Plate stacked heat exchanger

Abstract

Relieve the concentration of thermal stress in the vicinity of the flow rate restricting portion in the buffer plate laminated heat exchanger and prevent fatigue failure caused thereby. An opening portion identical to the flow path is also provided in the flow rate restricting portion, thereby reducing the rigidity difference from the flow path portion.

Description

Technical Field

[0001] The present invention relates to a plate-laminated heat exchanger that exchanges heat with a heat exchange object such as a semiconductor element. Background Art

[0002] The laminated heat sink described in Patent Document 1 below is formed by laminating a first perforated plate and a second perforated plate in which a plurality of holes are arranged in parallel, and covering the outer periphery with a housing. Further, a heat generating body such as a semiconductor element is mounted on the surface of the housing, and the heat generating body is cooled by a refrigerant flowing in the housing.

[0003] When a plurality of heat generating bodies are arranged separately from each other on the surface of the housing, in order to efficiently cool each heat generating body, it is necessary to concentrate and circulate the refrigerant there.

[0004] Then, holes for allowing the refrigerant to flow are not provided at positions where there is no heat generating body, and thus the refrigerant is supplied only to the heat generating body portion, thereby performing efficient cooling.

[0005] Prior Art Documents

[0006] Patent Documents

[0007] Patent Document 1: WO2017 / 047825 A1 Gazette Summary of the Invention

[0008] Problems to be Solved by the Invention

[0009] However, a difference is generated between the rigidity of the portion without holes for refrigerant flow and the rigidity of the portion with holes. Therefore, there is a concern that thermal stress generated due to the heat and cold cycle accompanying the use and stop of the heat sink is concentrated near the boundary between the portion without holes and the portion with holes, and cracks caused by fatigue failure are generated in the brazed portion in the vicinity.

[0010] In addition, there is also a concern that the solder in the portion without holes flows out to the portion with holes and clogs the holes.

[0011] Therefore, the problem to be solved by the present invention is to solve such problems.

[0012] Means for Solving the Problems

[0013] The present invention described in Technical Solution 1 is a plate-laminated heat exchanger, which includes:

[0014] A core 4 having a plurality of flat first perforated plates 2 and second perforated plates 3 made of metal, wherein the first perforated plates 2 and the second perforated plates 3 are respectively provided with a plurality of openings 1a and non-openings 1b penetrating therethrough in an alternately two-dimensional juxtaposed manner, the perforated plates 2 and 3 are stacked on top of each other, and the openings 1a of the adjacent perforated plates 2 and 3 are offset from each other in the planar direction; and

[0015] A housing 6 that covers the outer periphery of the core 4 and has a manifold portion 5 for the fluid flowing therethrough inside,

[0016] These components are integrally brazed and fixed, and a heat exchange object is mounted on the outer surface of the housing 6,

[0017] The plate stacked heat exchanger has a plurality of fluid flow paths 9, and the fluid meanders in the thickness direction inside the openings 1a of the first perforated plate 2 and the second perforated plate 3 while flowing as a whole in the planar direction,

[0018] The plate stacked heat exchanger is characterized in that,

[0019] Each of the flow paths 9 is formed parallel to each other from one end of the core 4 toward the other end,

[0020] At an intermediate position in the direction orthogonal to the flow path 9, there is a restricting portion 10 juxtaposed with the adjacent flow paths 9 that restricts the flow of the fluid,

[0021] In the restricting portion 10, a plurality of the openings 1a and non-openings 1b are respectively provided in the first perforated plate 2 and the second perforated plate 3 in an alternately two-dimensional juxtaposed manner, and a blocking portion 11 that blocks at least a part of the fluid flow direction to prevent the fluid from flowing is provided.

[0022] The present invention according to Technical Solution 2 is a plate stacked heat exchanger, comprising:

[0023] A core 4 having a plurality of flat first perforated plates 2 and second perforated plates 3 made of metal, wherein the first perforated plates 2 and the second perforated plates 3 are respectively provided with a plurality of openings 1a and non-openings 1b penetrating therethrough in an alternately two-dimensional juxtaposed manner, the two perforated plates 2 and 3 are stacked in contact with each other, and the openings 1a of the adjacent two perforated plates 2 and 3 are offset from each other in the planar direction; and

[0024] A housing 6 that covers the outer periphery of the core 4 and has a manifold portion 5 for the fluid flowing therethrough inside,

[0025] These components are integrally brazed and fixed, and a heat exchange object is mounted on the outer surface of the housing 6,

[0026] The plate-laminated heat exchanger has a plurality of fluid flow paths 9 through which the fluid meanders in the thickness direction within the respective openings 1a of the two perforated plates 2 and 3 and flows as a whole in the planar direction.

[0027] The plate-laminated heat exchanger is characterized in that

[0028] each of the flow paths 9 is formed parallel to each other from one end of the core 4 toward the other end.

[0029] At an intermediate position of the core 4 in a direction orthogonal to the flow path 9, there is a restricting portion 10 that is juxtaposed with the adjacent flow path 9 and restricts the flow of the fluid.

[0030] For the restricting portion 10, similarly to the adjacent flow path 9, a second flow path 12 for the fluid is juxtaposed, and its length is extended longer than the flow path length of the adjacent flow path, and its flow path resistance is formed larger than that of the adjacent flow path 9.

[0031] The invention according to claim 3 is based on the plate-laminated heat exchanger according to claim 2, and is characterized in that the second flow path 12 turns back from one end of the core 4 toward the other end, so that the flow path length of the second flow path 12 is extended longer than the flow path length of the adjacent flow path 9.

[0032] Advantages of the Invention

[0033] In the invention described in claim 1, at an intermediate position in a direction orthogonal to each flow path 9 of the fluid, there is a restricting portion 10 that is juxtaposed with the flow path 9 and restricts the flow of the fluid.

[0034] In this restricting portion 10, a plurality of openings 1a and non-openings 1b are alternately and two-dimensionally juxtaposed and penetrated through the first perforated plate 2 and the second perforated plate 3, and a blocking portion 11 is provided to block at least a part of the fluid flow direction and prevent the fluid from flowing.

[0035] Thus, by providing the blocking portion 11 for blocking the fluid flow in the restricting portion 10, the fluid can be supplied to other necessary flow paths 9 and effectively heat-exchanged with the heat exchange object. And by providing the opening 1a in the restricting portion 10, the rigidity difference with other parts is reduced, so that the generation of cracks caused by thermal cycling can be prevented. And the excess solder at the restricting portion 10 is absorbed by the opening 1a present therein, so that the outflow of the solder from the restricting portion 10 to the flow path 9 can be prevented.

[0036] In the invention described in claim 2, at an intermediate position of the core 4 in a direction orthogonal to each flow path 9, there is a restricting portion 10 that is juxtaposed with the adjacent flow path 9 and restricts the flow of the fluid.

[0037] Regarding this restricting portion 10, similarly to the adjacent flow path 9, a second flow path 12 for fluid is arranged in parallel, whose length is extended to be longer than the flow path length of the adjacent flow path, and whose flow path resistance is formed to be greater than that of the adjacent flow path 9.

[0038] Thus, by making the flow path resistance of the restricting portion 10 greater than that of the adjacent flow path 9, sufficient fluid can be supplied to the flow path 9 and also to the restricting portion 10. Therefore, heat exchange can be effectively performed on the heat exchange object according to the heat distribution generated by the heat exchange object. Also, by arranging the second flow path 12 for fluid in parallel in the restricting portion 10 similarly to the adjacent flow path 9, the rigidity difference from other parts is reduced. Therefore, generation of cracks caused by thermal cycling can be prevented. Moreover, excess solder at the restricting portion 10 is absorbed by the opening 1a existing therein. Therefore, outflow of the solder from the restricting portion 10 to the flow path 9 can be prevented.

[0039] Based on the above structure, in the invention described in the third aspect, the second flow path 12 turns back, so that it is extended to be longer than the flow path length of the adjacent flow path 9.

[0040] By doing so, it is easy to form the second flow path with a long flow path length and a large flow resistance, and the distribution of the fluid to each flow path can be adjusted. Through this adjustment, appropriate heat exchange corresponding to the magnitude of the heat generation amount and heat absorption amount at each position can be achieved. That is, relatively less heat exchange corresponding thereto can be achieved in the part where the heat generation amount and heat absorption amount are relatively small. BRIEF DESCRIPTION OF THE DRAWINGS

[0041] Figure 1 (A) of is a perspective view of the main part of the plate stacked type heat exchanger of the present invention, Figure 1 and (B) of is a top view of its core 4.

[0042] Figure 2 is an exploded perspective view of this heat exchanger.

[0043] Figure 3 is an exploded perspective view of the plate stacked type heat exchanger according to the second embodiment of the present invention.

[0044] Figure 4 (A) of is a top view of the third embodiment of the present invention, Figure 4 and (B) of is Figure 4 an enlarged view of part B in (A) of.

[0045] Figure 5 is a perspective view showing the operation of this third embodiment. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0046] Next, embodiments of the present invention will be described based on the drawings.

[0047] Embodiment 1

[0048] Figure 1 、 Figure 2 is the plate-laminated heat exchanger according to the first embodiment of the present invention, Figure 1 wherein (A) of FIG. is a perspective view of the main part of the core 4, Figure 1 and (B) of FIG. is a top view (B) of the entire core 4. In addition, Figure 2 is an exploded perspective view of this embodiment.

[0049] In this heat exchanger, a first perforated plate 2 and a second perforated plate 3 with different positions of the opening portions 1a are laminated to form the core 4, and the outer periphery of the core 4 is covered with a housing 6. And, a manifold portion 5 is formed inside the housing 6, and each component is integrally brazed and fixed to form the heat exchanger, and a heating element 7 is installed on the outer surface of the housing 6.

[0050] That is, the first perforated plate 2 and the second perforated plate 3 are each composed of a metal plate in which a plurality of opening portions 1a and non-opening portions 1b are alternately arranged two-dimensionally. And, the opening portions 1a of the first perforated plate 2 and the second perforated plate 3 are offset from each other in the plane direction. And, there is a flow path 9 through which the refrigerant 8 meanders in the thickness direction in each opening portion 1a of the first perforated plate 2 and the second perforated plate 3 and flows as a whole in the plane direction. The flow path 9 is formed parallel to each other from one end of the core 4 toward the other end. And, at an intermediate position in the direction orthogonal to the flow path 9, there is a restricting portion 10 that is juxtaposed with the adjacent flow path 9 and restricts the flow of the refrigerant 8.

[0051] The restricting portion 10, like the adjacent flow path 9, is formed by alternately penetrating the first perforated plate 2 and the second perforated plate 3 with a plurality of opening portions 1a and non-opening portions 1b. And, the restricting portion 10 is provided with a blocking portion 11 that blocks at least a part of the flow direction of the refrigerant 8 to prevent the flow of the refrigerant 8.

[0052] In this example, as shown in Figure 1 and Figure 2 , the blocking portions 11 are formed at both ends in the width direction of each plate, thereby preventing the flow of the refrigerant 8.

[0053] Function

[0054] In Figure 2 , the housing 6 that houses the core 4 includes: a housing main body 6a formed in a disk shape; and an end cap 6b that closes the opening of the housing main body 6a. A pair of pipes 17 are arranged separately from each other in the width direction of the housing main body 6a. And, when the core 4 is housed in the housing main body 6a, the manifold portion 5 is formed at both ends in the width direction of the core 4. And, the refrigerant 8 flowing in from one of the pipes 17 flows in the width direction of the core 4.

[0055] At this time, in Figure 1 in (A) of Figure 1 , the refrigerant 8 meanders in the vertical direction between the first perforated plate 2 and the second perforated plate 3 that are alternately stacked up and down, and as a whole, it flows in a straight line direction on the plane.

[0056] In this example, in Figure 2 at the middle position of a plurality of heating elements 7 arranged at intervals on the outer surface of the end cap 6b, a blocking portion 11 of the restricting portion 10 in Figure 1 is arranged. Although the restricting portion 10 is alternately formed with an opening portion 1a and a non-opening portion 1b in the same manner as other parallel flow paths 9 as described above, both ends thereof are blocked by the blocking portion 11. Therefore, the refrigerant 8 does not flow through the restricting portion 10. The refrigerant 8 only flows through each flow path 9 other than the restricting portion 10. And correspondingly to the refrigerant 8 not flowing through the restricting portion 10, the refrigerant 8 is distributed to other flow paths 9. Thus, the refrigerant 8 is efficiently distributed to the positions where the heating elements 7 are present and the heat exchanger is promoted.

[0057] Moreover, a plurality of opening portions 1a and non-opening portions 1b are also formed at the position where the restricting portion 10 is present. Therefore, at the position of the restricting portion 10 and other positions, their structures are substantially the same and their rigidities are also substantially the same. Therefore, when brazing each first perforated plate 2 and the second perforated plate 3 to form a heat exchanger, there will be no local excess of brazing material or brazing material blockage. And at the restricting portion 10, cracks associated with the cooling and heating cycles during the operation of the heat exchanger will not occur.

[0058] Embodiment 2

[0059] Next, Figure 3 is the second embodiment of the present invention. The difference between this embodiment and the above-described embodiment is the shapes of the housing 6 and the core 4.

[0060] The top plate 15 and the bottom plate 14 are provided on the upper and lower surfaces of the core 4. And they are integrally brazed and fixed between the plates. In this example, the manifolds 5 are integrally formed on each perforated plate constituting the core 4.

[0061] The restricting portion 10 and the blocking portion 11 formed in this core 4 are the same as those in the above-described embodiment.

[0062] Embodiment 3

[0063] Next, Figure 4 is the third embodiment of the present invention. Figure 4 (A) of Figure 4 is a top view of this core 4. Figure 4 (B) of Figure 4 is a top view of the main part and is Figure 4 an enlarged view of part B of (A) of Figure 4 . Figure 5 is an explanatory diagram showing its operation.

[0064] This example is the same asFigure 1 The difference from the example is the difference in the structure of the restricting portion 10 of the two.

[0065] In Figure 1 , as the restricting portion 10, the blocking portions 11 that block the opening 1a exist at both ends in the flow direction. In contrast, in Figure 4 's example, the restricting portion 10 forms the second flow path 12, where the refrigerant 8 flows back and forth in the planar direction. Its length is longer compared to other flow paths 9, and the flow resistance increases. That is, compared with the flow path 9 of the adjacent refrigerant 8, the flow path is longer.

[0066] In this example, in Figure 2 , the second flow path 12 is arranged at the middle position between the adjacent heating elements 7 as shown in Figure 4 . For this second flow path 12, the flow path turns back at the turning holes 16 at both ends of the core 4, making its length longer.

[0067] As an example, in this example, it becomes three times the length compared to the length of other flow paths 9. Correspondingly, the flow resistance of the refrigerant 8 becomes larger. However, since the refrigerant 8 also flows in the second flow path 12, in Figure 2 , the heat exchange is also promoted at the edge portions of the adjacent heating elements 7. Also, the opening 1a and the non-opening 1b are respectively formed in the first perforated plate 2 and the second perforated plate 3, and the restricting portion 10 also has a structure substantially the same as other parts, capable of coping with thermal cycling. And, there will be no blockage of the holes during the brazing of each plate.

[0068] Other embodiments

[0069] In the above-described third embodiment, by turning back the second flow path 12 at the turning holes 16 at both ends of the core 4 in the restricting portion 10, the length of the second flow path 12 is made longer than that of the flow path 9. However, instead of turning back, in the restricting portion 10, the lengths of the fluid flow directions of the opening 1a and the non-opening 1b can be made shorter than those of the flow path 9 and a greater number of them can be alternately penetrated, and the second flow path 12 can be made to meander more times in the stacking direction of the first perforated plate 2 and the second perforated plate 3, thereby making the length of the second flow path 12 longer than that of the flow path 9.

[0070] The plate stack type heat exchanger of each of the above embodiments is used to cool the heating element (heat exchange object) using the refrigerant (fluid), but is not limited to this use. The refrigerant as the fluid can also be replaced with a warm fluid, and the plate type heat exchanger of the present invention can be used for the purpose of heating the heat exchange object.

[0071] Explanation of reference numerals

[0072] 1a Opening

[0073] 1b Non-opening part

[0074] 2 First punching plate

[0075] 3 Second punching plate

[0076] 4 Core

[0077] 5 Manifold part

[0078] 6 Housing

[0079] 6a Housing main body

[0080] 6b End cover

[0081] 7 Heating element

[0082] 8 Refrigerant

[0083] 9 Flow path

[0084] 10 Restriction part

[0085] 11 Blocking part

[0086] 12 Second flow path

[0087] 13 Claw part

[0088] 14 Bottom plate

[0089] 15 Top plate

[0090] 16 Return hole

[0091] 17 Pipe

Claims

1. A plate-laminated heat exchanger, comprising: A core (4) having a plurality of flat metal first perforated plates (2) and second perforated plates (3), wherein the first perforated plates (2) and the second perforated plates (3) are respectively provided with a plurality of openings (1a) and non-openings (1b) penetrating therethrough in an alternately two-dimensionally juxtaposed manner, each of the perforated plates (2, 3) is laminated with each other, and the openings (1a) of adjacent perforated plates (2, 3) are offset from each other in the plane direction; and A housing (6) that encloses the outer periphery of the core (4) and has a manifold portion (5) for the fluid flowing therein inside, These components are integrally brazed and fixed to each other, and a heat exchange object (7) is mounted on the outer surface of the housing (6), The plate-laminated heat exchanger has a plurality of fluid flow paths (9), and the fluid (8) meanders in the thickness direction in the openings (1a) of the first perforated plate (2) and the second perforated plate (3) and flows as a whole in the plane direction through the flow paths (9), The plate-laminated heat exchanger is characterized in that Each of the flow paths (9) is formed parallel to each other from one end of the core (4) toward the other end, There is a restricting portion (10) that is juxtaposed with an adjacent flow path (9) and restricts the flow of the fluid at an intermediate position in the direction orthogonal to the flow path (9), In the restricting portion (10), a plurality of the openings (1a) and non-openings (1b) are respectively provided in the first perforated plate (2) and the second perforated plate (3) in an alternately two-dimensionally juxtaposed manner, and a blocking portion (11) is provided to block at least a part of the fluid flow direction to prevent the fluid (8) from flowing, 2. A plate-laminated heat exchanger, comprising: A core (4) having a plurality of flat metal first perforated plates (2) and second perforated plates (3), wherein the first perforated plates (2) and the second perforated plates (3) are respectively provided with a plurality of openings (1a) and non-openings (1b) penetrating therethrough in an alternately two-dimensionally juxtaposed manner, the two perforated plates (2, 3) are laminated in contact with each other, and the openings (1a) of adjacent two perforated plates (2, 3) are offset from each other in the plane direction; and A housing (6) that encloses the outer periphery of the core (4) and has a manifold portion (5) for the fluid flowing therein inside, These components are integrally brazed and fixed to each other, and a heat exchange object (7) is mounted on the outer surface of the housing (6), The plate-laminated heat exchanger has a plurality of fluid flow paths (9), and the fluid (8) meanders in the thickness direction in the openings (1a) of the two perforated plates (2, 3) and flows as a whole in the plane direction through the flow paths (9), The plate-laminated heat exchanger is characterized in that Each of the flow paths (9) is formed parallel to each other from one end of the core (4) toward the other end, There is a restricting portion (10) that is juxtaposed with an adjacent flow path (9) and restricts the flow of the fluid at an intermediate position of the core (4) in the direction orthogonal to the flow path (9), For the restricting portion (10), similarly to the adjacent flow path (9), a second flow path (12) of fluid is arranged in parallel, the length of which is extended to be longer than the flow path length of the adjacent flow path, and the flow path resistance thereof is formed to be larger than that of the adjacent flow path (9).

3. The laminated plate type heat exchanger according to claim 2, characterized in that the second flow path (12) turns back from one end of the core (4) toward the other end, so that the flow path length of the second flow path (12) is extended to be longer than the flow path length of the adjacent flow path (9).

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