Heat exchanger

Abstract

A heat exchanger in which heat exchange efficiency is improved, deflection of heat exchange members is suppressed, and a gap between the heat exchange members is kept constant. The heat exchanger stacks a plurality of heat exchange members and exchanges heat between internal heat medium flowing in a heat medium flow path provided in the heat exchange members and external heat medium flowing on an outer surface of the heat exchange members, the heat medium flow path including: a branch portion that branches the internal heat medium; and a first merging portion that merges the internal heat medium after being branched by the branch portion, the branch portion having a plurality of branch flow paths that protrude to an outer side of the heat exchange member and are arranged in a flow direction of the external heat medium, the first merging portion having: a first protruding portion that communicates with the plurality of branch flow paths and protrudes to the outer side of the heat exchange member in the flow direction of the external heat medium; and a second protruding portion that further protrudes to the outer side from the first protruding portion.

Description

TECHNICAL FIELD

[0001] The present application relates to a heat exchanger, and particularly to a heat exchanger in which a plurality of heat exchange members are stacked. BACKGROUND

[0002] In the past, a finless heat exchanger has been known, in which a plurality of flat heat exchange members each having a flow path of a heat medium inside is stacked. In the finless heat exchanger, the heat exchange members are stacked to form an air flow path crossing the flow path of the heat medium between the heat exchange members, and the heat medium passing through the flow path of the heat medium and the air passing through the air flow path are caused to exchange heat at the surface of each heat exchange member. At this time, the straight running of the air passing through the air flow path is hindered by the irregularities of the surface of the heat exchange member formed by the flow path of the heat medium, so that the heat conduction between the heat medium and the air is promoted. On the other hand, in the finless heat exchanger described above, since no fins such as corrugated fins are provided in each heat exchange member, the heat exchange members can be deflected, so that the interval between the heat exchange members can not be kept constant due to the deflection.

[0003] Therefore, for example, in Patent Literature 1, a structure is disclosed in which, in a heat exchanger in which a plurality of flat heat exchange members each having a communication flow path through which a heat medium flows are stacked, a plurality of protrusions (embossments) are formed at a portion of each heat exchange member at which the communication flow path is not formed, and the protrusions are brought into abutment with an adjacent heat exchange member. In the heat exchanger of Patent Literature 1, the deflection of the heat exchange members is suppressed by bringing the protrusions formed in one heat exchange member into abutment with another heat exchange member, and the interval between the adjacent heat exchange members is kept at a desired interval.

[0004] PRIOR ART DOCUMENTS

[0005] PATENT LITERATURE

[0006] Patent Literature 1: Japanese Patent No. 6531325

[0007] However, in the heat exchanger of Patent Literature 1, the protrusions in each heat exchange member are provided at a portion at which the communication flow path is not formed. That is, in the heat exchange member, since the communication flow path (convex portion) cannot be formed to the extent comparable to the protrusions, the total number of irregularities formed on the surface of the heat exchange member is reduced. As a result, the number of convex portions that change the flow direction of the air in the air flow path to hinder the straight running of the air is insufficient, and the heat exchange efficiency in the heat exchanger cannot be improved. SUMMARY

[0008] The present invention was made in view of the above-mentioned situation, and its object is to improve heat exchange efficiency, suppress the deflection of heat exchange components, and maintain a constant spacing between heat exchange components in a heat exchanger with multiple stacked heat exchange components.

[0009] One aspect of the present invention provides a heat exchanger having multiple heat exchange components stacked together, and enabling internal heat medium flowing in a heat medium flow path disposed within the heat exchange components to exchange heat with external heat medium flowing on the outer surface of the heat exchange components. The heat medium flow path comprises: a diversion section that diverts the internal heat medium; and a first confluence section that merges the internal heat medium diverted by the diversion section. The diversion section has multiple diversion channels that protrude outward from the heat exchange components and are arranged along the flow direction of the external heat medium. The first confluence section has: a first protrusion that communicates with the multiple diversion channels and protrudes outward from the heat exchange components along the flow direction of the external heat medium; and a second protrusion that further protrudes outward from the first protrusion.

[0010] According to the present invention, in a heat exchanger with multiple stacked heat exchange components, heat exchange efficiency can be improved, deflection of heat exchange components can be suppressed, and the spacing between heat exchange components can be kept constant. Attached Figure Description

[0011] Figure 1 This is a schematic diagram showing the structure of a heat exchanger according to an embodiment of the present invention.

[0012] Figure 2 This is a schematic diagram showing the structure of the heat exchange components that constitute the heat exchanger of an embodiment of the present invention.

[0013] Figure 3 This is a diagram showing the schematic structure of the heat exchange components that constitute the heat exchanger of an embodiment of the present invention.

[0014] Figure 4 This is a diagram of the heat exchange components constituting a heat exchanger according to an embodiment of the present invention, wherein... Figure 4 (A) is a side view. Figure 4 (B) is the front view. Figure 4 (C) is the rear view.

[0015] Figure 5 (A) to (D) are Figure 4 The heat exchange component shown in (B) is a cross-sectional view, wherein, Figure 5 (A) is a sectional view of AA. Figure 5 (B) is a sectional view of BB. Figure 5(A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 5 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view.

[0016] Figure 6 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 6 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 6 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view.

[0017] Figure 7 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 6 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 7 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 7 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 7 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 7 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view.

[0018] Figure 8 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 8 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 8 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 8 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view.

[0019] Figure 9 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 8 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 9 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 9 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 9 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 9 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view.

[0020] Figure 10 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 10 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 10 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view.

[0021] Figure 11 Figure 10 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 11 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 11 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 11 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view. Figure 11 (A) is a side view, (B) is a front view, (C) is a rear view, and (D) is a D-D cross-sectional view.

[0022] Figure 12 is a sectional view showing a modification of the first manifold in the heat exchange member of the heat exchanger constituting the embodiment of the present application.

[0023] Figure 13 is a sectional view showing a modification of the first manifold in the heat exchange member of the heat exchanger constituting the embodiment of the present application.

[0024] Figure 14 is a table relating to parameters and values thereof provided in the heat exchange member of the heat exchanger constituting the embodiment of the present application.

[0025] Figure 15 is a graph showing the parameters shown in the table of Figure 14 .

[0026] Figure 16 is a table showing the analysis results relating to the heat exchanger designed using the parameters shown in the table of Figure 14 .

[0027] Figure 17 is a graph showing the relationship between L1 and the heat exchange amount obtained according to the parameters of Figure 14 .

[0028] Figure 18 is a graph showing the relationship between L3 and the heat exchange amount obtained according to the parameters of Figure 14 .

[0029] Figure 19 is a graph showing the relationship between the thermal conductivity of the heat transfer plate and the heat exchange amount. DETAILED DESCRIPTION

[0030] Hereinafter, the embodiments of the present application will be described in detail with reference to the drawings. In the following description, the same symbols are used to denote the same functions, and the repeated description in the respective drawings will be appropriately omitted.

[0031] The schematic structure of the heat exchanger 1 of the embodiment of the present application is shown in Figure 1 . The heat exchanger 1 is applied to, for example, a vehicle air conditioning device or the like, and as shown in Figure 1 , includes a core portion 10 having a plurality of heat exchange members 11 through which an internal heat medium flows, first and second side plates 20A and 20B arranged at both ends of the core portion 10, and first and second tubes 30A and 30B provided to the core portion 10 with the first side plate 20A interposed therebetween and serving as an inlet and an outlet for the internal heat medium.

[0032] In the heat exchanger 1, heat exchange occurs between the internal heat medium flowing through the heat medium flow path 14 of the plurality of heat exchange members 11 flowing into the core 10 via the first pipe 30A and the external heat medium flowing on the surface of the heat exchange members 11. The internal heat medium then flows out of the core 10 via the second pipe 30B. At this time, the flow direction of the internal heat medium flowing in the heat medium flow path 14 within the heat exchange member 11 intersects (orthogonally) the flow direction of the external heat medium flowing on the surface of the heat exchange member 11.

[0033] like Figure 1 and Figure 2 As shown, the core 10 includes a plurality of heat exchange members 11 arranged at equal intervals. Each heat exchange member 11 is configured such that a first heat-conducting plate 41, formed by stamping or other processes on a metal plate, overlaps with a second heat-conducting plate 42. Figure 3 The first heat-conducting plate 41 and the second heat-conducting plate 42 will be described later.

[0034] like Figure 3 and Figure 4 As shown, the heat exchange component 11 is provided with a first manifold 12, a second manifold 13 and a heat medium flow path 14. The first manifold 12 is located on one side of the heat exchanger, the second manifold 13 is located on the other side of the heat exchanger, and the heat medium flow path 14 is formed between the first manifold 12 and the second manifold 13, and communicates with the first manifold 12 and the second manifold 13 to allow internal heat medium to flow.

[0035] exist Figure 4 The side view, front view, and rear view of the heat exchange component 11 are shown in (A) to (C). Furthermore, in Figure 5 (A) to (D) show Figure 4 (B) AA section view, BB section view, CC section view and DD section view.

[0036] exist Figure 6 (A) and (B) show a side view and a front view representing the state of multiple stacked heat exchange components 11. Figure 7 (A) to (D) show Figure 6 (B) AA section view, BB section view, CC section view and DD section view.

[0037] like Figure 4 to Figure 7 As shown, in the heat medium flow path 14, the branch section 15 and the confluence section 16 are arranged side by side in the flow direction of the internal heat medium. In this embodiment, the branch section 15 includes a first branch section 15A and a second branch section 15B, and the confluence section 16 includes a first confluence section 16A and a second confluence section 16B.

[0038] The first flow dividing portion 15A includes a plurality of flow paths 15a that divide the internal heat medium flowing into the heat exchange member 11. The plurality of flow paths 15a are provided in a manner that protrude toward the outside in the thickness direction (Z direction in the drawing) of the heat exchange member 11 along the longitudinal direction (X direction in the drawing) of the heat exchange member 11. Between the adjacent flow paths 15a, there is a flat portion 15c. The plurality of flow paths 15a are arranged along the flow direction (Y direction in the drawing) of the external heat medium (air) flowing on the outer surface of the heat exchange member 11, and are alternately provided on one side and the other side in the thickness direction of the heat exchange member 11. That is, in the first flow dividing portion 15A, the flat portion 15c is located on the other side in the thickness direction of the heat exchange member 11 corresponding to the flow path 15a on one side in the thickness direction.

[0039] The second flow dividing portion 15B includes a plurality of flow paths 15b that divide the internal heat medium that has been divided at the first flow dividing portion 15A and converged at the converging portion 16. The plurality of flow paths 15b are provided in a manner that protrude toward the outside in the thickness direction (Z direction in the drawing) of the heat exchange member 11 along the longitudinal direction (X direction in the drawing) of the heat exchange member 11. Between the adjacent flow paths 15b, there is a flat portion 15c.

[0040] The plurality of flow paths 15b are arranged along the flow direction (Y direction in the drawing) of the external heat medium (air) flowing on the outer surface of the heat exchange member 11, and are alternately provided on one side and the other side in the thickness direction of the heat exchange member 11. That is, in the first flow dividing portion 15B, the flat portion 15c is located on the other side in the thickness direction of the heat exchange member 11 corresponding to the flow path 15b on one side in the thickness direction.

[0041] On one side in the thickness direction of the heat exchange member 11, the arrangement positions of the flow paths 15a of the first flow dividing portion 15A and the flow paths 15b of the second flow dividing portion 15B in the flow direction of the external heat medium are offset from each other. Similarly, on the other side in the thickness direction of the heat exchange member 11, the arrangement positions of the flow paths 15a of the first flow dividing portion 15A and the flow paths 15b of the second flow dividing portion 15B in the flow direction of the external heat medium are offset from each other.

[0042] That is, the arrangement positions of the flow paths 15a of the first flow dividing portion 15A provided on one side sandwiching the converging portion 16 and the arrangement positions of the flow paths 15b of the second flow dividing portion 15B provided on the other side are offset from each other in the flow direction of the internal heat medium. In other words, in the heat exchange member 11, the phases of the flow paths 15a and the phases of the flow paths 15b are arranged to be different in the Y direction in the drawing. Due to this, the straight-line travel of the internal heat medium in the flow direction (X direction in the drawing) is hindered, and the internal heat medium meanders in the Y direction in the drawing to the extent that the phases of the flow paths 15a and the phases of the flow paths 15b are offset, and flows in the X direction in the drawing.

[0043] In this embodiment, the confluence section 16 includes a first confluence section 16A and a second confluence section 16B. The first confluence section 16A communicates with the first branch section 15A and the second branch section 15B, and is provided throughout the width direction of the heat exchange member 11, that is, throughout the flow direction of the air (external heat medium) flowing on the outer surface of the heat exchange member 11, so that the internal heat medium flowing in from each flow path 15a of the first branch section 15A converges.

[0044] The first busbar 16A protrudes outward in the thickness direction (Z direction in the figure) of the heat exchange member 11 with two or more layers of difference. That is, the first busbar 16A has: a first protrusion 16a that protrudes outward from the heat exchange member 11; and a second protrusion 16b that protrudes further outward from the first protrusion 16a.

[0045] The outer surface of the first manifold 16A has alternating concave and convex surfaces with first protrusions 16a and second protrusions 16b of different heights in different protruding directions. When multiple heat exchange members 11 are stacked, by having the second protrusions 16b of adjacent heat exchange members 11 abut against each other, the heat exchange members 11 are arranged at equal intervals, and the deflection of each heat exchange member 11 can be suppressed. Therefore, the interval between the heat exchange members 11 can be kept constant. Furthermore, the number and arrangement position of the second protrusions 16b can be appropriately determined. Moreover, by arranging multiple second protrusions 16b at equal intervals, the deflection of the heat exchange members 11 can be suppressed more effectively.

[0046] The second confluence 16B is provided throughout the flow direction (Y direction in the figure) of the air (external heat medium) flowing on the outer surface of the heat exchange member 11, and merges the internal heat medium flowing in from each flow path 15b of the second branch section 15B. The second confluence 16B protrudes outward from the heat exchange member 11, for example, in such a way that its height in the protruding direction is approximately the same as that of the first protrusion 16a. Therefore, in the case of stacking multiple heat exchange members 11, the second confluences 16B of adjacent heat exchange members 11 do not contact each other.

[0047] As described above, each heat exchange member 11 is configured, for example, to overlap a first heat-conducting plate 41 and a second heat-conducting plate 42 formed by stamping or other processes on a plate-shaped member that has thermal conductivity, such as metal.

[0048] exist Figure 8 The side view, front view, and rear view of the first heat-conducting plate 41 are shown in (A) to (C). Figure 9 (A) to (D) show Figure 8 (B) AA section view, BB section view, CC section view and DD section view.

[0049] like Figure 8 and Figure 9 As shown, in the first heat-conducting plate 41, a forged portion corresponding to the first manifold 12, the second manifold 13, the first branch section 15A, the second branch section 15B, the first confluence section 16A and the second confluence section 16B are formed in such a way that they protrude from the reference surface (flat portion 15c) of the first heat-conducting plate.

[0050] More specifically, the first heat-conducting plate 41 is provided with: a forging part 45a forming the flow path 15a of the first flow branch 15A, a forging part 46a forming the first flow confluence 16A, a forging part 45b forming the flow path 15b of the second flow branch 15B, and a forging part 46b forming the second flow confluence 16B.

[0051] exist Figure 10 The side view, front view, and rear view of the second heat-conducting plate 42 are shown in (A) to (C). Figure 11 (A) to (D) show Figure 10 Sectional views AA, BB, CC and DD of (B).

[0052] like Figure 10 and Figure 11 As shown, in the second heat-conducting plate 42, a forged portion corresponding to the first manifold 12, the second manifold 13, the first branch section 15A, the second branch section 15B, the first confluence section 16A and the second confluence section 16B are formed in such a way that they protrude from the reference surface (flat portion 15c) of the second heat-conducting plate.

[0053] More specifically, the second heat-conducting plate 42 is respectively formed with a forging part 45a forming a flow path 15a of the first flow branch 15A, a forging part 45b forming a flow path 15b of the second flow branch 15B, a forging part 46a forming the first flow confluence 16A, and a forging part 46b forming the second flow confluence 16B.

[0054] When the first heat-conducting plate 41 and the second heat-conducting plate 42 overlap, the forged portion 45a of one of the first heat-conducting plate 41 and the flat portion 15c of the other form a flow path 15a, and the forged portion 45b of one of the first heat-conducting plate 41 and the flat portion 15c of the other form a flow path 15b. Furthermore, the forged portions 46a of the first heat-conducting plate 41 and the second heat-conducting plate 42 face each other to form a first confluence portion 16A. Similarly, the forged portions 46b of the first heat-conducting plate 41 and the second heat-conducting plate 42 also face each other to form a second confluence portion 16B.

[0055] Additionally, for example, such as Figure 12 and Figure 13As shown, with respect to the first manifold portion 16A, only one of the one side and the other side in the thickness direction of the heat exchange member 11 can be provided with the concave-convex surface in which the first convex portion 16a and the second convex portion 16b having different heights in the protruding direction are alternately provided.

[0056] With respect to the heat exchanger configured in the above-described manner, a plurality of parameters related to the dimensions of the heat exchange member 11 are set to analyze the heat exchange amount.

[0057] Specifically, as shown in the table of FIG. 10, as the parameters related to the dimensions of the heat exchange member 11, there are set a pitch Tp between the heat exchange members 11, a height (thickness) Th of the heat exchange member 11, a thickness (wall thickness) Tt of the first heat conductive plate and the second heat conductive plate configuring the heat exchange member 11, a pitch Cp between the centers of the flow paths 15a, a width Cw of the flow path 15a, a number Cn of the flow paths 15a, a plumb portion angle Fa of the flow path 15a, and a corner R( ) of the flow path 15a. Among these, the wall thickness Tt of the first heat conductive plate and the second heat conductive plate and the number Cn of the flow paths are set to be constant, and three values (setting value 1 to setting value 3) are set for each of the other parameters. Figure 14 Figure 15 ) of the flow path 15a. Among these, the wall thickness Tt of the first heat conductive plate and the second heat conductive plate and the number Cn of the flow paths are set to be constant, and three values (setting value 1 to setting value 3) are set for each of the other parameters.

[0058] Further, a distance between the base end portions of the adjacent flow paths 15a is set to L1, a width of the top surface of the flow path 15a is set to L2, and a distance between the top portions of the flow paths 15a of the adjacent heat exchange members 11 (the shortest distance between the adjacent heat exchange members 11) is set to L3.

[0059] In addition, with respect to L1, L2, and L3, mathematical expressions (1), (2), and (3) can be determined based on the above-described parameters.

[0060] [Mathematical Expression 1]

[0061] L1 = Cp - Cw … (1)

[0062] [Mathematical Expression 2]

[0063]

[0064] [Mathematical Expression 3]

[0065] L3 = T P - T h … (3)

[0066] Figure 16 A graph showing the analysis of the heat exchanger in which the heat exchange member 11 is stacked with the parameters and values set in the above-described manner and the result thereof is drawn. Figure 16 (A) of FIG. 11 shows the relationship between the ventilation resistance (Pa) and the heat exchange amount (W), Figure 16 ​(B) shows the relationship between the ventilation resistance (Pa) and the heat exchange amount per unit volume (kW / m 3 ).

[0067] Further, the relationship between L1 calculated based on the above parameters and the heat exchange amount derived from the analysis results according to Figure 17 is shown in Figure 16 . Specifically, the relationship between L1 (mm) and the heat exchange amount per unit volume (kW / m 3 ) is shown in (A) of Figure 17 , and the relationship between L1 (mm) and the heat exchange amount per unit ventilation resistance (W / Pa) is shown in (B) of Figure 17 .

[0068] In (A) of Figure 17 , the maximum and minimum values of the parameters other than L1 are shown by solid lines. Further, the gray band of the central portion shows the range of the heat exchange capacity per unit volume of the general existing heat exchanger.

[0069] As is apparent from (A) of Figure 17 , there is a tendency that the heat exchange amount per unit volume decreases as L1 increases. In order to secure the capacity equivalent to that of the existing heat exchanger, it is more desirable to set L1 ≤ 1.3 mm. Further, if L1 = 0, the flow path 15a of the first flow dividing portion 15A and the flow path 15b of the second flow dividing portion 15B of the heat exchange member 11 communicate, or the wall thickness between the flow paths is thinned, so that the pressure resistance performance cannot be secured. Therefore, from the viewpoint of the capacity per unit volume, it is more desirable that 0.1 mm ≤ L1 ≤ 1.3 mm. Further, by setting 0.1 mm ≤ L1 ≤ 0.75 mm, the capacity above that of the existing heat exchanger can be achieved.

[0070] In (B) of Figure 17 , the maximum and minimum values of the parameters other than L1 are shown by solid lines, and the average values are shown by dotted lines. The gray band shows the range of the heat exchange capacity per unit ventilation resistance of the general existing heat exchanger. As is apparent from (B) of Figure 17 , there is a tendency that the heat exchange amount per unit ventilation resistance increases as L1 increases. If the average values are focused on, in order to secure the capacity equivalent to or above that of the existing heat exchanger, it is more desirable to set at least 0.25 ≤ L1.

[0071] According to (A) of Figure 17 and (B) of Figure 17 , the range of L1 can be more desirably set to 0.1 mm ≤ L1 ≤ 1.3 mm, and more desirably to 0.25 mm ≤ L1 ≤ 0.75 mm.

[0072] Next, in Figure 18(A) shows the heat exchange rate per unit volume (kW / m³) for L3 (mm). 3 The relationship between ) in Figure 18 Figure (B) shows the relationship between L3 (mm) and the heat exchange rate per unit ventilation resistance (W / Pa).

[0073] exist Figure 18 In (A), the maximum and minimum values ​​of parameters other than L3 are shown by solid lines, and the average values ​​are shown by dashed lines. The gray band in the center shows the range of heat exchange capacity per unit volume for typical existing heat exchangers. From Figure 18 As shown in (A), there is a tendency for the heat exchange capacity per unit volume to increase as L3 decreases. To ensure the same capacity as existing heat exchangers, it is ideal to set L3 ≤ 0.8 mm. Furthermore, by setting L3 ≤ 0.52 mm, a capacity exceeding that of existing heat exchangers can be achieved.

[0074] exist Figure 18 In (B), the maximum and minimum values ​​of parameters other than L3 are shown by solid lines. The gray bands show the range of heat exchange capacity per unit ventilation resistance of a typical existing heat exchanger. Figure 18 As shown in (B), there is a tendency for the heat exchange capacity per unit ventilation resistance to decrease as L3 decreases. To ensure the same capacity as existing heat exchangers, L3 needs to be 0.18 mm ≤ L3. Furthermore, by setting L3 to 0.32 mm ≤ L3, a capacity exceeding that of existing heat exchangers can be achieved.

[0075] according to Figure 18 (A) and Figure 18 (B) can ideally set the range of L3 to 0.18mm≤L3≤0.8mm, and even more ideally to 0.32mm≤L3≤0.52mm.

[0076] The first heat-conducting plate 41 and the second heat-conducting plate 42 mentioned above can also be structures formed by applying a resin coating to an aluminum sheet, or structures formed by overlapping a thermoplastic resin with multiple resins of different properties.

[0077] On the other hand, in the case of heat exchangers using the above-described method, the thermal conductivity and wall thickness of the heat-conducting plate have a significant impact on the heat exchange capacity. For example... Figure 19 As shown, when the thermal conductivity in the thickness direction of the heat-conducting plate is set to λW / (m·K), the wall thickness is set to t (m), and the thermal conductivity (U value) in the thickness direction is set to λ / t, if the thermal conductivity (U value) is 300W / (m·K), 2 Below ·K), the thermal conductivity drops sharply. Therefore, ideally, the thermal conductivity (U-value) of the first and second heat-conducting plates should be 300 W / (m²). 2• K) the above.

[0078] According to the heat exchanger 1 configured in the above-described manner, the heat exchange member 11 is provided with the first header portion 12, the heat medium flow path 14, and the second header portion 13 that communicate with each other, and the internal heat medium that flows into the inside of the heat exchange member 11 flows from the first header 12 to the second header portion 13 via the heat medium flow path 14. At this time, the internal heat medium exchanges heat with the external heat medium that flows outside the heat exchange member 11. Since the flow direction of the internal heat medium and the flow direction of the external heat medium cross (in this embodiment, orthogonal), generally, the temperature of the external heat medium increases or decreases with respect to the flow direction of the external heat medium. That is, with respect to the flow direction of the external heat medium, there is unevenness in the temperature difference between the internal heat medium and the external heat medium.

[0079] In contrast to this, in this embodiment, the first confluence portion 16A or the second confluence portion 16B is provided between the first flow dividing portion 15A and the second flow dividing portion 15B. Therefore, the internal heat medium that flows in the flow path 15a or the flow path 15b on the upstream side of the external heat medium and the internal heat medium that flows in the flow path 15a or the flow path 15b on the downstream side of the external heat medium confluences and mixes at the first confluence portion 16A or the second confluence portion 16B, so that the temperature of the internal heat medium becomes uniform. Thereby, it is possible to suppress unevenness in the temperature of the external heat medium that exchanges heat with the internal heat medium, and it is possible to improve the heat exchange efficiency.

[0080] Further, the arrangement positions of the flow path 15a of the first flow dividing portion 15A and the arrangement positions of the flow path 15b of the second flow dividing portion 15B are offset from each other in the flow direction of the internal heat medium, so that it is possible to suppress the development of the flow on the downstream side of the internal heat medium and the development of the temperature boundary layer, and it is possible to improve the heat exchange efficiency between the external heat medium and the internal heat medium.

[0081] Further, since the first confluence portion 16A of the heat exchange member 11 includes the second protrusion 16b that further protrudes outward from the first protrusion 16a, and the second protrusions of the adjacent heat exchange members 11 abut each other, it is possible to suppress the deflection of the heat exchange member 11, and it is possible to maintain the interval of the plurality of heat exchange members 11 as a constant interval. Further, since the second protrusion that abuts the adjacent heat exchange member 11 is provided integrally with the first confluence portion that is the flow path of the internal heat medium, the flow path of the internal heat medium is not blocked.

[0082] Since it is not necessary to provide an emboss or a protrusion for contact with the adjacent heat exchange member 11 at the first flow dividing portion 15A and the second flow dividing portion 15B, by providing the flat portion 15c between the flow path 15a, 15b and the flow path at the first flow dividing portion 15A and the second flow dividing portion 15B, it is possible to provide sufficient unevenness on the outer surface of the heat medium flow path 14, that is, the flow path of the external heat medium.

[0083] Thus, in the heat exchange member 11, by impeding the straight travel of the external heat medium by the concavo-convex formed on the outer surface of the heat medium flow path 14, and changing the flow direction of the external heat medium while passing through the surface of the heat exchange member 11 along the concavo-convex of the surface of the heat medium flow path 14, the heat conduction of the internal heat medium and the external heat medium can be promoted.

[0084] The above-described embodiments of the present application are described in detail with reference to the drawings, but the specific structure is not limited to these embodiments, and even design changes and the like within the scope of the gist of the present application are included in the present application.

[0085] (Symbol explanation)

[0086] 1 Heat exchanger; 10 Core; 11 Heat exchange member; 12 First header portion; 13 Second header portion; 14 Heat medium flow path; 15 Flow dividing portion; 15A First flow dividing portion; 15B Second flow dividing portion; 15a, 15b Flow path; 15c Flat portion; 16 Flow converging portion; 16A First flow converging portion; 16B Second flow converging portion; 16a First convex portion; 16b Second convex portion; 20A First side plate; 20B Second side plate; 30A First pipe; 30B Second pipe; 41 First heat conducting plate; 42 Second heat conducting plate; 45a, 45b, 46a, 46b Die-forged portion.

Claims

1. A heat exchanger in which a plurality of heat exchange members are stacked, and in which an internal heat medium flowing in a heat medium flow path provided in the heat exchange members and an external heat medium flowing on an outer surface of the heat exchange members are heat-exchanged, characterized in that: the heat medium flow path includes a branch portion that branches the internal heat medium, and a first collecting portion that collects the internal heat medium branched by the branch portion, the branch portion has a plurality of branch flow paths that protrude to an outside of the heat exchange member and are arranged in a flow direction of the external heat medium, the first collecting portion has a first protruding portion that communicates with the plurality of branch flow paths and protrudes to the outside of the heat exchange member in the flow direction of the external heat medium, and a second protruding portion that further protrudes to the outside from the first protruding portion.

2. The heat exchanger according to claim 1, characterized in that: the plurality of heat exchange members are stacked in a manner that the second protruding portions of the adjacent heat exchange members abut each other.

3. The heat exchanger according to claim 1, characterized in that: the second protruding portion is provided in the first protruding portion in a plurality in the flow direction of the external heat medium.

4. The heat exchanger according to claim 2, characterized in that: the second protruding portion is provided in the first protruding portion in a plurality in the flow direction of the external heat medium.

5. The heat exchanger according to any one of claims 1 to 4, characterized in that: the branch flow paths are alternately arranged in the flow direction of the external heat medium on one side and the other side in a thickness direction of the heat exchange member.

6. The heat exchanger according to any one of claims 1 to 4, characterized in that: the branch portion and the first collecting portion are alternately arranged in the flow direction of the internal heat medium in the heat medium flow path.

7. The heat exchanger according to any one of claims 1 to 4, characterized in that: in two branch portions arranged on one side and the other side with the first collecting portion interposed therebetween, the arrangement positions of the branch flow paths on one side and the arrangement positions of the branch flow paths on the other side are staggered with each other in the flow direction of the internal heat medium along the flow direction of the external heat medium.

8. The heat exchanger according to any one of claims 1 to 4, characterized in that: the heat medium flow path further includes a second collecting portion that is arranged side by side with the branch portion and the first collecting portion in the flow direction of the internal heat medium, the second collecting portion communicates with the plurality of branch flow paths and protrudes to the outside of the heat exchange member in the flow direction of the external heat medium.

9. The heat exchanger according to claim 8, characterized in that: the first collecting portion and the second collecting portion are alternately arranged in the flow direction of the internal heat medium in a manner that the branch portion is interposed therebetween.

10. The heat exchanger according to claim 8, characterized in that: ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ The arrangement position of the shunt flow path on one side and the arrangement position of the shunt flow path on the other side are staggered in the flow direction of the external heat medium along the flow direction of the internal heat medium.

11. The heat exchanger according to claim 9, wherein The arrangement position of the shunt flow path on one side and the arrangement position of the shunt flow path on the other side are staggered in the flow direction of the external heat medium along the flow direction of the internal heat medium.

12. The heat exchanger according to any one of claims 1 to 4, wherein The heat exchange member is composed of two heat-conducting plates which are overlapped, and the two heat-conducting plates are formed by processing a plate-shaped member having heat conductivity to form, in the thickness direction from the reference surface of the plate-shaped member, a die-forged portion corresponding to the shunt portion, the first collecting portion, and a second collecting portion arranged side by side with the shunt portion and the first collecting portion.

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