JP6162836B2 - Heat exchanger - Google Patents

Description

Embodiments of the present invention relates to a heat exchanger having a micro channel for heat exchange between fluids with temperature difference.

In recent years, in order to cope with an increase in heat generation density due to high integration of semiconductor elements and miniaturization of electronic devices typified by mobile phones, development of heat dissipation devices that are small and have high heat exchange performance is required. In addition, from the viewpoint of preventing global warming, there is a growing momentum for efficiently recovering energy from low-temperature heat sources that have been discarded as waste heat. For this purpose, a microchannel heat exchanger disclosed in Patent Document 1 using an anisotropic porous material has been proposed.
In this heat exchanger, by using a material having the same hole diameter and hole direction, pressure loss is reduced, and variations in hole diameter and flow path width can be controlled. In addition, since the flow paths of the high temperature fluid and the low temperature fluid are stacked close to each other and the fluids are made to face each other, high heat exchange efficiency is realized.

  However, since it is difficult to make all the high-temperature fluid flow paths and low-temperature fluid flow paths adjacent to each other, the heat transfer coefficient between the fluid and the porous material is high, and the heat conductivity of the porous material is low. Has a problem that the fin porosity decreases. Moreover, since the high-temperature and low-temperature fluid is distributed using the sealing plate, the pressure loss is increased, the productivity is lowered, and the cost is increased.

  In the laminated flow path element disclosed in Patent Document 2, the flow paths are stacked in a direction orthogonal to the flow, and the high temperature / low temperature flow paths are arranged in a direction approaching each other from the inlet to the heat exchange portion, and heat exchange is performed. From the part to the outlet, the high-temperature and low-temperature channels are arranged in directions away from each other, so that the high-temperature channel and the low-temperature channel are adjacent to each other in one direction perpendicular to the flow. It is the structure which does not require the sealing plate for use.

  However, the heat exchange performance is limited because the hot and cold fluids are adjacent to each other in only one direction, and the opening ratio of the flow path at the inlet / outlet is less than 50%, so avoid an increase in pressure loss. I can't.

JP 2010-216736 A JP 2009-30870 A JP 2008-147240 A

The present invention has been made in order to solve the above-described problems, and an object thereof is to provide a heat exchanger having high heat exchange performance.

The heat exchanger according to the present invention sequentially opens the heat conductive thin plate having a plurality of holes so that the holes and holes of the adjacent thin plates communicate with each other. A heat exchanger having a thin-plate laminate in which a plurality of flow paths penetrating in the stacking direction are formed, wherein the plurality of flow paths are formed of a plurality of first flow paths through which a first heat transfer medium flows. 1 channel group and a second channel group composed of a plurality of second channels through which the second heat transfer medium flows, and the relative positions of the holes of the thin plate in a two-dimensional projection plane field of view, and at least one of shape, comprises a structure for stacking thin varied gradually, said to produce a heat transfer at least two different directions in a thin plate stack, a first flow passage belonging to the first channel group the second flow path and at least two different people belonging to the second flow path group In are arranged next to each other, said plurality of thin plates each other so that the first heat transfer medium present in the high temperature region can conducts the heat to the thin laminate for flowing through the first flow path group And the second heat transfer medium existing in the low temperature region having a temperature lower than the high temperature region can be transferred to the thin plate laminate in order to be thermally connected to the second flow group. As described above, the plurality of thin plates are thermally connected to each other .

(A) is an internal see-through | perspective perspective view which shows the heat exchanger which concerns on 1st Embodiment typically, (b)-(k) is a cross section which shows the flow-path cross section in each site | part of the heat exchanger of (a). Pattern diagram. (A) (b) is a figure for demonstrating the manufacturing method of a heat exchanger. (A) is an internal perspective view which shows the modification of the heat exchanger which concerns on 1st Embodiment, (b)-(k) is a cross section which shows the flow-path cross section in each part of the heat exchanger of (a). Pattern diagram. (A) is an internal see-through | perspective perspective view which shows the heat exchanger which concerns on 2nd Embodiment typically, (b)-(m) is a cross section which shows the flow-path cross section in each site | part of the heat exchanger of (a). Pattern diagram. The expansion perspective view which expands and shows a part of heat exchanger concerning a 4th embodiment. (A) is a perspective view which shows typically the inlet side of the heat exchanger which concerns on 5th Embodiment, (b) is a distribution map which shows typically the flow velocity distribution and temperature distribution of a fluid. (A) is a perspective view which shows typically the inlet side of the heat exchanger which concerns on 6th Embodiment, (b) is a distribution map which shows typically the flow velocity distribution and temperature distribution of a fluid.

  A preferred embodiment of the present invention will be described below.

  (1) The heat exchanger according to the present embodiment sequentially stacks the heat conductive thin plates having a plurality of holes so that the holes of the adjacent thin plates communicate with each other. A heat exchanger having a thin plate laminate in which a plurality of flow paths that open and penetrate in the stacking direction are formed, wherein the plurality of flow paths are a plurality of first flow paths through which a first heat transfer medium flows. And a second flow path group consisting of a plurality of second flow paths through which the second heat transfer medium flows, and relative to the holes of the thin plate in a two-dimensional projection plane field of view The first flow path belonging to the first flow path group and the first flow path group so as to cause heat transfer in at least two different directions in the thin plate laminate by laminating the thin plates by changing at least one of the various positions and shapes The second flow paths belonging to the second flow path group are arranged adjacent to each other. That.

  In this embodiment, in the two-dimensional projection plane field of view, the thin plate is laminated by changing the relative positions of the holes of the thin plate (by shifting the holes), and the first flow path and the second flow path are adjacent to each other. The first heat transfer medium flows in one direction through the first flow path group from two different directions in the thin plate laminate, that is, from one side, and from the other side opposite to the first heat transfer medium. The second heat transfer medium is passed through the two flow path groups in the opposite direction opposite to the one direction (FIGS. 1 and 3).

  In the present embodiment, the relative shape of the holes in the thin plate is changed in the two-dimensional projection plane view (the cross-sectional shape of the flow path is changed and / or the flow paths are branched and merged). The first flow path and the second flow path are arranged adjacent to each other in close proximity to each other, and in the thin plate laminate, the first flow path passes through the first flow path group from two different directions, that is, from one side. The heat transfer medium is caused to flow in one direction, and the second heat transfer medium is caused to flow in the opposite direction opposite to the one direction from the other side facing the heat transfer medium through the second flow path group (FIG. 4).

  As described above, in the present embodiment, the first flow path belonging to the first flow path group and the second flow path belonging to the second flow path group are arranged adjacent to each other. The channel and the second channel approach each other, and the mutual distance from the first channel to the second channel is shortened. As a result, the heat exchange rate is improved. For example, the first heat transfer medium that flows from the high temperature region to the first flow channel group and the second heat flow medium that flows from the low temperature region to the second flow channel group. High-efficiency heat transfer occurs between the heat transfer medium and a heat exchanger having a high heat exchange rate.

  (2) In the above (1), the thin plate laminate may be composed of one or more metals or alloys selected from the group consisting of copper, aluminum, iron, stainless steel, titanium and titanium alloys. preferable. These metals or alloys not only have good thermal conductivity, but can also be used to produce thin plate laminates that are integrated by joining thin plates in a temperature range considerably lower than their melting point using diffusion bonding or the like. There are manufacturing advantages.

  (3) In any one of the above (1) or (2), the first heat transfer medium existing in the high temperature region can be transferred to the thin plate laminate in order to be passed through the first flow path group. Since the plurality of thin plates are thermally connected to each other and are passed through the second flow path group, the second heat transfer medium existing in the low temperature region lower in temperature than the high temperature region is transmitted to the thin plate laminate. It is preferable that the plurality of thin plates are thermally connected to each other so that they can be heated.

  According to the present embodiment, a plurality of laminated thin plates are closely bonded together using a diffusion bonding method or the like to improve not only the heat conduction between the liquid and the solid but also the heat conductivity between the solid and the solid. Therefore, a heat exchanger having a high heat exchange rate as a whole can be obtained.

  (4) In the above (3), at least a part of the high temperature region and the low temperature region is formed by laminating a deformed thin plate having a plurality of holes, and the plurality of the plurality of holes formed by the plurality of holes of the thin plate. A flow path can spatially connect the inflow side and the outflow side of each of the high temperature region and the low temperature region.

  In the present embodiment, when the first and second heat transfer media are supplied to the inflow side of each of the high temperature region and the low temperature region via a manifold, a header, or the like, the high temperature region and the low temperature region pass through the plurality of flow paths. The heat exchange is effectively performed between the first and second heat transfer mediums while reaching each of the outflow sides and exiting the thin plate laminate.

  According to the present embodiment, it is not necessary to leave a space for adjoining the heat / cold two fluids in the heat exchange region at the inlet / outlet portion, and for the flow path before the inlet and after the outlet, The opening ratio of the heat exchanger can be increased.

  (5) In any one of the above (1) to (4), the total length of the boundary portion between the high temperature region and the low temperature region in the cross section crossing the flow channel is the outer peripheral length of the flow channel. It can be set to 1/2 or more.

  According to the present embodiment, the total length of the boundary portion between the high temperature region and the low temperature region is ½ or more of the outer peripheral length of the flow path, so that the heat transfer rate from the heat transfer medium to the thin plate laminate can be increased. The heat exchange rate can be further improved.

  (6) In any one of the above (1) to (5), when the average perimeter of the cross section of the flow path is L and the average area is S, the formula D = 4 * S / L. The equivalent diameter D can be 10 mm or less.

  In the present embodiment, it is clarified that a microchannel heat exchanger having a fine flow path (microchannel) whose flow path equivalent diameter D is 10 mm or less is targeted. In the microchannel heat exchanger having such a fine flow path, the flow resistance in the microchannel increases, so the opening ratio of the heat exchanger is set as large as possible, and the microchannel inlet and outlet portions are It is necessary to minimize the pressure loss that occurs.

  (7) The manufacturing method of the heat exchanger according to the present embodiment includes (a) producing a leading segment thin plate having a plurality of holes, and (b) one-to-one corresponding to the plurality of holes in the leading segment thin plate. Further sequentially producing a plurality of subsequent segment laminae having a plurality of holes, at least one of the plurality of holes being gradually displaced in the two-dimensional projection plane field of view relative to the position of the hole of the leading segment lamina, (C) Starting from the top segment thin plate, the subsequent segment thin plates are sequentially stacked, thereby forming a thin plate laminate assembly in which a plurality of segment thin plates are laminated, and (d) adjacent segments in the thin plate laminate The thin plates are joined together by a joining means, whereby the thin plate laminate assembly is integrated into a thin plate laminate, and the plurality of segments in the thin plate laminate are combined. A plurality of heat exchange channels that are three-dimensionally continuous and open at both ends; and (e) a first channel through which the first heat transfer medium flows through the plurality of heat exchange channels. A first flow path belonging to the group and a second flow path belonging to the second flow path group through which the second heat transfer medium flows, and heat transfer is generated in at least two different directions in the thin plate laminate. Thus, the first flow path belonging to the first flow path group and the second flow path belonging to the second flow path group are arranged adjacent to each other.

  According to this embodiment, since the plurality of first flow paths and the plurality of second flow paths are arranged next to each other, the first flow path and the second flow path approach each other, and The mutual distance from the first channel to the second channel is shortened. As a result, the heat exchange rate is improved. For example, the first heat transfer medium that flows from the high temperature region to the first flow channel group and the second heat flow medium that flows from the low temperature region to the second flow channel group. High-efficiency heat transfer occurs between the heat transfer medium and a heat exchanger having a high heat exchange rate.

  Hereinafter, various preferred embodiments for carrying out the present invention will be described with reference to the accompanying drawings.

(First embodiment)
The heat exchanger according to the first embodiment will be described with reference to FIG.

  The heat exchanger 1 of this embodiment includes a thin plate laminate 10 in which first and second flow paths 4 and 5 for heat exchange are formed, and a plurality of unillustrated attachments attached to both end faces of the thin plate laminate 10. , A first heat transfer medium supply source (not shown) that supplies the first heat transfer medium to the first manifold that communicates with the first flow path 4, and a second that communicates with the second flow path 5. And a second heat transfer medium supply source (not shown) for supplying the second heat transfer medium to the manifold.

  The thin laminate 10 is a rectangular parallelepiped extending in the X-axis direction, and a plurality of flow paths 4 and 5 are formed therein. These flow paths 4 and 5 are through-holes that extend substantially along the longitudinal axis (X axis) of the thin plate laminate 10 and open at both end surfaces 2 and 3 of the thin plate laminate, and are not shown. The 1st or 2nd heat-transfer medium supplied from is flowing.

  In addition to the rectangular parallelepiped of the present embodiment, the thin plate laminate can be formed in various shapes such as a cylinder, a semi-column, a long cylinder, an elliptical column, a triangular column, a hexagonal column, and an octagonal column. Moreover, the heat exchange channel of the thin plate laminate can have various cross-sectional shapes such as a circular shape, a semicircular shape, and a rectangular shape. In this embodiment, the cross-sectional shape of the flow paths 4 and 5 is circular. When the cross-sectional shape of the channel is circular, the diameter is desirably 1 μm or more and 10 mm or less. When the diameter of the flow path is less than 1 μm, it becomes difficult to manufacture and the pressure loss increases remarkably. On the other hand, when the diameter of the flow path exceeds 10 mm, the surface area in contact with the heat transfer medium is insufficient, and the heat exchange performance is deteriorated.

  The end surface 2 on one side of the thin plate laminate 10 is divided into two rectangular regions of an entrance surface 21 and an exit surface 22. Nine first flow paths 4 are open on the entrance surface 21. Nine second flow paths 5 are open on the outlet surface 22. A first heat transfer medium is supplied to the inlet surface 21 at a desired pressure from a first heat transfer medium supply source (not shown) via a first inlet manifold (not shown). The second heat transfer medium after exchanging heat with the first heat transfer medium flowing through the first flow path 4 is discharged from the outlet face 22 to a second outlet manifold (not shown).

  The end surface 3 on the other side of the thin plate laminate 10 is divided into two rectangular regions of an exit surface 31 and an entrance surface 32. Nine second flow paths 5 are opened in the entrance surface 32. Nine first flow paths 4 are open on the outlet surface 31. The inlet surface 32 is supplied with a second heat transfer medium at a desired pressure from a second heat transfer medium supply source (not shown) via a second inlet manifold (not shown). The first heat transfer medium after exchanging heat with the second heat transfer medium flowing through the second flow path 5 is discharged from the outlet surface 31 to a first outlet manifold (not shown).

  Next, materials used for manufacturing the thin plate laminate will be described.

  It is preferable to use one or more metals or alloys selected from the group consisting of copper, aluminum, iron, stainless steel, titanium, and titanium alloys as the material for the segment thin plates that make up the thin plate laminate. . For heat exchangers that require particularly high thermal conductivity, it is preferable to use copper, iron, aluminum, and alloys thereof. In addition, when the heat exchanger is required to have impact resistance and corrosion resistance, stainless steel, titanium, and a titanium alloy are preferable.

  Next, a manufacturing method of the thin plate laminate will be described with reference to FIG.

  First, a leading segment thin plate m1 having a plurality of holes is prepared using a copper thin plate. With reference to the leading segment thin plate m1, a plurality of subsequent segment thin plates m2, m3, m4 in which at least one of the plurality of holes is gradually displaced in the two-dimensional projection plane view with respect to the position of the hole of the leading segment thin plate m1. .About.mn are sequentially produced. These subsequent segment thin plates m2, m3, m4 to mn have a plurality of holes corresponding one-to-one with the plurality of holes of the leading segment thin plate m1.

  As a hole forming method, a method described in Patent Document 3, a chemical processing process such as etching or electroforming, a cutting process using a drill, a machining process such as press processing, electric discharge processing, or laser processing is used. . Here, the holes are provided in almost all portions of the segment thin plates m1 to mn of various shapes described below, and the holes are penetrated as heat exchangers by accurately aligning the positions of the segment thin plates m1 to mn. A flow path is formed. As the lamination method, known methods such as diffusion bonding, brazing, and adhesion can be used.

  As shown in FIG. 2 (a), starting from the first segment thin plate m1, the subsequent segment thin plates m2, m3, m4 to mn are sequentially stacked, whereby a thin plate laminate assembly in which a plurality of segment thin plates are laminated. Form. In the stacking of the segment thin plates m1 to mn, the positions of the holes between the layers are gradually shifted in a direction different from the above-described section so that the two fluids of warm and cold are adjacent to each other in two directions with respect to the flow direction. In the next section, the layers are stacked so that the holes in each layer are aligned in one direction, but this is the section with the highest heat exchange performance between the high temperature fluid and the low temperature fluid. Next, the positions of the terms between the layers are gradually shifted so as to be adjacent in only one direction perpendicular to the flow direction. Next, the positions of the holes between the layers are gradually shifted so that the flow paths of the two hot and cold fluids are gathered.

  The thin plate laminate assemblies stacked in this way are placed in a diffusion furnace, heated to a predetermined temperature range in a vacuum or an inert gas atmosphere, and diffusion bonded between the segment thin plates m1 to mn. As a result, as shown in FIG. 2B, a thin plate laminate 10 in which the thin plate laminate assembly is integrated is obtained. In the obtained thin plate laminate 10, the holes of the plurality of segment thin plates are three-dimensionally continuous, and a plurality of flow paths 4 and 5 that are open at both end surfaces are formed. In these flow paths, the first flow path 4 belonging to the first flow path group and the second flow path 5 belonging to the second flow path group are adjacent to each other so as to cause heat transfer in different directions. Matching.

  Next, the arrangement of the first and second flow paths and the change in their relative positions will be described with reference to FIGS.

  The thin plate laminate 10 has five different flow path sections A to E divided by the surfaces 1b to 1k. That is, there are five sections: vertical shift section A, horizontal shift section B, vertical / horizontal adjacent section C, horizontal shift section D, and vertical shift section E. In these sections A to E, the arrangement of the flow passages is gradually changed as described below, so that the end faces 1b and 1k and the cross sections 1c to 1j are as shown in FIGS. However, the arrangement of the flow paths is different.

  In the vertical direction shifting section A defined from the surface 1b to the surface 1d, first, in the end surface 1b, as shown in FIG. One flow path 4 is opened in an arrangement state of 3 rows × 3 rows. In the drawing, nine second flow paths 5 are opened in an outlet state 22 which is a rectangular area in the lower half in an arrangement state of 3 rows × 3 rows. Furthermore, the relative position of the group of the first flow path 4 of 3 columns × 3 rows and the group of the second flow path 5 of 3 rows × 3 rows is shifted in the Y-axis direction by approximately half a pitch. doing.

  In the cross section 1c, as shown in FIG. 1C, three of the first flow paths 4 in the upper half rectangular area (projection area) in the figure are the lower half rectangular area (projection area). On the other hand, three of the second flow paths 5 in the lower half rectangular area (projection area) in the drawing are arranged in the upper half rectangular area (projection area). Furthermore, nine groups of the first flow paths 4 are unevenly distributed in the left half area in the figure, while nine groups of the second flow paths 5 are unevenly distributed in the right half area in the figure. Yes.

  In the cross section 1d, as shown in FIG. 1 (d), nine groups of the first flow paths 4 are arranged symmetrically from the center in the figure, while 9 groups vertically symmetrical from the center in the figure. A group of two second flow paths 5 is arranged. The group of nine first flow paths 4 and the group of nine second flow paths 5 are arranged adjacent to each other only in the horizontal direction (Y direction). However, the entire group including the first and second flow paths 4 and 5 is arranged in 6 rows × 3 rows.

  In the horizontal direction shifting section B defined from the surface 1d to the surface 1f, as shown in (d), (e), and (f) of FIG. The upper row and the lower row are displaced in the horizontal direction (−Y direction), and the middle row is displaced in the opposite horizontal direction (+ Y direction).

  In the vertical / horizontal adjacent section C defined from the surface 1f to the surface 1g, as shown in FIG. 1 (g), a group of nine first flow paths 4 and a group of nine second flow paths 5 Are arranged adjacent to each other in the vertical direction (Z direction) and also arranged adjacent to each other in the horizontal direction (Y direction).

  In the horizontal direction shifting section D defined from the surface 1g to the surface 1i, as shown in (g) and (h) of FIG. The lower row is displaced in the horizontal direction (−Y direction), and the middle row is displaced in the opposite horizontal direction (+ Y direction). As a result, as shown in FIG. 1 (i), the entire group including the first and second flow paths 4 and 5 without any positional deviation in the horizontal direction (Y-axis direction) is 6 rows × 3 horizontal. Arranged in rows.

  In the vertical direction shifting section E defined from the surface 1i to the surface 1k, as shown in FIG. 1 (j), the overall arrangement is the same as in FIG. 1 (c) described above. As shown in FIG. 1 (k), the arrangement returns to the same arrangement as that of FIG. 1 (b) described above.

  As described above, the flow paths 4 and 5 of the two hot and cold fluids divided at the inlet portion of the heat exchanger have two or more directions perpendicular to the flow through the through flow paths in arbitrary directions. Adjacent. The flow direction of both fluids can be freely selected, but in order to improve the heat exchange performance, a counterflow type as shown in the figure is generally desirable. Note that the diameter and the number of flow paths of the hot and cold fluids may be different.

  The operation and effect of this embodiment will be described.

  In this embodiment, in the two-dimensional projection plane field of view, the relative positions of the holes of the thin plate are changed (the holes are displaced), and the thin plates are stacked, and the first flow path and the second flow path are mutually connected. Adjacent to each other, the first heat transfer medium flows in one direction through the first flow path group from two sides in the thin plate laminate, that is, from one side, and from the other side opposite to the first heat transfer medium. The second heat transfer medium is passed through the second flow path group in a facing direction opposite to the one direction.

  In the present embodiment, since the first flow path belonging to the first flow path group and the second flow path belonging to the second flow path group are arranged adjacent to each other, the first flow path and the first flow path The two flow paths approach each other, and the mutual distance from the first flow path to the second flow path becomes shorter. For this reason, the heat exchange rate is improved, for example, the first heat transfer medium that flows from the high temperature region to the first flow channel group and the second heat flow that flows from the low temperature region to the second flow channel group. High-efficiency heat transfer occurs between the heat transfer medium and the heat exchange rate.

  According to this embodiment, the heat transfer coefficient between the fluid and the solid is high, the thermal resistance of the solid is large, and the size of the channel cross section perpendicular to the flow direction is larger than when the hot / cold fluid contacts only in one direction. If the distance between the flow paths is shorter than that, the heat exchange performance is expected to be improved. For example, when high-temperature and low-temperature fluids are adjacent to each other in two directions, the heat transfer area is doubled at a maximum as compared with the case of only one direction, so the heat exchange amount is also doubled at maximum.

(Second Embodiment)
Next, the heat exchanger of 2nd Embodiment is demonstrated with reference to FIG. In addition, description of the part which this embodiment overlaps with said embodiment is abbreviate | omitted.

  In 1 A of heat exchangers of this embodiment, the cross-sectional shape of the 1st and 2nd flow paths 4 and 5 in the thin-plate laminated body 10A is made into the rectangle.

  According to this embodiment, since the cross-sectional shape of the flow paths 4 and 5 is rectangular, the contact area with the heat transfer medium is increased as compared with the flow path having a circular cross-sectional shape in the above-described embodiment. Efficiency is improved.

  In the present embodiment, the material of the thin plate laminate 10A is titanium.

  According to the present embodiment, by producing the thin plate laminate with titanium, the corrosion resistance is improved as compared with the thin plate laminate produced with copper of the above embodiment, the maintenance cost is suppressed, and the life of the heat exchanger is extended. Can be expected.

(Third embodiment)
Next, a heat exchanger according to a third embodiment will be described with reference to FIG. In addition, description of the part which this embodiment overlaps with said embodiment is abbreviate | omitted.

  In the heat exchanger 1B of the present embodiment, the cross-sectional shapes of the first and second flow paths 4 and 5 in the thin plate laminate 10B are changed in some sections. The arrangement of the first and second flow paths 4 and 5 and the change in the cross-sectional shape thereof will be described with reference to FIGS.

  The thin plate laminate 10B has five different flow path sections A to E divided by the surfaces 1b to 1m. That is, there are five sections: a flow path cross section deformation section A, a horizontal shift section B, a vertical / horizontal adjacent section C, a horizontal shift section D, and a flow path cross section deformation section E. In these sections A to E, since the cross-sectional shape of the flow path is gradually changed as described below, the end faces 1b and 1m and the cross sections 1c to 1l are respectively shown in FIGS. 4B to 4K. Thus, the arrangement of the flow paths is different.

  In the flow passage cross section deformation section A defined from the surface 1b to the surface 1e, the cross sectional shape of the flow passage is changed from a rectangular shape to an elongated triangular shape as shown in FIGS. 4B and 4C. ) And (d), the cross-sectional shape of the flow path from a long and narrow triangular shape to a narrow rectangular shape, and from a narrow rectangular shape to a small square shape as shown in FIGS. 4 (d) and (e), respectively. Has changed.

  In the first sections 1b to 1c of section A, as shown in FIGS. 4B and 4C, two stages × 3 rows of three upper rectangular channels 4 and three lower rectangular channels 5 are arranged. From the arrangement and shape, the three elongated inverted triangular channels 4 and the three elongated triangular channels 5 are alternately arranged and arranged side by side. More specifically, the top of the inverted triangular channel 4 enters between the two triangular channels 5, and the top of the triangular channel 5 enters between the two inverted triangular channels 4, so that the triangle as a whole. The shape of the flow path is changed to a side-by-side arrangement and shape.

  In the next sections 1c to 1d of section A, as shown in FIGS. 4 (c) and 4 (d), six triangular channels are arranged from the side-by-side arrangement and shape. The layout and shape are changed side by side. More specifically, three narrow rectangular channels 4 and three narrow rectangular channels 5 are alternately arranged side by side.

  In the sections 1d to 1e following the section A, the small square flow is obtained from the arrangement and shape of the six horizontal rows of the narrow rectangular channels 4 and 5 as shown in FIGS. 4 (d) and 4 (e). The arrangement and shape of the roads 4 and 5 are changed to 6 rows and 6 rows.

  In the horizontal direction shifting section B defined from the surface 1e to the surface 1g, as shown in FIGS. 4E, 4F, and 4G, the small square-shaped flow paths 4 and 5 are arranged in 6 columns vertically and horizontally, respectively. The first, third, and fifth stages are shifted to the left in the horizontal direction in the figure, and the second, fourth, and sixth stages are shifted to the right in the horizontal direction in the figure. (Shift in Y direction).

  In the vertical / horizontal adjacent section C defined from the surface 1g to the surface 1h, as shown in FIG. 4 (h), the small square channel 4 and the channel 5 are arranged adjacent to each other in six columns in length and width. Has been.

  In the horizontal direction shifting section D defined from the surface 1g to the surface 1i, like the section B, the first stage, the third stage, the fifth stage of the small square-shaped channels 4 and 5 each having six columns in the vertical and horizontal directions. The positions of the eyes are shifted to the right in the horizontal direction in the drawing, and the positions of the second, fourth, and sixth steps are shifted to the left in the horizontal direction in the drawing (shift in the Y direction).

  In the channel cross section deformation section E defined from the surface 1j to the surface 1m, as in the section A, the small square shape as shown in (j), (k), (l), and (m) in FIG. The shape changes from a rectangular shape to a triangular shape to a rectangular shape, and the arrangement changes in the order of 6 rows in the vertical direction, 6 rows in the horizontal direction, 3 rows in the upper row, and 3 rows in the lower row.

  The operation and effect of this embodiment will be described.

  In the present embodiment, the thin plate is laminated by changing the relative shape of the holes of the thin plate in the two-dimensional projection plane field of view (changing the cross-sectional shape of the flow path and / or merging after branching the flow path). The first flow path and the second flow path are arranged adjacent to each other and adjacent to each other, and in the thin plate laminate, the first transmission path passes through the first flow path group from two different directions, that is, from one side. The heat medium is caused to flow in one direction, and the second heat transfer medium is caused to flow in the opposite direction opposite to the one direction through the second flow path group from the other side opposite to the heat medium.

  In this embodiment, it is not necessary to leave a space for adjoining different kinds of fluids in the mixing region at the inlet / outlet portions, and the opening of the heat exchanger is open to the flow path before the inlet and after the outlet. The rate can be increased, and an increase in pressure loss at the inlet / outlet portions can be prevented, and at the same time, the entire apparatus can be miniaturized. In addition, since the high-temperature fluid and the low-temperature fluid have structures that are adjacent to each other in two or more directions before the mixing portion, the distance until mixing can be shortened.

(Fourth embodiment)
Next, a heat exchanger according to a fourth embodiment will be described with reference to FIG. In addition, description of the part which this embodiment overlaps with said embodiment is abbreviate | omitted.

  In the heat exchanger 1C of the present embodiment, a rib 6 having a rectangular opening 7 is attached to an appropriate position of the flow paths 4 and 5 of the thin plate laminate, and the diameter D1 of the flow paths 4 and 5 is partially narrowed to a small diameter D2. ing. The ratio between the diameters D1 and D2 can be determined according to process conditions such as pressure loss.

  According to this embodiment, it is possible to easily form an arbitrary ribbed flow path by changing the diameter and shape of the holes between the adjacent stacked layers. In particular, the two-dimensional unevenness shown in FIG. 5 can be produced by reducing the diameter of the hole of the thin member to be laminated only at the protruding portion.

  Incidentally, in the method of laminating the channels perpendicular to the flow direction, it is necessary to perform three-dimensional processing on each layer when the rib 6 is formed. In this embodiment, the diameter of the hole between adjacent segment thin plates By changing the shape, it is possible to easily produce a flow path with ribs.

(Fifth embodiment)
Next, the heat exchanger of 5th Embodiment is demonstrated with reference to FIG. In addition, description of the part which this embodiment overlaps with said embodiment is abbreviate | omitted.

  In the heat exchanger 1d of the present embodiment, the aperture adjustment ribs 6a, 6b, 6c are attached at appropriate positions in the flow path to adjust the aperture ratio distribution. For example, the end face 2 (or 3) of the thin plate laminate is suitable as the attachment position of the diameter adjusting ribs 6a, 6b, 6c on the inlet side of the heat transfer medium.

  The operation of this embodiment will be described.

  As shown in FIG. 6B, in the flow velocity / temperature distribution curve P1, the flow velocity vector 8 at the center of the heat exchanger is larger than the flow velocity vector 9 at the peripheral portion. For this reason, the temperature of the central portion is likely to be higher than that of the peripheral portion, and heat is likely to be accumulated in the central portion. When the flow velocity and temperature at the inlet portion of the heat exchanger are distributed, the flow rate and temperature of each flow path inside the heat exchanger are not uniform, causing an increase in pressure loss and a decrease in heat exchange performance.

  However, in this embodiment, it is assumed at the entrance portion from the flow paths (reduced diameter flow paths) 7, 7 a, 7 b, 7 c narrowed by the ribs 6 a, 6 b, 6 c by attaching the diameter adjustment ribs 6 a, 6 b, 6 c. By distributing the pore diameter of the layer in the vicinity of the inlet corresponding to the flow velocity / temperature distribution, variations in the flow rate / temperature flowing through each flow path can be suppressed.

(Sixth embodiment)
Next, a heat exchanger according to a sixth embodiment will be described with reference to FIG. In addition, description of the part which this embodiment overlaps with said embodiment is abbreviate | omitted.

  In a microchannel heat exchanger having a fine flow path, the flow resistance in the microchannel increases, so the opening ratio of the heat exchanger is set as large as possible, and pressure loss occurs at the inlet and outlet portions of the microchannel. Must be kept as small as possible.

  In the heat exchanger 1E of the present embodiment, the flow path length adjusting ribs 61 and 62 are attached to appropriate positions of the flow path so as to extend the length of some of the flow paths. That is, the first flow path length adjusting ribs 61 are attached to the end faces 2 and 3, respectively, so that the length of the flow path 71 located substantially in the center is longer than the other peripheral flow paths 4 and 5. Further, the second flow path length adjusting ribs 62 are respectively attached to the end faces 2 and 3 so that the length of the flow path 72 located in the center is longer than the other flow paths 71 in the vicinity.

  The operation of this embodiment will be described.

  As shown in FIG. 7B, in the flow velocity / temperature distribution curve P2, the flow velocity vector 8 at the center of the heat exchange bundle is larger than the flow velocity vector 9 at the peripheral portion. For this reason, the temperature of the central portion is likely to be higher than that of the peripheral portion, and heat is likely to be accumulated in the central portion. When the flow velocity and temperature at the inlet portion of the heat exchanger are distributed, the flow rate and temperature of each flow path inside the heat exchanger are not uniform, causing an increase in pressure loss and a decrease in heat exchange performance.

  However, in the present embodiment, the first flow path length adjusting ribs 61 are respectively attached to the end faces 2 and 3 so that the length of the flow path 71 located substantially in the center is longer than the other flow paths 4 and 5 in the vicinity. Further, the second flow path length adjusting ribs 62 are respectively attached to the end faces 2 and 3, and the length of the flow path 72 located in the center is made longer than the other flow paths 71 in the vicinity. Variations in flow rate and temperature flowing through the road can be suppressed.

  The heat exchanger of the present invention can be used as a cooler for cooling various devices and apparatuses that generate heat during operation and raise the temperature. In particular, the heat exchanger of the present invention may be widely used in various fields as a cooler having microchannels for cooling small and thin electronic devices.

  Moreover, the heat exchanger of the present invention can effectively use exhaust heat exhausted from various devices and apparatuses, and can improve the efficiency of exhaust heat utilization.

  Furthermore, the heat exchanger of the present invention can also be used for improving the performance of new energy utilization technologies such as biomass.

1, 1A, 1B, 1C, 1D, 1E ... heat exchanger,
1b, 1c, 1d, 1e, 1f, 1g, 1h, 1i, 1j, 1k, 1l, 1m ... surface,
A, B, C, D, E ... section,
10, 10A, 10B ... thin plate laminate,
2, 3 ... end face, 21, 32 ... inlet face, 22, 31 ... outlet face,
4 ... 1st flow path, 5 ... 2nd flow path,
6, 6a, 6b, 6c ... caliber rib,
7, 7 a, 7 b, 7 c...
61, 62 ... flow path length adjusting ribs,
71, 72 ... an extended flow path extended by ribs,
P1, P2 ... Flow velocity / temperature distribution curve,
m1, m2-mm-mn ... Segment thin plate.

Claims (9)

A plurality of flow paths that open at both ends in the laminating direction and penetrate in the laminating direction by sequentially laminating heat conductive thin plates having a plurality of holes so that the holes and holes of adjacent thin plates communicate with each other A heat exchanger having a thin plate laminate in which is formed,
The plurality of flow paths include a first flow path group including a plurality of first flow paths through which the first heat transfer medium flows, and a second flow path including a second flow path through which the second heat transfer medium flows. Including a channel group,
The at least one of relative position and shape of the holes of the sheet in a two-dimensional projection plane field includes structure for stacking thin varied gradually so as to produce a heat transfer at least two different directions in the sheet stack the a first first belonging to the flow channel groups of the channel and the second channel belonging to the second flow path groups are arranged next to one another in at least two different directions,
The plurality of thin plates are thermally connected to each other such that the first heat transfer medium existing in a high temperature region to be passed through the first flow path group can transfer heat to the thin plate laminate; and The plurality of thin plates are mutually connected so that the second heat transfer medium existing in a low temperature region lower in temperature than the high temperature region can be transferred to the thin plate laminate in order to flow through the second distribution group. A heat exchanger characterized in that it is thermally connected to . The thin laminate, rectangular, cylindrical, semi-cylindrical, long cylinder, elliptic cylinder, a triangular prism, and having any polygonal shape such as octagonal prism, the heat exchanger according to claim 1. The cross-sectional shape of the flow path of the sheet stack, characterized in that it has a rectangular, triangular, circular, any polygonal shape such as a semicircle, the heat exchanger according to claim 1. In the two-dimensional projection plane field of view, the thin plate laminate has a section 1 in which the relative positions of the holes in the thin plate are gradually shifted, and a section 2 in which the relative positions of the holes in the thin plate are gradually shifted in the vertical direction from the section 1. When the heat exchanger according to claim 1, wherein the first flow path and the second flow path and having a section 3 which is adjacent in at least two different directions, the. In the two-dimensional projection plane field of view, the thin plate laminate has a section 1 in which the relative positions of the holes in the thin plate are gradually shifted, and a section 2 in which the relative positions of the holes in the thin plate are gradually shifted in the vertical direction from the section 1. A section 3 in which the first flow path and the second flow path are adjacent in at least two different directions, a section 4 for gradually shifting the relative positions of the holes of the thin plate, and a hole of the thin plate the heat exchanger according to claim 1, characterized in that it comprises a section 5 for shifting gradually the relative position in the vertical direction and the section 4, the. In the two-dimensional projection plane field of view, the thin plate laminate is a section 1 that gradually deforms the shape of the holes of the thin plate,
2. The heat exchanger according to claim 1, wherein the first flow path and the second flow path have a section 2 adjacent in at least two different directions . In the thin plate laminate, in the two-dimensional projection plane view, the section 1 that gradually deforms the shape of the hole of the thin plate, and the first flow path and the second flow path are adjacent to each other in at least two different directions. The heat exchanger according to claim 1 , comprising a section 2 and a section 3 that gradually deforms the shape of the hole of the thin plate . The heat exchanger according to claim 1, wherein an aperture adjustment rib is attached to an end of the flow path to adjust an aperture ratio distribution. The heat exchanger according to claim 1, wherein a flow path length adjusting rib is attached to an end of the flow path to adjust a flow path length distribution.