portion of the partial flow path, and the second distributor supplies the low-temperature fluid from the other end portion of the remaining partial flow path, which is opposite to the one end portion, so that the low-temperature fluid flows in the partial flow path in the opposite direction to the direction in which the high-temperature fluid flows. (Note 8) The heat exchanger according to Note 6, wherein the first distributor and the second distributor alternately supply the high-temperature fluid and the low-temperature fluid to the plurality of flow paths arranged in a direction in which the flow paths intertwine with each other.(Note 9) In the plurality of flow paths, the flow paths whose central axes of the helix are adjacent in either the first direction or the second direction are intertwined with each other, the flow paths whose central axes of the helix are adjacent in either the first direction or the second direction are not intertwined with each other, the intertwined flow paths are in communication with each other, the fluid flows between the intertwined flow paths, and the first and second distributors alternately supply the high-temperature fluid and the low-temperature fluid to the flow paths whose central axes of the helix are adjacent in either the first or second direction, as described in Note 6. (Note 10) The heat exchanger according to Note 2, wherein the main body comprises a plurality of stacked flow path units, each having the flow path, and each of the flow path units has a portion of the flow path formed thereon in either the first direction or the second direction with the central axis of the spiral adjacent to it, and the entire flow path formed by stacking the plurality of flow path units in the other of the first direction or the second direction with the central axis of the spiral adjacent to it, and the plurality of flow path units are stacked in the other of the first direction or the second direction. (Note 11) The heat exchanger according to Note 10, wherein among the plurality of flow path plates, adjacent flow path plates in the stacking direction are joined together by brazing. (Note 12) In each of the flow path units, the flow paths adjacent to each other in either the first direction or the second direction are intertwined with each other, and the intertwined flow paths are formed with their inner walls separated, thereby allowing the fluid to flow separately, as described in Note 10 or 11. (Note 13) In each of the flow path units, the flow paths adjacent to each other in either the first direction or the second direction are intertwined with each other, and the intertwined flow paths are formed with their intertwined portions communicating, thereby allowing the fluid to flow between them, as described in Note 10 or 11.(Note 14) The heat exchanger according to any one of Notes 10 to 13, further comprising a discharge plate having a discharge passage and disposed between the flow path units to discharge the leaked fluid to the outside of the heat exchanger itself when the fluid leaks from the flow path unit. (Note 15) The heat exchanger according to Note 2, wherein the main body comprises a plurality of stacked flow path units, each having the flow path, and each flow path unit comprises a flow path component having a plurality of flow paths with the central axes of the spiral adjacent to each other in either the first direction or the second direction, and a distribution component that houses the flow path component and distributes the fluid supplied from the outside to each of the plurality of flow paths of the flow path component, and the plurality of flow path units are stacked in either the first direction or the second direction. (Note 16) The heat exchanger according to Note 15, wherein the distribution component has the shape of a frame for housing the flow channel component, and a sealing member is provided between the inner wall of the frame facing either the first direction or the second direction and the flow channel component. (Note 17) The heat exchanger according to any one of Notes 1 to 16, wherein the inner walls of the plurality of flow channels are covered with a corrosion-resistant material. (Note 18) The heat exchanger according to Note 17, wherein the corrosion-resistant material is a resin, and the value obtained by dividing the thickness of the coating film formed by the corrosion-resistant material by the thermal conductivity is 85 or less. (Note 19) A method for manufacturing a heat exchanger as described in any one of Notes 1 to 9, the method comprising: a step of forming the plurality of flow paths with metal tubes; a step of electrodepositing the inner walls of the metal tubes; and a step of forming the main body having the plurality of flow paths by casting the metal tubes with a heat-conductive metal, wherein the step of forming the main body having the plurality of flow paths is performed before or after the step of electrodepositing. (Note 20) A method for manufacturing a heat exchanger as described in Note 10, comprising: a step of assembling each of the flow path units by stacking a plurality of flow path plates and further joining the plurality of flow path plates; and a step of electrodepositing the inner walls of the flow paths.(Note 21) A method for manufacturing a heat exchanger as described in Note 15, comprising the steps of: stacking a plurality of flow path units, each containing the flow path component and the distribution component, and inserting brazing material between adjacent flow path units in the stacking direction to form a laminate; and heating the laminate to melt the brazing material and brazing the flow path units, wherein in the step of forming the laminate, the thickness of the flow path component and the distribution component of a specific flow path unit among the plurality of flow path units is T. １ , T ２ The thickness of the first brazing material that is adjacent to the specific flow channel unit in the stacking direction and in one direction is set to T. ３ Of the brazing material, the thickness of the second brazing material adjacent to the specific flow channel unit in the stacking direction and in other directions is T. ４ In this case, the first brazing material and the second brazing material are T １ -T ２ <T ３ +T ４ A method for manufacturing a heat exchanger that satisfies the following relationship.

[0199] This disclosure allows for various embodiments and modifications without departing from the broad spirit and scope of this disclosure. Furthermore, the embodiments described above are for illustrative purposes only and do not limit the scope of this disclosure. In other words, the scope of this disclosure is indicated by the claims, not by the embodiments. Various modifications made within the scope of the claims and the equivalent significance of the disclosure are considered to be within the scope of this disclosure.

[0200] This application is based on Japanese Patent Application No. 2025-009362, filed on 22 January 2025. The entire specification, claims, and drawings of Japanese Patent Application No. 2025-009362 are incorporated herein by reference.

[0201] 1A-1H Heat exchanger, 2A, 2B Distributor, 3A-3G Flow path, 4A-4C Main body, 21P, 21Q Inlet section, 22P, 22Q Piping section, 23P, 23Q Piping section, 24P, 24Q Outlet section, 31, 32 Joint section, 33 Discontinuous section, 34 Partial flow path, 41, 42 Outer plate, 43P Flow path unit, 43P １ -43P １１ Flow channel plate, 44Q; Flow channel unit, 45; Partition plate, 46; Laminate, 47; Flow channel unit, 47R １ -47R １１ Flow path plate, 48, 49 Brazing material, 51-54 Discharge groove, 55, 56 Partition plate, 57 Discharge plate, 221 Branch pipe section, 222, 223 Branch pipe, 231 Branch pipe section, 232 Branch pipe, 431, 432 Inlet / outlet hole, 433, 434 Connecting hole, 435, 436 Connecting passage, 437 Distribution component, 438 Flow path component, 439, 440 Sealing member, 441, 442 Connecting hole, 443, 444 Inlet / outlet hole, 445, 446 Flow path, 451-454 Connecting hole, 471-474 Through hole, 475-478 Connecting passage, 501-504 Through hole, 551, 552, 555, 556, 561-566 Discharge groove, 577, 578 Part, 579 Discharge groove, C central axis, C1 center line, C2, C3 recess, C4, C5 minute recess, G1, G2 gap, p pitch, P, Q fluid, T １ -T ４ Thickness.

Claims

1. A heat exchanger comprising: a heat-conducting body; and a plurality of flow channels, each having a helical shape, through which a fluid flows, thereby transferring heat from the fluid to the body, wherein the plurality of flow channels are arranged in a first direction perpendicular to the central axis of the helix and a second direction perpendicular to the central axis of the helix and the first direction, and in the plurality of flow channels, the flow channels adjacent to each other in at least one of the first and second directions are intertwined with each other.

2. The heat exchanger according to claim 1, wherein in the plurality of flow paths, the flow paths that are adjacent to each other in either the first direction or the second direction are intertwined with each other.

3. The heat exchanger according to claim 1 or 2, wherein the plurality of flow paths satisfy the relationship 0 < d < 2A, where d is the distance between the central axes of the helices of the intertwined flow paths, and A is the amplitude of the helices in the direction in which the flow paths intertwine.

4. The heat exchanger according to any one of claims 1 to 3, wherein the intertwined flow channels are formed with their inner walls separated, thereby allowing the fluid to flow separately.

5. The heat exchanger according to any one of claims 1 to 3, wherein the intertwined flow channels are connected to each other, thereby allowing the fluid to flow between them.

6. A heat exchanger according to any one of claims 1 to 3, comprising: a first distributor for distributing the high-temperature fluid to some of the plurality of flow paths; and a second distributor for distributing the low-temperature fluid to the remaining portion of the plurality of flow paths.

7. The heat exchanger according to claim 6, wherein the first distributor supplies the high-temperature fluid from one end portion of the partial flow path, and the second distributor supplies the low-temperature fluid from the other end portion of the remaining partial flow path, which is opposite to the one end portion, so that the low-temperature fluid flows in the partial flow path in the opposite direction to the direction in which the high-temperature fluid flows.

8. The heat exchanger according to claim 6, wherein the first and second distributors alternately supply the high-temperature fluid and the low-temperature fluid to the plurality of flow paths arranged in a direction in which the flow paths intertwine with each other.

9. In the plurality of flow paths, the flow paths whose central axes of the helix are adjacent in either the first direction or the second direction are intertwined with each other, the flow paths whose central axes of the helix are adjacent in either the first direction or the second direction are not intertwined with each other, the intertwined flow paths are in communication with each other, the fluid flows between the intertwined flow paths, and the first and second distributors alternately supply the high-temperature fluid and the low-temperature fluid to the flow paths whose central axes of the helix are adjacent in either the first or second direction, the heat exchanger according to claim 6.

10. The heat exchanger according to claim 2, wherein the main body comprises a plurality of stacked flow path units, each having the flow path, each of the flow path units having a portion of the flow path formed thereon in either the first direction or the second direction with the central axis of the helix adjacent to it, and the plurality of flow path units are stacked in either the first direction or the second direction to form the entire flow path with the central axis of the helix adjacent to it, and the plurality of flow path units are stacked in either the first direction or the second direction.

11. The heat exchanger according to claim 10, wherein, among the plurality of flow path plates, adjacent flow path plates in the stacking direction are joined together by brazing.

12. In each of the flow path units, the flow paths adjacent to each other in either the first direction or the second direction are intertwined with each other, and the intertwined flow paths are formed with their inner walls separated, thereby allowing the fluid to flow separately, as described in claim 10 or 11.

13. In each of the flow path units, the flow paths adjacent to each other in either the first direction or the second direction are intertwined with each other, and the intertwined flow paths are in communication with each other at their intertwined portions, thereby allowing the fluid to flow between them, as described in claim 10 or 11.

14. A heat exchanger according to any one of claims 10 to 13, further comprising a discharge plate having a discharge passage and disposed between the flow path units, which discharges the leaked fluid to the outside of the heat exchanger itself when the fluid leaks from the flow path units.

15. The heat exchanger according to claim 2, wherein the main body comprises a plurality of stacked flow path units, each having the flow path, each of the flow path units comprising: a flow path component having a plurality of flow paths with the central axes of the spiral adjacent to each other in either the first direction or the second direction; and a distribution component housing the flow path component and distributing the fluid supplied from the outside to each of the plurality of flow paths of the flow path component, and the plurality of flow path units are stacked in either the first direction or the second direction.

16. The heat exchanger according to claim 15, wherein the distribution component has the shape of a frame for housing the flow path component, and a sealing member is provided between the inner wall of the frame facing either the first direction or the second direction and the flow path component.

17. The heat exchanger according to any one of claims 1 to 16, wherein the inner walls of the plurality of flow paths are covered with a corrosion-resistant material.

18. The heat exchanger according to claim 17, wherein the corrosion-resistant material is a resin, and the value obtained by dividing the thickness of the coating film formed by the corrosion-resistant material by the thermal conductivity is 85 or less.

19. A method for manufacturing a heat exchanger according to any one of claims 1 to 9, the method comprising: a step of forming the plurality of flow channels with metal tubes; a step of electrodepositing the inner walls of the metal tubes; and a step of forming the main body having the plurality of flow channels by casting the metal tubes with a heat-conductive metal, wherein the step of forming the main body having the plurality of flow channels is performed before or after the step of electrodepositing.

20. A method for manufacturing a heat exchanger according to claim 10, comprising the steps of: assembling each of the flow path units by stacking a plurality of the flow path plates and further joining the plurality of the flow path plates; and electrodepositing the inner wall of the flow path.

21. A method for manufacturing a heat exchanger according to claim 15, comprising the steps of: stacking a plurality of flow path units, each comprising a distribution component housing the flow path component, and inserting brazing material between adjacent flow path units in the stacking direction to form a laminate; and heating the laminate to melt the brazing material and brazing the flow path units, wherein in the step of forming the laminate, the thickness of the flow path component and the distribution component of a specific flow path unit among the plurality of flow path units is set to T １ , T ２ The thickness of the first brazing material that is adjacent to the specific flow channel unit in the stacking direction and in one direction is set to T. ３ Of the brazing material, the thickness of the second brazing material adjacent to the specific flow channel unit in the stacking direction and in other directions is T. ４ In this case, the first brazing material and the second brazing material are T １ -T ２ <T ３ +T ４ A method for manufacturing a heat exchanger that satisfies the following relationship.

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