JP2020088357A - Heat exchanger - Google Patents

Abstract

To provide a heat exchanger capable of bringing the current velocity of heat transfer medium, flowing through a duct formed by multiple open holes, close to uniform current velocity in the lamination direction of the laminate, in a configuration including a laminate formed by laminating multiple layers in which multiple open holes are formed.SOLUTION: A heat exchanger 20 includes a case 22 provided with an inlet and an outlet, a lamination core 30 received in the case 22, where multiple layers in which multiple open holes are formed are laminated, and a duct 28 for introducing cooling medium L in a direction from the inlet toward the outlet is formed by the open holes, and a lid 26 and a bottom 24B sandwiching the lamination core 30 from the lamination direction so as to close the multiple open holes formed in the outermost layer. The duct 28 is formed of a first outer layer passage part 56 and a second outer layer passage part 58 formed of the lid, the bottom and the open holes in the outermost layer, and a general passage part 60 formed of the open holes of the intermediate layers, and the lamination core 30 is configured so that the flow passage area of the first outer layer passage part 56 becomes smaller than that of the general passage part 60.SELECTED DRAWING: Figure 7

Description

The present invention relates to heat exchangers.

Patent Document 1 discloses a heat sink in which a laminated core is housed in a case in which a refrigerant flows. The laminated core has a plurality of through-holes extending linearly along the first direction and having a plurality of vertical ribs provided at intervals in a direction orthogonal to the first direction and at intervals in the first direction. A plurality of punched plates provided with lateral ribs that connect the vertical ribs adjacent to each other in the orthogonal direction are formed, and the vertical ribs are overlapped with each other while the horizontal ribs are spaced in the first direction. It is formed by stacking so as to be spaced apart.

Japanese Patent No. 6026808

In Patent Document 1, a flow path through which cooling water flows is formed by a through hole located between adjacent vertical ribs in a direction orthogonal to the first direction of each punched plate. The cooling water flowing through this flow path is agitated in the stacking direction by repeatedly dividing and merging in the stacking direction by a plurality of horizontal ribs formed on each punched plate. Here, in Patent Document 1, since the punched plates having the same plate thickness are laminated to form the laminated core, between the through holes of the outermost punched plate and the case wall surface in the laminating direction in the flow path. The flow passage area in the formed outer layer flow passage portion is the same as the flow passage area of the general flow passage portion formed by the through holes of the adjacent punched plates excluding the outermost punched plate. However, the flow rate of the cooling water flowing from the general flow channel portion to the outer layer flow channel portion branching outward in the stacking direction is smaller than the flow rate of the cooling water flowing in the general flow channel portion. Therefore, there is a problem that the flow velocity of the cooling water becomes slower in the outer layer flow passage than in the general flow passage.

In view of the above facts, the present invention provides a heat medium that flows in a flow path formed by a plurality of through holes in a configuration including a laminated body formed by laminating a plurality of layers in which a plurality of through holes are formed. It is an object of the present invention to provide a heat exchanger capable of making the flow velocity of (1) uniform in the stacking direction of the stack.

The heat exchanger according to the first aspect of the present invention includes a case having an inlet through which a heat medium flows in and an outlet through which the heat medium flows out, and a plurality of layers housed in the case and having a plurality of through holes formed therein. Of the plurality of layers constituting the laminated body and the laminated body in which a flow path for guiding the heat medium in the direction from the inlet to the outlet is formed by the through hole, A pair of wall portions sandwiching the stacked body from the stacking direction so as to close the plurality of through holes formed in an outer layer, and the flow path includes the wall portion and the through hole of the outermost layer. The outer layer flow path portion formed by, and the general flow path portion formed by the through holes of the intermediate layers located on the inner side in the stacking direction with respect to the outermost layer, the laminated body, The flow passage area of the outer layer flow passage portion on one side in the stacking direction is configured to be smaller than the flow passage area of the general flow passage portion.

In the heat exchanger of the first aspect, the heat medium flows into the case from the inlet, passes through the flow path formed in the stack housed in the case, and flows out of the case from the outlet. At this time, heat exchange is performed via the case between the heat exchange target arranged in contact with the case and the heat medium flowing in the case.

In the heat exchanger, in the general flow path portion forming the flow path and the outer layer flow path portion on one side in the stacking direction, heat flowing into the outer layer flow path portion on one side branching out from the general flow path portion to the outer side in the stacking direction. The flow rate of the medium is lower than the flow rate of the heat medium flowing into the general flow path section. Therefore, the flow passage area of the outer layer flow passage portion on one side is made smaller than the flow passage area of the general flow passage portion. With such a configuration, the flow velocity of the heat medium flowing through the outer layer flow passage on one side becomes faster, and the flow velocity of the heat medium flowing through the outer layer flow passage on the one side becomes faster than the flow velocity of the heat medium flowing through the general flow passage. Approach. That is, the flow velocity of the heat medium approaches uniform in the stacking direction of the stack. In the heat exchanger having such a configuration, the heat exchange target and the heat medium are efficiently exchanged by bringing the heat exchange target into contact with one side of the case near the outer layer flow passage.

A heat exchanger according to a second aspect of the present invention is the heat exchanger according to the first aspect, wherein the laminate has a width in the direction orthogonal to the laminating direction of the outer layer flow passage portion on the one side in the general flow passage portion. And the height of the outer layer flow passage on the one side in the stacking direction is lower than the height of the general flow passage.

In the heat exchanger of the second aspect, the width of the outer layer flow path portion on one side in the stacking direction is the same as the width of the general flow path portion, and the height of the outer layer flow path portion on one side is greater than the height of the general flow path portion. Is also low. Thereby, for example, as compared with the configuration in which the width of the outer layer channel portion on one side and the width of the general channel portion are different, the heat medium smoothly flows from the general channel portion to the outer layer channel portion on the one side, The pressure loss of the heat medium can be suppressed.

A heat exchanger according to a third aspect of the present invention is the heat exchanger according to the first aspect or the second aspect, wherein the pair of the wall portions are opposite walls of the case.

In the heat exchanger of the third aspect, since the pair of wall portions sandwiching the stack in the stacking direction are the opposing walls of the case, the number of parts of the heat exchanger can be reduced.

A heat exchanger according to a fourth aspect of the present invention is the heat exchanger according to the first aspect or the second aspect, wherein the wall portion is a plate material, and the laminated body is sandwiched by a pair of the plate materials. It is contained in a case.

In the heat exchanger of the fourth aspect, the stacked body is housed in the case in a state of being sandwiched by the pair of plate members which are the pair of wall portions. By sandwiching the laminated body with a pair of plate materials as one component in this manner, it is easy to prevent foreign matter from entering the plurality of through holes of the laminated body during storage during manufacturing.

A heat exchanger according to a fifth aspect of the present invention is the heat exchanger according to any one of the first aspect to the fourth aspect, wherein the laminate has one of the one side on a side close to a heat exchange target in contact with the case. The outer layer channel portion is housed in the case so as to be positioned, and the channel area of the outer layer channel portion on the other side in the stacking direction located on the side far from the heat exchange target of the laminate is It is the same as the flow passage area of the general flow passage portion.

In the heat exchanger of the fifth aspect, the heat exchange target comes into contact with the side closer to the outer layer flow passage on one side of the case, so that the heat exchange between the heat exchange target and the heat medium is efficiently performed. On the other hand, in the outer layer flow path portion on the other side in the stacking direction, which is located farther from the heat exchange target of the laminate, even if the flow velocity of the heat medium is slower than that of the general flow path portion, it has little effect on the heat exchange performance. .. For this reason, the manufacturing cost can be reduced by making the outermost flow path area and the general flow path area of the other side flow path area on the other side the same, and by sharing the outermost layer and the intermediate layer on the other side in the stacking direction. The rise can be suppressed.

A heat exchanger according to a sixth aspect of the present invention is the heat exchanger according to any one of the first aspect to the fifth aspect, in which the layer is formed of a plate material in which the plurality of through holes are formed, In the laminated body, the thickness of the plate material forming the outermost layer on one side in the stacking direction is smaller than the thickness of the plate material forming the intermediate layer.

In the heat exchanger of the sixth aspect, in the laminated body, the thickness of the plate material forming the outermost layer on one side is made thinner than the thickness of the plate material forming the intermediate layer, and the outer layer flow passage on one side is formed. The flow passage area of the general flow passage portion can be made smaller than that of the general flow passage portion. That is, the heat exchanger can improve the heat exchange performance with the simple configuration as described above.

A heat exchanger according to a seventh aspect of the present invention is the heat exchanger according to the sixth aspect, wherein the laminated body is formed by laminating the plate members having the same shape in opposite directions.

In the heat exchanger of the seventh aspect, since a plurality of plate materials having the same shape (excluding plate thickness) are laminated in the opposite directions to each other to form a laminated body, for example, a plurality of plate materials having different shapes are laminated. The number of components can be reduced as compared with the configuration in which the laminated body is formed. This can suppress an increase in manufacturing cost.

A heat exchanger according to an eighth aspect of the present invention is the heat exchanger according to any one of the first aspect to the fifth aspect, wherein the wall portion on one side in the stacking direction has the plurality of outermost layers. A protrusion is provided to enter the through hole.

In the heat exchanger of the eighth aspect, the simple configuration in which the protrusion provided on the wall portion on the one side in the stacking direction is inserted into the plurality of through holes of the outermost layer on the one side in the stacked body is used. The flow passage area of the outer layer flow passage portion can be made smaller than the flow passage area of the general flow passage portion. That is, the heat exchanger can improve the heat exchange performance with the simple configuration as described above.

As described above, according to the present invention, in a configuration including a stacked body formed by stacking a plurality of layers in which a plurality of through holes are formed, heat flowing in the flow path formed by the plurality of through holes It is possible to provide a heat exchanger in which the flow velocity of the medium can be made uniform in the stacking direction of the stack.

It is a top view of the heat exchanger which concerns on one Embodiment of this invention. FIG. 2 is a sectional view taken along line 2-2 of FIG. 1. FIG. 3 is a sectional view taken along line 3-3 of FIG. 2. It is a top view which shows the surface of the punching board which forms the laminated core of FIG. It is a top view which shows the back surface of the punching plate of FIG. FIG. 3 is an enlarged plan view in which a part of the laminated core of FIG. 2 is enlarged. FIG. 7 is a sectional view taken along line 7-7 of FIG. 3. FIG. 8 is a sectional perspective view taken along line 8-8 of FIG. 6. It is sectional drawing (sectional view corresponding to FIG. 7) of the laminated core used for the heat exchanger which concerns on other embodiment of this invention. It is sectional drawing (sectional view corresponding to FIG. 7) of the laminated core used for the heat exchanger which concerns on other embodiment of this invention. It is a cross-sectional perspective view (cross-sectional perspective view corresponding to FIG. 8) of the laminated core used for the heat exchanger which concerns on other embodiment of this invention. It is a cross-sectional perspective view (cross-sectional perspective view corresponding to FIG. 8) of the laminated core used for the heat exchanger which concerns on other embodiment of this invention. FIG. 8 is a sectional perspective view (a sectional view corresponding to FIG. 7) of a laminated core used in a heat exchanger according to another embodiment of the present invention. It is a graph which shows the pressure loss and heat transfer coefficient of an example and a comparative example.

Hereinafter, a heat exchanger according to an embodiment of the present invention will be described with reference to the drawings. In addition, the arrow X, the arrow Y, and the arrow Z, which are appropriately illustrated in each drawing, respectively indicate the device width direction, the device depth direction, and the device thickness direction of the heat exchanger. Further, in the present embodiment, the arrow Z direction will be described as the device vertical direction.

FIG. 1 shows a heat exchanger 20 of this embodiment. The heat exchanger 20 is used, for example, to cool a heating element H such as a CPU or a power semiconductor element. Specifically, the heating element H is brought into contact with the heat exchanger 20 and the heat of the heating element H is transferred to the refrigerant L flowing inside the heat exchanger 20 to cool the heating element H. .. The heating element H of the present embodiment is an example of the heat exchange target in the present invention. Further, the refrigerant L of the present embodiment is an example of the heat medium in the present invention.

As shown in FIGS. 1 and 2, the heat exchanger 20 of the present embodiment has a case 22 and a laminated core 30 installed in the case 22.

As shown in FIG. 2, the case 22 has a case body 24 and a lid body 26 that closes the opening 24A of the case body 24 in the device thickness direction.

The case main body 24 is composed of a plate-shaped bottom portion 24B and a side wall portion 24C provided upright on the outer peripheral edge portion of the bottom portion 24B. The case body 24 is formed using a metal material (for example, aluminum or copper).

As shown in FIGS. 1 and 2, the lid 26 has a plate shape and is joined to an end surface of the side wall portion 24C of the case body 24 opposite to the bottom portion 24B side. In the present embodiment, the lid 26 is joined to the end surface of the case body 24 by brazing. The lid 26 is formed using a metal material (for example, aluminum or copper).

Further, an inlet 27A through which a refrigerant (for example, cooling water or oil) L flows into the case 22 is formed on the side wall portion 24C of the case body 24 at one end side in the device width direction. A supply pipe 28 (see FIG. 1) connected to a coolant supply source is connected to the inlet 27A. The inlet 27A of the present embodiment is an example of the inlet of the present invention.

Further, the side wall 24C of the case main body 24 is provided with an outlet 27B through which the refrigerant L inside the case 22 flows out on the other end side in the device width direction. A discharge pipe 29 (see FIG. 1) is connected to the outlet 27B. The outlet 27B of the present embodiment is an example of the outlet in the present invention.

As shown in FIGS. 2 and 3, the refrigerant L supplied from the inlet 27A to the inside of the case 22 through the supply pipe 28 flows through a flow path 38 described later formed in the laminated core 30, and the outlet 27B discharges the pipe. It is discharged to the outside through 29. Here, the refrigerant L flows in the case 22 from the inlet 27A toward the outlet 27B.

As shown in FIGS. 3 to 8, the laminated core 30 is configured by laminating a plurality of punched plates 32 having a plurality of through holes 44 formed therein. That is, the laminated core 30 is formed by laminating a plurality of layers, with one punched plate 32 as one layer. The laminated core 30 of the present embodiment is an example of the laminated body of the present invention.

Further, the laminated core 30 is formed by stacking punched plates 32 having the same shape in the opposite directions. Specifically, in the laminated core 30, the back surface 32B of the punching plate 32 is overlapped with the back surface 32B of the punching plate 32 (the surface shown in FIG. 5), and the front surface 32A of the punching plate 32 (shown in FIG. 4). The surface 32A of the punching plate 32 is further overlapped with the surface 32A. The laminated core 30 of this embodiment is formed by laminating six punched plates 32. That is, the laminated core 30 is formed with six layers of punched plates 32. The punched plate 32 of the present embodiment is an example of the plate material of the present invention. Further, in the present embodiment, the stacking direction of the punched plate 32 of the stacked core 30 is the same as the device thickness direction.

The punching plate 32 is formed by punching and forming a plurality of through holes 44 in a metal material plate, and forming a plurality of linear portions 34 and a plurality of connecting portions 36. As the material of the plate material that becomes the punched plate 32, for example, aluminum or copper is preferably used. In this embodiment, from the viewpoint of brazing, a clad steel plate (made of aluminum) whose both sides are brazing material layers is used.

The linear portion 34 is a direction orthogonal to the laminating direction of the laminated core 30 and the direction in which the refrigerant L goes from the inlet 27A to the outlet 27B, that is, the flow direction of the refrigerant L (in the present embodiment, along the device width direction. The strip-shaped portion extends in a wave shape in the same direction) and has a constant width between both ends in the extending direction. The extending direction of the linear portion 34 here is a direction along the center line CL1 passing through the width center of the linear portion 34. The width of the linear portion 34 is a length between both sides of the linear portion 34 measured along a direction orthogonal to one side of the linear portion 34.

Further, the linear portions 34 are a direction orthogonal to the laminating direction of the laminated core 30, and are provided in plural at intervals in the amplitude direction of the wave (in the present embodiment, the direction along the device depth direction). The linear portion 34 of the present embodiment extends in a triangular wave shape (in other words, a zigzag shape) in the flow direction of the refrigerant L. Further, the linear portions 34 that are adjacent to each other in the amplitude direction are arranged in parallel with each other.

The connecting portions 36 are provided at intervals in the extending direction of the linear portions 34, and connect the linear portions 34 that are adjacent to each other in the amplitude direction. The connecting portion 36 is a strip-shaped portion that linearly extends from one linear portion 34 to the other linear portion 34 that is adjacent in the amplitude direction, and has a constant width between both ends in the extending direction. The extending direction of the connecting portion 36 is a direction along the center line CL2 passing through the width center of the connecting portion 36. In addition, the width of the connecting portion 36 is a length between both sides of the connecting portion 36 measured along a direction orthogonal to one side of the connecting portion 36.

As shown in FIG. 6, in one connecting portion 36, between the linear portions 34 that are adjacent to each other in the amplitude direction, a downstream side in the flow direction of the refrigerant L with respect to the top portion 34A of one linear portion 34, that is, in general, The portion 34B is connected to the general portion 34B of the other linear portion 34. Further, the other connecting portion 36 on the downstream side of the one connecting portion 36 in the flow direction of the refrigerant L flows through the refrigerant L more than the general portion 34B of the one linear portion 34 and the top portion 34A of the other linear portion 34. The downstream side of the direction, that is, the general portion 34B is connected. The general portion 34B referred to here is a portion between the top portion 34A and the bottom portion 34C of the linear portion 34. Further, in the present embodiment, since the linear portion 34 has a triangular wave shape, the top portion 34A is a triangular wave corner portion, the bottom portion 34C is a triangular wave corner portion, and the general portion 34B is a triangular wave corner portion and a corner portion. It is a straight part that connects. Further, as shown in FIG. 6, the connecting portion 36 includes a general portion 34B of one linear portion 34 and a general portion 34B of the other linear portion 34 between the linear portions 34 adjacent to each other in the amplitude direction. It is connected.

Further, in the laminated core 30, a plurality (six in the present embodiment) of punched plates 32 are overlapped with the linear portions 34 of the punched plates 32 in opposite directions, and the connecting portions 36 of the punched plates 32 that are overlapped with each other are formed into a line. The laminated portions are stacked so as to be spaced apart from each other in the extending direction of the shaped portions 34 (in other words, arranged so that the connecting portions 36 do not overlap each other). Here, a plurality of through holes 44 are formed between the linear portions 34 adjacent to each other in the wave amplitude direction of the punched plate 32, and the punched plates 32 stacked with each other as described above have respective through holes 44 of the through holes 44. Part of each of them is overlapped with each other in the plate thickness direction (stacking direction) of the punched plate 32. The flow path 38 for the refrigerant L is formed by these through holes 44. Since the flow path 38 is formed by the plurality of through holes 44 between the linear portions 34 of the punched plates 32 which are overlapped with each other and which are adjacent to each other in the amplitude direction, the flow channels 38 are formed in the plate thickness direction (stacking direction) of the punched plates 32. As seen, it is formed in a triangular wave shape like the linear portion 34. As a result, a curved portion is formed in the flow path 38 between the top portion 34A and the bottom portion 34C, and the connecting portion 36 is provided at a position avoiding the apex of the curved portion. The stacked punched plates 32 are joined to each other by brazing.

The plurality of punched plates 32 forming the laminated core 30 are composed of one punched plate 50, one punched plate 52, and a plurality of (four in this embodiment) punched plates 54. There is.

The punched plate 50 is located on one side (upper side of the apparatus in the present embodiment) of the laminated core 30 in the laminating direction and forms one outermost layer. On the other hand, the punching plate 52 is located on the other side (lower side of the apparatus) in the stacking direction of the laminated core 30 on the side opposite to the punching plate 50 and forms the other outermost layer. Further, the plurality of punched plates 54 are located between the punched plate 50 and the punched plate 52 in the stacking direction of the laminated core 30 to form a plurality of intermediate layers. These punched plates 50, 52, 54 have the same shape except for the plate thickness. In other words, the punched plates 50, 52, 54 have at least the same outer shape and the same shape as the through hole 44.

Further, as shown in FIGS. 7 and 8, the plate thickness T1 of the punched plate 50 is made smaller than the plate thickness T2 of the punched plate 52 and the plate thickness T3 of the punched plate 54. In other words, the layer thickness of one outermost layer (the outer layer on the upper side of the device in this embodiment) formed by the punching plate 50 is equal to the outermost layer of the other formed by the punching plate 52 (the outer layer on the lower side of the device in this embodiment). 2) and the thickness of the intermediate layer formed by the punching plate 54. In this embodiment, the plate thickness T2 of the punched plate 52 and the plate thickness T3 of the punched plate 54 are the same.

The outer surface (the surface on the upper side of the device in this embodiment) of the punched plate 50 forming one outermost layer of the laminated core 30 is brazed to the lower surface of the lid 26. That is, the punching plate 50 is arranged on the side closer to the heating element H.

The outer surface of the punched plate 52 forming the other outermost layer of the laminated core 30 (the lower surface of the device in this embodiment) is brazed to the bottom surface of the case body 24. That is, the punched plate 52 is arranged farther from the heating element H than the punched plate 50.

The lid 26 and the bottom portion 24B of the case body 24 sandwich the laminated core 30 from the stacking direction, and the through holes 44 of the punched plate 50 and the through holes 44 of the punched plate 52 are closed. The lid 26 and the bottom portion 24B of the case body 24 of the present embodiment are examples of opposing walls of the case according to the present invention.

As shown in FIGS. 7 and 8, the flow channel 38 is formed of a first outer layer flow channel portion 56, a second outer layer flow channel portion 58, and a general flow channel portion 60.

The first outer layer flow path portion 56 is formed by the lid 26 and the through hole 44 of the punched plate 50. On the other hand, the second outer layer flow path portion 58 is formed by the bottom portion 24B of the case body 24 and the through hole 44 of the punched plate 52. Further, the general flow path portion 60 is formed by the through holes 44 of the plurality of punched plates 54.

The flow passage area of the first outer layer flow passage portion 56 is smaller than the flow passage area of the general flow passage portion 60. Specifically, since the plate thickness T1 of the punched plate 50 is smaller than the plate thickness T3 of the punched plate 54, the width of the first outer layer flow passage portion 56 is the same as the width of the general flow passage portion 60. The height of the first outer layer flow path portion 56 is lower than the height of the general flow path portion 60. The width of each of the first outer layer flow path portion 56 and the general flow path portion 60 here is the width in the direction orthogonal to the extending direction of the flow path 38, that is, between the linear portions 34 adjacent in the amplitude direction. Refers to the distance. Further, the height of each of the first outer layer flow passage portion 56 and the general flow passage portion 60 referred to here is the height of the laminated core 30 in the laminating direction, that is, the layer thickness (thickness of the punched plate).

Next, the function and effect of the heat exchanger 20 of this embodiment will be described.
In the heat exchanger 20, as shown in FIGS. 1 and 2, by disposing the heating element H in contact with the lid 26 of the case 22, heat generation with the refrigerant L flowing in the case 22 through the case 22 is achieved. Heat is exchanged with the body H. Specifically, the heat from the heating element H is transferred to the case 22 and the laminated core 30 via the case 22. The case 22 and the laminated core 30 are cooled by heat exchange with the refrigerant L supplied into the case 22. As a result, the heat of the heating element H is taken (transferred) by the refrigerant L, and the heating element H is cooled.

As shown in FIGS. 7 and 8, the refrigerant L flowing through the general flow path portion 60 flows in the direction from the inlet 27A to the outlet 27B while repeatedly dividing and joining in the stacking direction by the connecting portion 36. Here, the refrigerant L split from the general flow path portion 60 flows into the first outer layer flow path portion 56 that branches outward from the general flow path portion 60 in the stacking direction. Therefore, the flow rate of the refrigerant L flowing through the first outer layer flow path portion 56 is smaller than the flow rate of the refrigerant L flowing through the general flow path portion 60 (refrigerant L that has joined after splitting). Here, in the heat exchanger 20, since the flow passage area of the first outer layer flow passage portion 56 is smaller than the flow passage area of the general flow passage portion 60, the flow velocity of the refrigerant L flowing through the first outer layer flow passage portion 56 is high. Therefore, the flow velocity of the refrigerant L flowing through the flow passage 38 approaches the flow velocity of the refrigerant L flowing through the general flow passage portion 60. That is, the flow velocity of the refrigerant L approaches uniform in the laminating direction of the laminated core 30. By thus increasing the flow velocity of the first outer layer flow path portion 56 on the side closer to the heating element H, it is possible to efficiently remove heat from the heating element H (transfer the heat to the refrigerant L). As a result, in the heat exchanger 20, the heat exchange between the heating element H and the refrigerant L is efficiently performed, and the heat exchange performance is improved.

Further, in the heat exchanger 20, the width of the first outer layer flow passage portion 56 is the same as the width of the general flow passage portion 60, and the height of the first outer layer flow passage portion 56 is lower than the height of the general flow passage portion 60. I am doing it. Thereby, for example, as compared with the configuration in which the width of the first outer layer flow passage portion 56 and the width of the general flow passage portion 60 are made different, the refrigerant L smoothly flows from the general flow passage portion 60 into the first outer layer flow passage portion 56. Therefore, the pressure loss of the refrigerant L can be suppressed.

In the heat exchanger 20, since the through hole 44 of the punched plate 50 and the through hole 44 of the punched plate 50 are closed by the lid 26 and the bottom portion 24B of the case main body 24, for example, the through hole 44 of the punched plate 50 and the punched plate 52 are used. The number of parts can be reduced as compared with the configuration in which the through hole 44 of FIG.

In the heat exchanger 20, the punching plate 50 and the punching plate 54 having the same shape (excluding the plate thickness) have a simple configuration in which the plate thickness T1 is smaller than the plate thickness T3, and the flow of the first outer layer flow path portion 56 is reduced. The passage area can be made smaller than the passage area of the general passage portion 60. That is, the heat exchange performance of the heat exchanger 20 can be improved with a simple configuration in which the plate thickness T1 is thinner than the plate thickness T3.

Further, in the heat exchanger 20, in the second outer layer flow passage portion 58 of the laminated core 30 located on the side farther from the heating element H, even if the flow velocity of the refrigerant L is slower than that of the general flow passage portion 60, the heat exchange performance. Has little effect on Therefore, the flow passage area of the second outer layer flow passage portion 58 and the flow passage area of the general flow passage portion 60 have the same flow passage area, that is, the punching plate 52 and the punching plate 54 are made common to reduce the number of parts. It can be reduced. This can suppress an increase in manufacturing cost.

Then, in the heat exchanger 20, the plurality of punched plates 32 having the same shape are stacked on each other in the opposite directions to form the laminated core 30, so that, for example, a plurality of punched plates having different shapes are stacked to form the laminated core 30. The number of parts can be reduced as compared with the configuration in which the is formed. This can suppress an increase in manufacturing process cost.

In the heat exchanger 20 of the above-described embodiment, six punched plates 32 having the same shape are laminated to form the laminated core 30, but the present invention is not limited to this configuration. If the number of punched plates 32 forming the laminated core 30 is four or more, the effect of the present invention can be achieved.

Further, in the heat exchanger 20 of the above-described embodiment, the linear portion 34 is formed in a triangular wave shape, but the present invention is not limited to this configuration. In the heat exchangers of other embodiments, for example, the linear portion 34 may be formed in a sine wave shape or a trapezoidal wave shape. Further, the linear portion 62 may be formed in a linear shape like the punched plate 33 shown in FIG. 11. The linear portion 62 extends linearly along the flow direction of the refrigerant L.

Further, in the heat exchanger 20 of the above-described embodiment, the punched plates 32 having the same shape (excluding the plate thickness) are laminated to form the laminated core 30, but the present invention is not limited to this configuration. In heat exchangers of other embodiments, punched plates having different shapes may be alternately laminated to form a laminated core.

Further, in the heat exchanger 20 of the above-described embodiment, the heating element H is brought into contact with the surface of the lid body 26, but the present invention is not limited to this configuration. For example, as in the laminated core 64 shown in FIG. 9, the punching plate 66 forming the other outermost layer has the same plate thickness T2 as the plate thickness T1 of the punching plate 50 forming one outermost layer, that is, the intermediate thickness. The punching plate 54 forming the layers may be thinner than the plate thickness T3. In this case, the flow rate of the refrigerant L becomes more uniform in the stacking direction of the stacked core 30. Further, by bringing another heating element H into contact with the lower surface of the case body 24, heat exchange can be performed between the other heating element H and the refrigerant L.

Further, in the heat exchanger 20 of the above-described embodiment, the punched plates 32 are laminated to form the laminated core 30, but the present invention is not limited to this configuration. For example, a laminated core having the same shape as the laminated core 30 may be formed by cutting out from a metal lump, or a laminated core having the same shape as the laminated core 30 may be formed by metal laminating. The laminated core 68 shown in FIG. 12 is formed by metal additive manufacturing, and the layer is defined by the connecting portion 36.

In the heat exchanger 20 of the above-described embodiment, the laminated core 30 is sandwiched by the lid 26 and the bottom portion 24B of the case body 24 from the stacking direction, and the through holes 44 of the punched plate 50 and the punched plates 52 are provided. Although the through hole 44 is closed, the present invention is not limited to this configuration. For example, as shown in FIG. 13, the laminated core 30 may be sandwiched by a pair of plate members 70 from the laminating direction, and the through holes 44 of the punched plate 50 and the through holes 44 of the punched plate 52 may be closed. With such a configuration, the laminated core 30 becomes one component in a state of being sandwiched between the pair of plate members 70, and therefore foreign matter is prevented from entering the plurality of through holes 44 provided in the laminated core 30 during storage during manufacturing. Easy to control.

Furthermore, in the heat exchanger 20 of the above-described embodiment, in order to make the flow passage area of the first outer layer flow passage portion 56 of the laminated core 30 smaller than the flow passage area of the general flow passage portion 60, the punching plate 50 is formed. Although the plate thickness T1 is smaller than the plate thickness T3 of the punched plate 54, the present invention is not limited to this configuration. For example, as in the heat exchanger 72 shown in FIG. 10, a shape that matches the through hole 44 of the punched plate 50 that forms one outermost layer on the back surface of the lid 26 (a shape that can enter the through hole 44). The protrusion 74 may be formed and the protrusion 74 may be inserted into the through hole 44 of the punching plate 50. In this case, the flow passage area of the first outer layer flow passage portion 56 is formed by a simple configuration in which the protrusions 74 provided on the lid 26 are inserted into the plurality of through holes 44 of the punched plate 50 in the laminated core 30. Can be made smaller than the flow passage area of the general flow passage portion 60. That is, the heat exchanger 72 can improve the heat exchange performance with the simple configuration as described above. Further, if the protruding portion 74 is provided on the back surface of the lid body 26, the flow passage area of the first outer layer flow passage portion 56 can be made smaller than the flow passage area of the general flow passage portion 60, so the punched plates 50, 52, 54. The plate thicknesses of can be all the same. That is, the laminated core can be formed by a plurality of punched plates 32 having the same shape. Therefore, the number of parts can be further suppressed.

Further, in the heat exchanger 20 of the above-described embodiment, the heat generating element H is cooled by heat exchange between the refrigerant L and the heat generating element H, but the present invention is not limited to this configuration. In the heat exchangers of other embodiments, for example, the heating target may be heated by heat exchange between the heating medium (an example of the heating medium in the present invention) and the heating target (heat exchange target).

(Test example)
Next, in order to verify the effect of the present invention, two types of heat exchangers of the example to which the present invention is applied and two types of heat exchangers of comparative examples are prepared, while changing the supply amount (flow rate) of the refrigerant. , Heat transfer coefficient and pressure loss were measured. The graph shown in FIG. 14 was obtained from the measured data.

(Test heat exchanger)
Example 1 A heat exchanger having the same structure as the heat exchanger 20 and six laminated cores.
Example 2... A heat exchanger in which the laminated core of Example 1 has eight layers.
Comparative Example 1... A heat exchanger in which all layers of the laminated core of Example 1 have the same layer thickness, that is, the cross-sectional areas of flow passages forming flow passages are all the same.
Comparative Example 2... A heat exchanger in which all the layers of the laminated core of Example 2 have the same layer thickness, that is, the cross-sectional areas of the flow passages forming the flow passages are all the same.

As shown in FIG. 14, the heat exchanger of Example 1 and the heat exchanger of Example 2 to which the present invention is applied are more than the corresponding heat exchangers of Comparative example 1 and Comparative example 2, respectively. It can be seen that the results are good with low pressure loss and high heat transfer coefficient.

The embodiments of the present invention have been described above with reference to the embodiments, but these embodiments are merely examples, and various modifications may be made without departing from the scope of the invention. Further, it goes without saying that the scope of rights of the present invention is not limited to these embodiments.

20 heat exchanger 22 case 27A inlet 27B outlet 38 flow path 30 laminated core (laminated body)
32 Punched plate (plate material)
44 through hole 50 punched plate (plate material forming one outermost layer)
52 Punched plate (plate material forming the intermediate layer)
56 First Outer Layer Flow Path (Outer Layer Flow Path on One Side)
58 Second Outer Layer Channel (Outer Layer Channel on Other Side)
60 General flow path H H heating element (heat exchange target)
T1 plate thickness (thickness of the plate material forming the outermost layer)
T3 plate thickness (thickness of plate material forming the intermediate layer)
64 laminated core (laminated body)
66 Punching plate (plate material forming the other outermost layer)
68 Laminated Core (Laminate)
70 plate material 72 heat exchanger 74 protrusion X device width direction (direction from inlet to outlet)
Z device thickness direction (stacking direction)

Claims (8)

A case provided with an inlet through which the heat medium flows in and an outlet through which the heat medium flows out;
A laminate in which a plurality of layers, each of which is housed in the case and in which a plurality of through holes are formed, are laminated, and a flow path for guiding the heat medium in a direction from the inlet to the outlet is formed by the through holes,
Of the plurality of layers constituting the laminated body, a pair of wall portions sandwiching the laminated body from the laminating direction so as to close the plurality of through holes formed in the outermost layer in the laminating direction,
Equipped with
The flow passage is formed by an outer layer flow passage portion formed by the wall portion and the through hole of the outermost layer, and the through hole of the intermediate layers located inside the outermost layer in the stacking direction. It is formed with the general channel part,
The heat exchanger, wherein the laminated body is configured such that a flow passage area of the outer layer flow passage portion on one side in the stacking direction is smaller than a flow passage area of the general flow passage portion. The laminated body has a width in the direction orthogonal to the laminating direction of the outer layer channel portion on the one side that is the same as the width of the general channel portion, and the height of the outer layer channel portion on the one side in the laminating direction. Is lower than the height of the said general flow path part, The heat exchanger of Claim 1. The heat exchanger according to claim 1, wherein the pair of wall portions are walls of the case that face each other. The wall portion is a plate material,
The heat exchanger according to claim 1 or 2, wherein the stacked body is housed in the case while being sandwiched between a pair of the plate members. The laminated body is housed in the case so that the outer layer flow path portion on the one side is located on the side close to the heat exchange target in contact with the case,
The flow passage area of the outer layer flow passage portion on the other side in the stacking direction located on the side farther from the heat exchange target of the laminate is the same as the flow passage area of the general flow passage portion. The heat exchanger according to any one of 1. The layer is formed of a plate material in which the plurality of through holes are formed,
The heat exchange according to any one of claims 1 to 5, wherein a thickness of a plate material forming the outermost layer on one side in the stacking direction of the laminate is smaller than a thickness of a plate material forming the intermediate layer. vessel. The heat exchanger according to claim 6, wherein the laminated body is formed by laminating the plate materials having the same shape so as to be opposite to each other. The heat exchanger according to claim 1, wherein the wall portion on one side in the stacking direction is provided with a protrusion that enters the plurality of through holes of the outermost layer.