Heat exchanger

Abstract

To improve heat exchange performance of a heat exchanger.SOLUTION: A plane part of a first plate 11 of a heat exchanger has: round projection parts 40 which contact with a second plate 12; and V-shaped projection parts 50 which protrude toward the second plate 12, are provided in a V shape in a longitudinal direction of a first passage 10A along a surface of the first plate 11, and face the second plate 12 while forming a gap therebetween. A plane part of the second plate 12 has round projection parts which contact with the round projection parts 40 at positions facing the round projection parts 40 of the first plate 11. The round projection parts 40 and the V-shaped projection parts 50 are disposed at multiple positions in the longitudinal direction of the first passage 10A. Each round projection part 40 is disposed, at the plane part of the first plate 11, on a virtual line A connecting a protruding part having a protruding shape in the longitudinal direction of the first passage 10A of the V-shaped projection part 50 with a protruding part having a protruding shape in the longitudinal direction of the first passage 10A of another V-shaped projection part 50 located adjacent to the V-shaped projection part 50 in the longitudinal direction of the first passage 10A.SELECTED DRAWING: Figure 3

Description

Technical Field

[0001] The present invention relates to a heat exchanger.

Background Art

[0002] Patent Document 1 discloses a heat exchanger in which a first heat transfer plate and a second heat transfer plate are alternately laminated, and a first flow path through which a first fluid flows and a second flow path through which a second fluid flows are alternately arranged between them, and inner fins are provided in these flow paths.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In the heat exchanger of Patent Document 1, the first flow path through which the first fluid flows and the second flow path through which the second fluid flows are configured to include inner fins having a large number of wavy protrusions in the space of the flow path. However, in order to appropriately circulate the first fluid and the second fluid while performing heat exchange, it may not always be appropriate to provide inner fins.

[0005] The present invention has been made in view of the above points, and an object thereof is to improve the heat exchange performance in both the flow path of the first fluid and the flow path of the second fluid in a heat exchanger in which the flow paths of the first fluid and the second fluid are alternately formed.

Means for Solving the Problems

[0006] According to an aspect of the present invention, a heat exchanger that performs heat exchange between a first fluid and a second fluid includes a plurality of first plates provided in parallel with a gap therebetween, and a second plate disposed with a gap between a pair of adjacent first plates and alternately laminated with the first plates to alternately form a first flow path through which the first fluid flows and a second flow path through which the second fluid flows. The first plate and the second plate each have a flat portion and a wall portion standing upright from the periphery of the flat portion. The flat portion of the first plate has a first protrusion protruding toward the second plate and contacting the second plate, and a first V-shaped protrusion protruding toward the second plate and provided in a V-shape along the longitudinal direction of the first flow path on the surface of the first plate and facing the second plate with a gap therebetween. The flat portion of the second plate has a second protrusion protruding toward the first plate and contacting the first protrusion at a position facing the first protrusion of the first plate. A plurality of the first protrusions and the first V-shaped protrusions are arranged in the longitudinal direction of the first flow path. The first protrusion is disposed on a virtual line connecting a convex portion that is convex in the longitudinal direction of the first flow path of the first V-shaped protrusion and a convex portion that is convex in the longitudinal direction of the first flow path of the first V-shaped protrusion adjacent to the first V-shaped protrusion in the longitudinal direction of the first flow path on the flat portion of the first plate.

Effects of the Invention

[0007] In the above aspect, since the first V-shaped protrusions are erected and arranged in the first flow path, when the first fluid flowing through the first flow path passes through them, a flow that becomes a longitudinal vortex in the stacking direction of the heat exchanger is generated, and the first fluid flows in the first flow path. Thereby, the heat exchange performance between the first fluid and the second fluid can be improved.

Brief Description of the Drawings

[0008]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Mode for Carrying Out the Invention

[0009] Hereinafter, with reference to the drawings, the heat exchanger 1 according to an embodiment of the present invention will be described.

[0010] First, with reference to FIGS. 1 and 2, the overall configuration of the heat exchanger 1 will be described. FIG. 1 is a front view of the heat exchanger 1 according to an embodiment of the present invention, and FIG. 2 is a plan view of the heat exchanger 1.

[0011] The heat exchanger 1 is provided, for example, in a refrigeration cycle mounted on a vehicle or the like, and performs heat exchange between cooling water as a first fluid and a gas-liquid two-phase refrigerant as a second fluid.

[0012] The heat exchanger 1 includes a core portion 10, a support plate 20 (see FIG. 2), and a bottom plate 30.

[0013] As shown in FIG. 1, the core portion 10 is configured by alternately laminating a plurality of first plates 11 and a plurality of second plates 12 arranged in parallel. On the upper surface of the core portion 10, there are provided a first fluid inlet 15 for allowing cooling water to flow into the core portion 10, a first fluid outlet 16 for allowing cooling water to flow out of the core portion 10, a second fluid inlet 25 for allowing the gas-liquid two-phase refrigerant to flow into the core portion 10, and a second fluid outlet 26 for allowing the gas-liquid two-phase refrigerant to flow out of the core portion 10. The structure of the core portion 10 will be described in detail later with reference to FIG. 3.

[0014] As shown in FIG. 2, the support plate 20 is attached to one end face (here, the upper surface) of the core portion 10. The support plate 20 is made of a member thicker than the first plate 11 and the second plate 12 constituting the core portion 10, supports the core portion 10 from above, and fixes the first fluid inlet 15, the first fluid outlet 16, the second fluid inlet 25, and the second fluid outlet 26.

[0015] The bottom plate 30 is attached to the other end face (here, the lower face) of the core part 10. The bottom plate 30 is composed of a member thicker than the first plate 11 and the second plate 12 that constitute the core part 10, and supports the core part 10 from the lower face. The bottom plate 30 is provided with a flange 31 for fixing the heat exchanger 1 to other members.

[0016] The first plate 11 and the second plate 12 are formed using flat plate members (plates) made of a metal with high thermal conductivity such as aluminum so that their outer peripheries have the same rectangular shape (rectangle). As shown in FIG. 2, the corners of the first plate 11 and the second plate 12 have a slightly rounded shape in order to guide the flow of cooling water and the gas-liquid two-phase refrigerant.

[0017] Pipes (not shown) through which cooling water flows are connected to the first fluid inlet 15 and the first fluid outlet 16. Pipes (not shown) through which the gas-liquid two-phase refrigerant flows are connected to the second fluid inlet 25 and the second fluid outlet 26. Since the volume of the gas-liquid two-layer refrigerant changes between the gas phase and the liquid phase, the pressure in the heat exchanger is higher compared to the cooling water. For this reason, the second fluid inlet 25 and the second fluid outlet 26 are provided with bolt holes for fixing with pipe bolts or the like.

[0018] Next, with reference to FIGS. 1, 2, and 3, the structure of the core part 10 will be described. FIG. 3 is a longitudinal sectional view of the heat exchanger 1 and corresponds to the III-III section in FIG. 2.

[0019] As shown in FIG. 3, the core part 10 is configured by alternately arranging a plurality of first plates 11 and second plates 12. In the core part 10, a pair of second plates 12 adjacent to the first plate 11 alternately form a first flow path 10A through which cooling water as the first fluid flows and a second flow path 10B through which the gas-liquid two-phase refrigerant as the second fluid flows. Inner fins 18 are provided in the second flow path 10B.

[0020] Cooling water flowing into each of the plurality of first flow paths 10A from the first fluid inlet 15 branches and flows into the inside of the support plate 20 after changing its flow direction. The cooling water that has passed through the plurality of first flow paths 10A merges and flows out of the heat exchanger 1 from the first fluid outlet 16.

[0021] As shown in FIG. 3, in each of the plurality of second flow paths 10B, a gas-liquid two-phase refrigerant flowing into the second fluid inlet 25 branches and flows into the inside of the support plate 20 after changing its flow direction. The gas-liquid two-phase refrigerant that has passed through the plurality of second flow paths 10B merges and flows out of the heat exchanger 1 from the second fluid outlet 26. As shown in FIG. 3, the first flow path 10A is joined to the first plate 11 and the second plate 12 at the ends of the communication paths so as to be closed with respect to the second flow path 10B. Although not shown, the second flow path 10B is joined to the first plate 11 and the second plate 12 at the ends of the communication paths so as to be closed with respect to the first flow path 10A.

[0022] The inner fin 18 is provided in the second flow path 10B and abuts against the first plate 11 and the second plate 12. The inner fin 18 is a fin for increasing the heat transfer area of the first plate 11 and the second plate 12 and promoting heat exchange of the gas-liquid two-phase refrigerant flowing through the second flow path 10B. Further, the inner fin 18 also serves to support the second flow path 10B in the stacking direction so that the first plate 11 and the second plate 12 are not deformed by the pressure of the gas-liquid two-phase refrigerant.

[0023] The surfaces of the first plate 11 and the second plate 12 that are in contact with the inner fin 18 are formed flat. On the other hand, the surfaces of the first plate 11 and the second plate 12 on the side of the first flow path 10A are formed such that a plurality of round protrusions 40 and V-shaped protrusions 50 project as described below.

[0024] Figures 4, 5, and 6 are explanatory diagrams of the first plate 11 and the second plate 12. Figure 4 is an exploded perspective view of a pair of the first plate 11 and the second plate 12. Figure 5 is a top view of the first plate 11 and the second plate 12. Figure 6 is an enlarged view of the R portion of Figure 5.

[0025] The first plate 11 and the second plate 12 are rectangular in shape with rounded corners, and inlets and outlets for cooling water and a gas-liquid two-phase refrigerant are arranged at the four corners thereof. The cooling water and the gas-liquid two-phase refrigerant are configured to flow along the longitudinal direction of the first flow path 10A and the second flow path 10B on the surfaces of the first plate 11 and the second plate 12.

[0026] The first plate 11 has a flat portion 110 and a wall portion 111 that stands upright so as to surround the periphery of the flat portion 110. The wall portion 111 has a tapered shape that widens outward as it goes upward. Thus, the first plate 11 is in the shape of a washbasin or a dish as a whole.

[0027] In the flat portion 110 of the first plate 11, a first fluid inlet side communication path 151, a first fluid outlet side communication path 161, a second fluid inlet side communication path 251, and a second fluid outlet side communication path 261 are respectively formed to penetrate therethrough. In the first plate 11, the first fluid inlet side communication path 151 and the second fluid outlet side communication path 261 are arranged.

[0028] The first flow path 10A formed between the flat portion 110 of the first plate 11 and the opposing second plate 12 has a round protrusion (first protrusion) 40 and a V-shaped protrusion (first V-shaped protrusion) 50 that project toward the flat portion 110 of the second plate 12.

[0029] The V-shaped protrusion 50 is configured such that a V-shaped shape is repeatedly formed in the width direction from one long side along the longitudinal direction of the first flow path 10A in the first plate 11 to the other long side opposing the long side. A plurality of V-shaped protrusions 50 are arranged along the longitudinal direction of the first flow path 10A. In the example shown in Figure 4, nine V-shaped protrusions 50 are arranged.

[0030] As shown in FIG. 5, the V-shaped protrusion 50 is composed of a convex portion 51 of a convex shape formed in a V-shape in a plan view in the longitudinal direction of the first flow path 10A, a concave portion 52 of a concave shape formed in a V-shape in a plan view in the longitudinal direction of the first flow path 10A, and a connecting portion 53 that connects the convex portion 51 and the concave portion 52. The convex portion 51, the concave portion 52, and the connecting portion 53 are repeatedly formed in the width direction. In the example shown in FIG. 5, the V-shaped protrusion 50 has six convex portions 51 and five concave portions 52. Thus, the V-shaped protrusion 50 has a wavy shape composed of a plurality of convex portions 51 and a plurality of concave portions 52.

[0031] In this way, by arranging the V-shaped protrusion 50 upright in the first flow path 10A, when the cooling water flowing through the first flow path 10A passes through the V-shaped protrusion 50, a flow that becomes a longitudinal vortex in the stacking direction of the heat exchanger 1 is generated. Due to such a flow, the cooling water flows in the first flow path 10A, and the heat exchange between the cooling water and the gas-liquid two-phase refrigerant is promoted.

[0032] Note that the V-shaped protrusion 54 is also arranged between the first fluid inlet side communication path 151 and the second fluid outlet side communication path 261, and between the first fluid outlet side communication path 161 and the second fluid inlet side communication path 251. Different from the V-shaped protrusion 50, the end portion of the V-shaped protrusion 54 does not contact the end portion in the width direction of the first plate 11 or the communication path. The V-shaped protrusion 54 is configured in a shape having one concave portion 52 and two convex portions 51. Round protrusions 40 are arranged near the two concave portions 52. With this configuration, by providing the V-shaped protrusion 54 near the end portion of the first plate 11 where the flow of the cooling water is likely to stagnate, the stagnation of the cooling water can be suppressed. Furthermore, by arranging the round protrusions 40 near the communication path penetrating the four corners of the first plate 11, deformation of the first plate 11 and the second plate 12 in this vicinity is suppressed.

[0033] Near the concave portion 52 of the V-shaped protrusion 50, a round protrusion 40 is formed. As shown in FIG. 5, five round protrusions 40 are arranged near the concave portion 52 of one V-shaped protrusion 50. The center of the round protrusion 40 is arranged on a line (virtual line A) connecting the convex portion 51 of the V-shaped protrusion 50 of the first plate 11 and the convex portion 51 of the V-shaped protrusion 55 of the second plate 12.

[0034] The round protrusion 40 is also arranged around each of the first fluid inlet side communication passage 151, the first fluid outlet side communication passage 161, the second fluid inlet side communication passage 251, and the second fluid outlet side communication passage 261. On the opposing second plate 12, a round protrusion (second protrusion) 45 is formed at the same position as the round protrusion 40 of the first plate 11. The round protrusion 40 of the first plate 11 and the round protrusion 45 of the second plate 12 are in contact with each other at their tops. By the round protrusion 40 and the round protrusion 45 being in contact with each other at their tops, in the first flow path 10A, between the first plate 11 and the second plate 12, they are erected and arranged in a columnar shape.

[0035] The round protrusion 40 is arranged on the virtual line A of the first plate 11, between the convex portion 51 of the V-shaped protrusion 50 of the first plate 11 and the convex portion 51 of the V-shaped protrusion 55 of the second plate 12, at a location where the distance between them is large. Specifically, as shown in FIG. 6, on the virtual line A, the distance between the convex portion 51 of the V-shaped protrusion 50 and the convex portion 51 of the adjacent V-shaped protrusion 55 is S1, and when the distance between the convex portion 51 of this V-shaped protrusion 55 and the convex portion 51 of another adjacent V-shaped protrusion 55 is S2 which is larger than S1, the round protrusion 40 is arranged between the convex portion 51 of the V-shaped protrusion 55 with a large distance and the convex portion 51 of the V-shaped protrusion 55.

[0036] In this way, when a plurality of V-shaped protrusions 50 or V-shaped protrusions 55 are arranged in the longitudinal direction of the first flow path 10A, by arranging the round protrusion 40 at a location where the distance between the convex portions 51 and the convex portions 51 is large on the virtual line A, the operation of forming the first plate 11 by pressing or the like becomes easy. The same applies to the round protrusion 45 arranged on the second plate 12 facing the first plate 11.

[0037] In this way, on the first plate 11, the round protrusions 40 are arranged at positions such that they form a lattice pattern over the entire flat surface portion 110. By arranging the round protrusions 40 upright in this manner, when the first plate 11 and the second plate 12 are stacked and assembled, the channel height of the first flow channel 10A at the positions where dimensional management is required can be maintained at a specified height. Further, by interposing the round protrusions 40 and the round protrusions 45 between the first plate 11 and the second plate 12, it is possible to prevent them from deforming due to the pressure of the cooling water or the gas-liquid two-phase refrigerant.

[0038] Note that, since the round protrusions 40 are arranged upright in a columnar shape, a flow in which the cooling water flowing through the first flow channel 10A becomes a lateral vortex in the plane direction of the flat surface portion 110 near the round protrusions 40 is generated. As a result, in the vicinity of the round protrusions 40, particularly on the downstream side of the round protrusions 40, the cooling water may stagnate and the heat exchange efficiency may decrease. On the other hand, the round protrusions 40 are arranged near the concave portion 52 of the V-shaped protrusions 50. More specifically, the round protrusions 40 are arranged on a virtual line A connecting the convex portion 51 of the V-shaped protrusions 50 adjacent in the longitudinal direction of the first flow channel 10A and the concave portion 52 of the V-shaped protrusions 55. In the first flow channel 10A, the cooling water passes over the connecting portions 53 having different directions at the V-shaped protrusions 50 and the V-shaped protrusions 55, so that longitudinal vortices in different directions act on the round protrusions 40. As a result, the stagnation of the cooling water near the round protrusions 40 is suppressed, and heat exchange is promoted.

[0039] As a result, a uniform flow of the cooling water is generated over the entire surface of the first flow channel 10A, and it becomes difficult for the cooling water to stagnate. Therefore, the heat exchange efficiency between the cooling water in the first flow channel 10A and the gas-liquid two-phase refrigerant and the gas-liquid two-phase refrigerant 10B is improved.

[0040] The flat surface portion 120 of the second plate 12 facing the first plate 11 also has a basin shape or a dish shape having a flat surface portion 120 and a wall portion 121 erected so as to surround the periphery of the flat surface portion 120, similar to the first plate 11.

[0041] On the flat portion 120 of the second plate 12, a first fluid inlet side communication passage 151, a first fluid outlet side communication passage 161, a second fluid inlet side communication passage 251, and a second fluid outlet side communication passage 261 are respectively formed to penetrate therethrough, and have a round protrusion 45 and a V-shaped protrusion (second V-shaped protrusion, indicated by a dotted line) 55 protruding toward the flat portion 110 of the opposing first plate 11. Similar to the V-shaped protrusion 50, the V-shaped protrusion 55 is composed of a convex portion 51 of a convex-shaped portion formed in a V-shape in plan view in the longitudinal direction of the first flow path 10A, a concave portion 52 of a concave-shaped portion formed in a V-shape in plan view in the longitudinal direction of the first flow path 10A, and a connecting portion 53 connecting the convex portion 51 and the concave portion 52, and the convex portion 51, the concave portion 52, and the connecting portion 53 are repeatedly formed in the width direction. And, in the V-shaped protrusion 55, the convex portion 51 and the concave portion 52 are arranged in the opposite direction to the V-shaped protrusion 50.

[0042] As shown in FIG. 5, the V-shaped protrusion 50 of the first plate 11 and the V-shaped protrusion 55 of the second plate 12 are arranged at positions that do not intersect with each other in plan view. More specifically, the concave portion 52 of the V-shaped protrusion 55 of the second plate 12 is arranged to face the convex portion 51 of the V-shaped protrusion 50 of the first plate 11. The concave portion 52 of the V-shaped protrusion 50 of the first plate 11 and the convex portion 51 of the V-shaped protrusion 55 of the second plate 12 are separated in the longitudinal direction of the first flow path 10A, and a round protrusion 40 is arranged therebetween.

[0043] In this way, by arranging the V-shaped protrusion 50 of the first plate 11 and the V-shaped protrusion 55 of the second plate 12 so as not to intersect with each other in plan view, the height in the stacking direction of the first flow path 10A becomes unnecessarily narrow due to the V-shaped protrusions 50 and 55 protruding from each other, and it is possible to suppress the stagnation of the flow of the cooling water. In the core portion 10, the first plate 11 and the second plate 12 are configured to be in contact with each other in the stacking direction at the wall portions 111 and 121. These are fixed, for example, by brazing.

[0044] In addition, in the above-described embodiment, the flat portion 120 of the second plate 12 facing the first plate 11 may be configured without the V-shaped protrusion 55. That is, in the first flow path 10A, the V-shaped protrusion 50 may be provided only on the flat portion 110 of the first plate 11, and the flow of the cooling water may be configured to be caused by this V-shaped protrusion 50.

[0045] According to the above embodiment, the following effects are obtained.

[0046] This embodiment is configured as a heat exchanger 1 that performs heat exchange between cooling water and a gas-liquid two-phase refrigerant. This heat exchanger 1 includes a plurality of first plates 11 provided in parallel with a gap therebetween, and a first flow path 10A in which cooling water flows and a second flow path 10B in which a gas-liquid two-phase refrigerant flows are alternately formed by being alternately stacked with the first plates 11 with a gap therebetween and disposed between a pair of adjacent first plates 11. The first plate 11 and the second plate 12 each have flat portions 110, 120 and wall portions 111, 121 standing upright from the peripheries of the flat portions 110, 120. The flat portion 110 of the first plate 11 protrudes toward the second plate 12 and has a round protrusion (first protrusion) 40 that contacts the second plate 12, and a V-shaped protrusion (first V-shaped protrusion) 50 that protrudes toward the second plate 12 and is provided in a V shape along the longitudinal direction of the first flow path 10A on the surface of the first plate 11 and faces the second plate 12 with a gap therebetween. The flat portion 120 of the second plate 12 has a round protrusion (second protrusion) 45 that protrudes toward the first plate 11 and contacts the round protrusion 40 at a position facing the round protrusion 40 of the first plate 11. The round protrusion 40 and the V-shaped protrusion 50 are arranged in a plurality in the longitudinal direction of the first flow path 10A. The round protrusion 40 is disposed on an imaginary line A that connects a convex portion 51 that is convex in the longitudinal direction of the first flow path 10A of the V-shaped protrusion 50 and a convex portion 51 that is convex in the longitudinal direction of the first flow path 10A of the V-shaped protrusion 50 adjacent to the V-shaped protrusion 50 in the longitudinal direction of the first flow path 10A on the flat portion 110 of the first plate 11.

[0047] In this configuration, the V-shaped protrusions 50 are erected and arranged in the first flow path 10A. When the cooling water flowing through the first flow path 10A passes through, a flow that forms longitudinal vortices in the stacking direction of the heat exchanger 1 is generated, and the cooling water flows in the first flow path 10A, promoting heat exchange between the cooling water and the gas-liquid two-phase refrigerant. Further, by interposing the round protrusions 40 and the round protrusions 45 between the first plate 11 and the second plate 12, they are prevented from being deformed by the pressure of the cooling water or the gas-liquid two-phase refrigerant. Further, by arranging the round protrusions 40 on the virtual line connecting the convex portions 51 of the adjacent V-shaped protrusions 50, the retention of the cooling water in the vicinity of the round protrusions 40 is suppressed.

[0048] Also, in the present embodiment, the flat portion 120 of the second plate 12 protrudes toward the first plate 11 and is provided in a V-shape in the longitudinal direction of the first flow path 10A and in the direction opposite to the V-shaped protrusions 50, and has V-shaped protrusions (second V-shaped protrusions) 55 that face the first plate 11 with a gap therebetween. A plurality of V-shaped protrusions 55 are arranged in the longitudinal direction of the first flow path 10A, and the round protrusions (second protrusions) 45 are arranged between the concave portions 52 that are concave in the longitudinal direction of the first flow path 10A of the adjacent V-shaped protrusions 55 on the flat portion 120 of the second plate 12.

[0049] In this configuration, the V-shaped protrusions 55 are arranged on the second plate 12 of the first flow path 10A, and the round protrusions 45 are arranged near the concave portions 52 of the V-shaped protrusions 55. In the first flow path 10A, the cooling water passes over the V-shaped protrusions 50 and the V-shaped protrusions 55 with different directions, so that longitudinal vortices with different directions act on the round protrusions 40 and the round protrusions 45. As a result, the retention of the cooling water in the vicinity of the round protrusions 40 and the round protrusions 45 is suppressed, and heat exchange is promoted.

[0050] Also, in the present embodiment, the first plate 11 and the second plate 12 are rectangular, the V-shaped protrusions 50 and the V-shaped protrusions 55 have a plurality of convex portions 51, and are formed from one of the wall portions 111, 121 intersecting the longitudinal direction of the first flow path 10A to the other wall portions 111, 121.

[0051] In this configuration, since the V-shaped protrusions 50 and 55 are arranged across the width direction of the first plate 11 and the second plate 12, the strength of the first plate 11 and the second plate 12 can be increased, and deformation thereof due to the pressure of the cooling water and the gas-liquid two-phase refrigerant is suppressed. Further, compared with a configuration in which the V-shaped protrusions are not continuous in the width direction, heat exchange between the cooling water and the gas-liquid two-phase refrigerant is more promoted.

[0052] Also, in the present embodiment, the round protrusion 40 is disposed on the virtual line A between the convex portion 51 of the V-shaped protrusion 50 and the convex portion 51 of the V-shaped protrusion 55 adjacent in the longitudinal direction of the first flow path 10A, at a location where the distance therebetween is large.

[0053] In this configuration, when a plurality of the V-shaped protrusions 50 or 55 are arranged in the longitudinal direction of the first flow path 10A, the round protrusion 40 is arranged at a location where the distance between the convex portions 51 is large, so that the operation of forming the first plate 11 by pressing or the like becomes easy. Further, since the flat portion 120 around the round protrusion 40 has a space, retention of the cooling water near the round protrusion 40 is suppressed, and heat exchange is promoted.

[0054] Also, in the present embodiment, the convex portion 51 of the V-shaped protrusion 50 in the flat portion 110 of the first plate 11 and the convex portion 51 of the V-shaped protrusion 55 in the flat portion 120 of the second plate 12 overlap in a plan view.

[0055] In this configuration, the V-shaped protrusion 50 and the V-shaped protrusion 55 overlap with each other by the concave portion 52 and the convex portion 51, and are arranged so as not to overlap at other locations, particularly at the connecting portion 53. Therefore, compared with a structure in which the connecting portions 53 overlap in the stacking direction, a decrease in the flow path cross-sectional area is suppressed, and retention of the cooling water in the first flow path 10A is suppressed.

[0056] Also, in the present embodiment, an inner fin 18 is provided between the first plate 11 and the second plate 12 in the second flow path 10B, the first fluid is the cooling water, and the second fluid is the gas-liquid two-phase refrigerant.

[0057] In this configuration, since the inner fin 18 is provided in the second flow path 10B through which the gas-liquid two-phase refrigerant flows, where the pressure increases due to the mixing of the gas phase and the liquid phase, the deformation of the second flow path 10B due to pressure is further suppressed.

[0058] Also, in the present embodiment, a support plate 20 having a greater thickness than the first plate 11 and the second plate 12 is fixed to the upper portions of the first plate 11 and the second plate 12. The support plate 20 is provided with a first fluid inlet 15 and a first fluid outlet 16 that communicate with the first flow path 10A, and a second fluid inlet 25 and a second fluid outlet 26 that communicate with the second flow path 10B.

[0059] In this configuration, since the support plate 20 with a large thickness difference is fixed to the upper portion of the core portion 10 formed by laminating the first plate 11 and the second plate 12, and the fluid inlets and outlets are fixed to the support plate 20, it is possible to suppress the deformation due to the pressure of the gas-liquid two-phase refrigerant while reducing the number of components.

[0060] As described above, the embodiments of the present invention have been explained. However, the above embodiments merely show a part of the application examples of the present invention, and are not intended to limit the technical scope of the present invention to the specific configurations of the above embodiments.

[0061] In the above embodiment, the first fluid is cooling water and the second fluid is a gas-liquid two-phase refrigerant. However, the first fluid and the second fluid are not limited to these. Any fluid can be applied as long as it performs heat exchange between the first fluid and the second fluid having different temperatures.

[0062] Also, in the present embodiment, the V-shaped protrusion 50 is provided on both the first plate 11 and the second plate 12. However, the V-shaped protrusion 50 may be provided on at least one of the first plate 11 and the second plate 12.

[0063] In addition, in this embodiment, as shown in FIG. 5, the round protrusions 40 are configured to be formed as protrusions of the same type at the same positions on the first plate 11 and the second plate 12. However, they may be formed as protrusions standing upright from at least one of the plates to the same height as the channel height.

Explanation of Reference Numerals

[0064] 1 Heat exchanger 10A First flow channel 10B Second flow channel 11 First plate 12 Second plate 15 First fluid inlet 16 First fluid outlet 20 Support plate 25 Second fluid inlet 26 Second fluid outlet 40, 45 Round protrusions 50, 54, 56 V-shaped protrusions 51 Crest 52 Trough 53 Connecting part 110, 120 Flat parts 111, 121 Wall parts

Claims

1. A heat exchanger that performs heat exchange between a first fluid and a second fluid, a plurality of first plates provided in parallel with a gap therebetween, a second plate disposed with a gap between a pair of adjacent first plates, alternately laminated with the first plates to alternately form a first flow path through which the first fluid flows and a second flow path through which the second fluid flows, comprising: the first plate and the second plate each have a flat portion and a wall portion standing upright from the periphery of the flat portion, the flat portion of the first plate has a first protrusion protruding toward the second plate and contacting the second plate, has a first V-shaped protrusion protruding toward the second plate, provided in a V-shape along the longitudinal direction of the first flow path on the surface of the first plate, and facing the second plate with a gap therebetween, the flat portion of the second plate has a second protrusion protruding toward the first plate and contacting the first protrusion at a position facing the first protrusion of the first plate, a plurality of the first protrusions and the first V-shaped protrusions are arranged in the longitudinal direction of the first flow path, the first protrusion is arranged on a virtual line connecting a convex portion that is convex in the longitudinal direction of the first flow path of the first V-shaped protrusion and a convex portion that is convex in the longitudinal direction of the first flow path of the first V-shaped protrusion adjacent to the first V-shaped protrusion in the longitudinal direction of the first flow path on the flat portion of the first plate, a heat exchanger.

2. The heat exchanger according to claim 1, wherein the flat portion of the second plate has a second V-shaped protrusion protruding toward the first plate, provided in a V-shape in the longitudinal direction of the first flow path and in a direction opposite to the first V-shaped protrusion, and facing the first plate with a gap therebetween, a plurality of the second V-shaped protrusions are arranged in the longitudinal direction of the first flow path, a concave portion that is concave in the longitudinal direction of the first flow path of the second protrusion and the second V-shaped protrusion is arranged on the virtual line, a heat exchanger.

3. The heat exchanger according to claim 2, wherein the first protrusion is arranged on the virtual line between the convex portion of the first V-shaped protrusion and the convex portion of the second V-shaped protrusion adjacent to the first V-shaped protrusion in the longitudinal direction of the first flow path, at a location where the distance therebetween is large, a heat exchanger.

4. The heat exchanger according to claim 2, The first plate and the second plate are rectangular, and the first V-shaped protrusion and the second V-shaped protrusion each have a plurality of the convex portions, and are formed from one wall portion provided along the longitudinal direction of the first flow path to the other wall portion facing the wall portion. Heat exchanger. **Claim 5** The heat exchanger according to claim 4, wherein the convex portions of the first V-shaped protrusion in the flat portion of the first plate and the convex portions of the second V-shaped protrusion in the flat portion of the second plate overlap in a plan view. Heat exchanger. **Claim 6** The heat exchanger according to claim 1 or 2, wherein an inner fin is provided between the first plate and the second plate in the second flow path, wherein the first fluid is cooling water and the second fluid is a gas-liquid two-phase refrigerant. Heat exchanger. **Claim 7** The heat exchanger according to claim 1 or 2, wherein a support plate having a greater thickness than the first plate and the second plate is fixed to the upper portions of the first plate and the second plate, and the support plate is provided with a first fluid inlet and a first fluid outlet communicating with the first flow path, and a second fluid inlet and a second fluid outlet communicating with the second flow path. Heat exchanger.

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