Cooling heat exchanger

Abstract

The utility model provides a cooling heat exchanger with a novel structure, which can enable a heat medium to stably flow in a cooling flow path and effectively generate the flow of the heat medium crossing a bulge, so that the cooling performance is improved. A cooling heat exchanger in which a cooling flow path (16) through which a cooling heat medium flows is formed therein and which cools an object to be cooled (17) that overlaps a cooling surface (18), in which a protrusion (34) that disturbs the flow of the heat medium is provided on the cooling flow path (16) so as to protrude from the bottom surface of the cooling flow path (16), and the protrusion (34) extends over the entire flow path width of the cooling flow path (16). Both ends of the protrusion (34) are formed as connecting end portions (54) that are continuous with the side wall portions of the cooling flow path (16), and the connecting end portions (54) in the protrusion (34) are formed as flow regulation portions (56) that extend in the flow path length direction of the cooling flow path (16) in a shape that is recessed toward the bottom surface side.

Description

Technical Field

[0001] This invention relates to a heat exchanger for cooling, for example, for use in cooling objects such as battery packs for electric vehicles. Background Technology

[0002] For example, in electrified vehicles such as electric vehicles and hybrid vehicles, the heat generated by battery packs and other objects to be cooled increases due to miniaturization and higher performance, making cooling performance increasingly important for these battery packs. As a cooling heat exchanger for cooling battery packs and other objects, a structure having a cooling flow path for the flow of a cooling medium has been conventionally proposed, as disclosed in U.S. Patent No. 10,355,331 (Patent Document 1). In this cooling heat exchanger, the cooling surface overlaps with the object being cooled, such as the battery pack, and the cooling surface is cooled by the heat medium flowing in the cooling flow path, thereby cooling the object.

[0003] Existing technical documents

[0004] Patent documents

[0005] Patent Document 1: U.S. Patent No. 10,355,331 Utility Model Content

[0006] Problems to be solved by the utility model

[0007] However, the figures in Patent Document 1 illustrate a structure with a protrusion extending into the cooling flow path. In Patent Document 1, this protrusion locally reduces the cross-sectional area of ​​the cooling flow path. The protrusion is formed by making at least one of the upper and lower walls of the cooling flow path recessed in a point-like manner, and the protrusion is locally provided in both the width and length directions of the cooling flow path.

[0008] However, if such a localized protrusion is formed, it can easily cause the flow of hot medium in the cooling flow path to bypass the protrusion along the width of the flow path, thereby inhibiting the flow over the protrusion. In addition, there is a risk that the flow of hot medium bypassing the protrusion and passing through the side wall of the cooling flow path becomes faster, which could lead to the wall of the cooling flow path, including the protrusion, being worn by the high-velocity hot medium, and there is also a risk of leakage and other adverse conditions.

[0009] The drawings of Patent Literature 1 also show a protrusion that is continuous throughout the full length in the flow path width direction of the cooling flow path. However, it is also considered that the heat medium flowing at both end portions in the flow path width direction of the cooling flow path is subjected to greater flow resistance under the influence of the side wall portion of the cooling flow path than the heat medium flowing at the middle in the flow path width direction, and thus, when a protrusion of a constant height like that of Patent Literature 1 is formed throughout the full length in the flow path width direction of the cooling flow path, a decrease in the local flow rate of the heat medium occurs at both end portions in the flow path width direction, thereby causing an adverse situation of impeding the flow of the heat medium or generating an undesirable vortex.

[0010] The present application solves the problem by providing a heat exchanger for cooling with a new structure, which can stably flow the heat medium in the cooling flow path and effectively generate the flow of the heat medium over the protrusion, thereby achieving an improvement in cooling performance.

[0011] Means for solving the problem

[0012] Hereinafter, preferred modes for grasping the present application will be described, but each mode described below is an illustrative mode, and not only can be appropriately combined and adopted with each other, but also can be as independently as possible to recognize and adopt the plurality of constituent elements described in each mode, and can be appropriately combined and adopted with any constituent element described in other modes. Thus, in the present application, it is not limited to the modes described below, and various other modes can be achieved.

[0013] The first mode is a heat exchanger for cooling, which has a cooling flow path in which a heat medium for cooling flows formed therein, and cools a cooling object overlapping a cooling surface, in which a protrusion that disturbs the flow of the heat medium is provided protruding from a bottom surface of the cooling flow path, the protrusion extends throughout the entire of the flow path width of the cooling flow path, both end portions of the protrusion are formed as connection end portions continuous with side wall portions of the cooling flow path, and the connection end portions in the protrusion are formed as flow adjusting portions extending in the flow path length direction of the cooling flow path in a shape recessed toward the bottom surface side.

[0014] According to the heat exchanger for cooling formed in accordance with the present mode, since there is no gap between the protrusion and the side wall portion of the cooling flow path, the flow of the heat medium through the gap is restricted, and thus it becomes easy to generate the flow over the protrusion, and thus the turbulent flow promoting effect (stirring effect of the heat medium) based on the protrusion is effectively exerted.

[0015] The connection end portions constituting both end portions of the protrusion are continuous with the side wall portions of the cooling flow path, and no gap without the protrusion is formed between the protrusion and the side wall portion of the cooling flow path, thereby preventing the polishing of the flow path wall surface or the like caused by the rapid flow that has passed through the gap, and thus avoiding adverse situations such as liquid leakage.

[0016] It is also considered that the flow resistance of the heat medium flowing in the both end portions of the side wall portion close to the flow path portion easily becomes larger than the flow resistance of the heat medium flowing in the middle portion away from the side wall portion, and therefore when a protrusion of the same height as the middle portion is provided in the connecting end portion of the both end portions of the side wall portion, the flow is excessively restricted, and the flow of the heat medium in the both end portions in the flow path width direction of the cooling flow path deteriorates. Therefore, the connecting end portion of the both end portions of the protrusion constituting the side wall portion of the cooling flow path is provided as a flow adjusting portion of a shape recessed toward the bottom surface side, whereby the height of the both end portions of the protrusion can be adjusted in a manner that the heat medium flows moderately, and thus the improvement and stabilization of the cooling performance are achieved.

[0017] The second aspect is the cooling heat exchanger according to the first aspect, wherein the bottom portion of the flow adjusting portion formed in a recessed shape is formed as a curved surface.

[0018] According to the cooling heat exchanger formed in the structure according to the present aspect, the bottom portion of the flow adjusting portion becomes easily smoothly continuous with respect to the inner surface of the side wall of the cooling flow path. In addition, the heat medium passing over the flow adjusting portion becomes easily smoothly flowing.

[0019] The third aspect is the cooling heat exchanger according to the first or second aspect, wherein the bottom portion of the flow adjusting portion is directly continuous with the protruding front end of the side wall portion protruding from the bottom surface of the cooling flow path.

[0020] According to the cooling heat exchanger formed in the structure according to the present aspect, for example, the connecting end portion of the protrusion is continuous with the protruding front end of the side wall portion, whereby the height of the connecting end portion easily becomes high on the continuous side with the side wall portion, but the connecting end portion of the protrusion is formed as a flow adjusting portion of a recessed shape, whereby it is possible to prevent the case where the flow of the heat medium is excessively hindered by the connecting end portion of the protrusion.

[0021] The fourth aspect is the cooling heat exchanger according to any one of the first to third aspects, wherein the protrusion is inclined in the flow path length direction of the cooling flow path while extending in the flow path width direction of the cooling flow path.

[0022] The present aspect relates to the cooling heat exchanger in which the heat medium flowing in the cooling flow path passes over the protrusion in a substantially orthogonal direction, and therefore the protrusion extends obliquely with respect to the flow direction of the heat medium, that is, the flow path length direction of the cooling flow path, and according to the cooling heat exchanger, the flow direction of the heat medium when passing over the protrusion easily becomes the oblique direction with respect to the flow path length direction. As a result, the heat medium passing over the protrusion can easily generate a change in the flow direction in the flow path width direction, and more effectively generate disturbance of the flow of the heat medium.

[0023] Further, when the protrusions are formed in an inclined shape as in the present embodiment, the heat medium becomes easy to flow along the protrusions to the end portions in the flow path width direction. In this case, for example, there is a concern that when the protrusions or the like are formed so as to extend over the entire width of the cooling flow path, the height of the width direction end portions (connection end portions) of the protrusions is high, the heat medium guided along the protrusions in the flow path width direction flows into the corner portion formed in a closed loop shape at the connection portion of the connection end portions of the protrusions and the side wall portion of the flow path portion, and thus stagnation and turbulence of the heat medium occur in the corner portion, resulting in a decrease in cooling performance due to an obstruction of the flow of the heat medium. Therefore, the connection end portions of the protrusions are provided as the concave flow adjusting portions, and thus it is possible to make it difficult for the stagnation and turbulence of the heat medium to occur at the end portions in the flow path width direction, and it is possible to effectively obtain the effect of an increase in cooling performance due to the heat medium passing over the protrusions. On the other hand, for example, there is a concern that when there is a gap between the both ends of the protrusions and the side wall of the flow path in the flow path width direction, a straight and high-speed flow portion connecting the gaps occurs in the flow path length direction in combination with the guiding action of the heat medium by the inclined protrusions, and thus the heat exchange performance decreases or the erosion action to the side wall portion forming the gap becomes a problem. In the present embodiment, by providing the flow adjusting portions between the both ends of the protrusions and the side wall portion, it is possible to appropriately adjust the flow state of the heat medium in the gaps, and it is possible to achieve a reduction or elimination of the problems described above.

[0024] The fifth aspect is the cooling heat exchanger according to the fourth aspect, wherein the protrusions extend obliquely toward either one of the upstream side and the downstream side of the cooling flow path from both sides in the flow path width direction of the cooling flow path.

[0025] According to the cooling heat exchanger formed in accordance with the present aspect, the oblique directions of the both side portions of the protrusions are formed in opposite directions to each other, and thus the heat media passing over the both side portions of the protrusions converge with each other or flow apart from each other toward the side wall portion on the downstream side of the protrusions. In either case, the flow directions of the heat media change in the flow path width direction, and thus the temperature difference of the heat media in the flow path width direction is reduced, and thus an increase in cooling performance due to the uniformization of the temperature of the heat media is achieved.

[0026] The sixth aspect is the cooling heat exchanger according to the fifth aspect, wherein the protrusions are formed in a V shape obliquely extending toward the downstream side of the cooling flow path from both sides in the flow path width direction of the cooling flow path.

[0027] According to the cooling heat exchanger formed in accordance with the structure of the present aspect, the protrusions are formed in a V shape obliquely extending toward the downstream side from both sides in the flow path width direction, and the heat media passing over the both side portions of the protrusions converge with each other on the downstream side of the protrusions. Thus, on the downstream side of the protrusions, the flow of the heat media is disturbed or a vortex or the like is formed, and thus an increase in cooling performance due to the agitation of the heat media is advantageously achieved.

[0028] In the cooling heat exchanger according to any one of the first to sixth aspects, a width dimension of the flow regulating portion in the flow path width direction of the cooling flow path is in a range of 1 to 30% with respect to a width dimension of the protrusion in the flow path width direction of the cooling flow path.

[0029] According to the cooling heat exchanger formed in the structure according to the present aspect, the width dimension of the flow regulating portion is 1% or more with respect to the width dimension of the protrusion, and thus the effective flow of the heat medium due to the provision of the flow regulating portion can be more effectively achieved. In addition, the width dimension of the flow regulating portion is 30% or less with respect to the width dimension of the protrusion, and thus the middle portion of the protrusion (the portion after the removal of the flow regulating portion toward the inner side in the flow path width direction) that can more advantageously stir the heat medium can be designed with a sufficiently large width.

[0030] Effect of Invention

[0031] According to the present invention, the heat medium can be stably flowed in the cooling flow path, and the flow of the heat medium over the protrusion can be effectively generated, and thus the improvement of the cooling performance of the cooling heat exchanger can be achieved. BRIEF DESCRIPTION OF DRAWINGS

[0032] Figure 1 is an exploded perspective view of the cooling heat exchanger according to the first embodiment of the present invention.

[0033] Figure 2 is a cross-sectional view of the cooling heat exchanger shown in Figure 1 , which corresponds to a II-II cross section of Figure 3 .

[0034] Figure 3 is a III-III cross-sectional view of Figure 2 .

[0035] Figure 4 is a view that shows a portion of a IV-IV cross section of Figure 2 in an enlarged manner.

[0036] Figure 5 is a view that shows a portion of a V-V cross section of Figure 3 in an enlarged manner.

[0037] Figure 6 is a cross-sectional view that shows a portion of the cooling heat exchanger according to the second embodiment of the present invention.

[0038] Explanation of Reference Numerals

[0039] 10: cooling heat exchanger (first embodiment);

[0040] 12: upper plate;

[0041] 14: lower plate

[0042] 16: cooling flow path

[0043] 17: battery pack (cooling object)

[0044] 18: cooling surface

[0045] 20: outer peripheral fixed portion

[0046] 22: liquid seal region

[0047] 24: partition wall portion

[0048] 26: inlet side flow path portion

[0049] 28: supply port

[0050] 30: outlet side flow path portion

[0051] 32: discharge port

[0052] 34: protrusion

[0053] 35: bottom surface

[0054] 36: inclined portion

[0055] 38: ridge line

[0056] 40: protrusion top

[0057] 42: protrusion base

[0058] 44: upstream inclined portion

[0059] 46: downstream inclined portion

[0060] 48: turbulent flow portion

[0061] 50: laminar flow portion

[0062] 52: inclined surface

[0063] 54: connection end portion

[0064] 56: flow regulating portion

[0065] 70: cooling heat exchanger (second embodiment)

[0066] 72: protrusion

[0067] 74: connection end portion

[0068] 76: flow regulating portion

[0069] R: radius of curvature of protrusion top

[0070] L: length dimension of the base of the protrusion;

[0071] α: inclination angle of the upstream inclined portion;

[0072] β: inclination angle of the downstream inclined portion;

[0073] h, h': minimum height dimension of the flow regulating portion;

[0074] H: height dimension of the protrusion on the ridge line;

[0075] w1: width dimension of the flow regulating portion;

[0076] w2: width dimension of the middle portion of the protrusion after the flow regulating portion is removed;

[0077] W: width dimension of the protrusion. DETAILED DESCRIPTION

[0078] Hereinafter, the embodiments of the present application will be described with reference to the drawings.

[0079] Figures 1-3 represents a cooling heat exchanger 10 as a first embodiment of the present application. The cooling heat exchanger 10 has a structure in which an upper plate 12 and a lower plate 14 are fixedly attached to each other in a superposed manner, and a cooling flow path 16 in which a cooling medium flows is formed inside. Further, the cooling heat exchanger 10 cools a battery pack 17 as a cooling target superposed with the upper plate 12 by heat exchange of the cooling medium flowing in the cooling flow path 16 and the battery pack 17. In the following description, the up-down direction refers to the up-down direction in FIG. 1, the left-right direction refers to the flow path length direction of the cooling flow path 16, that is, the left-right direction in FIG. 2, and the front-rear direction refers to the flow path width direction of the cooling flow path 16, that is, the front-rear direction in FIG. 3. Figure 3 Figure 2 Figure 2

[0080] The upper plate 12 is formed in a substantially rounded rectangular plate shape, and is formed to be longer in the left-right direction than in the front-rear direction. The upper plate 12 is preferably formed of a material having a high thermal conductivity, for example, an electrically conductive synthetic resin mixed with an electrically conductive filler such as a metal, a metal particle, or the like. The upper plate 12 of the present embodiment is formed of a metal. The upper surface of the upper plate 12 is formed as a cooling surface 18 on which the battery pack 17 is superposed. The cooling surface 18 is formed as a flat surface and extends orthogonally with respect to the up-down direction. In the present embodiment, the upper plate 12 is formed to have a substantially constant thickness dimension throughout the entirety, and the upper surface (cooling surface 18) and the lower surface of the upper plate 12 are formed to be substantially parallel to each other.

[0081] ​​​The lower plate 14 is formed in a substantially rectangular plate shape with rounded corners corresponding to the upper plate 12 when viewed in the up-down direction, and is longer in the left-right direction than in the front-rear direction. The lower plate 14 is formed of, for example, a metal such as iron or an aluminum alloy, a synthetic resin, or the like. The lower plate 14 can be a mold formed product, but is formed as a punched metal piece in the present embodiment.

[0082] The lower plate 14 is formed with a peripheral fixed portion 20 in which the peripheral end portion is protruding upward. The peripheral fixed portion 20 is formed in a substantially U-shaped cross-sectional shape with opposite up-down directions, and has a flat portion in which the upper end surface extends substantially parallel with respect to the up-down direction. Further, the flat portion of the upper end surface of the peripheral fixed portion 20 overlaps the lower surface of the peripheral end portion of the upper plate 12, and is fixed by means such as adhesion, fusion, brazing, or the like, whereby the upper plate 12 and the lower plate 14 are fixed to each other at the peripheral end portion.

[0083] The peripheral fixed portion 20 of the lower plate 14 is liquid-tightly fixed to the upper plate 12 over the entire periphery. Thus, a liquid seal region 22 that is liquid-tightly separated from the outside space is formed on the inner periphery side of the peripheral fixed portion 20 between the upper plate 12 and the lower plate 14.

[0084] A plurality of partition wall portions 24 are provided in the left-right direction intermediate portion of the lower plate 14. Like the peripheral fixed portion 20, the partition wall portions 24 are provided so as to protrude upward. The cross-sectional shape of the partition wall portions 24 of the present embodiment is formed in a substantially U-shaped cross-sectional shape with opposite up-down directions. The partition wall portions 24 extend linearly in the left-right direction. The both end portions of the partition wall portions 24 are away from the peripheral fixed portion 20 in the left-right direction. In the present embodiment, four partition wall portions 24, 24, 24, 24 are arranged at substantially equal intervals in the front-rear direction in the liquid seal region 22. Further, the left-right intermediate portion of the liquid seal region 22 is divided into five in the front-rear direction by the four partition wall portions 24, 24, 24, 24, and a cooling flow path 16 is formed between the edge portions of the peripheral fixed portion 20 on the front-rear sides adjacent in the flow path width direction and the partition wall portions 24, and between the partition wall portions 24 and 24 adjacent in the flow path width direction, respectively.

[0085] The bottom wall portion of each cooling flow path 16 in the present embodiment is constituted by the flat plate-shaped lower wall portion of the lower plate 14. In addition, the side wall portions on the width direction both sides of each cooling flow path 16 are constituted by the partition wall portions 24, the peripheral fixed portion 20 that stand from the bottom wall portion in the lower plate 14. Further, the upper wall portion of each cooling flow path 16 is constituted by the flat plate-shaped upper plate 12. That is, the upper end of each side wall portion is formed as the protruding front end surface of the partition wall portion 24, the peripheral fixed portion 20 that stands from the bottom wall portion in the lower plate 14 and overlaps the upper plate 12.

[0086] The upstream side, i.e., the left end, of the cooling flow path 16 is connected to the inlet-side flow path section 26. The inlet-side flow path section 26 is located to the left of the partition wall section 24, forming the left end of the liquid seal region 22. The inlet-side flow path section 26 is not divided by the partition wall section 24 along the flow path width direction, and five cooling flow paths 16, 16, 16, 16, 16, 16 branch out to the right from the inlet-side flow path section 26. A supply port 28 is provided in the inlet-side flow path section 26, penetrating the lower wall of the lower plate 14, and the supply port 28 is connected to an external pipeline (not shown). Furthermore, in the operating state of the cooling heat exchanger 10, a low-temperature heat medium is supplied from the external pipeline to the inlet-side flow path section 26 through the supply port 28.

[0087] The downstream side, i.e., the right end, of the cooling flow path 16 communicates with the outlet side flow path 30. The outlet side flow path 30 is located to the right of the partition wall 24, forming the right end of the liquid seal region 22. Similar to the inlet side flow path 26, the outlet side flow path 30 is not divided along the flow path width by the partition wall 24, and five cooling flow paths 16 converge in the outlet side flow path 30. A discharge port 32 penetrating the lower wall of the lower plate 14 is provided in the outlet side flow path 30, and the discharge port 32 is connected to an external pipeline (not shown). Furthermore, in the operating state of the cooling heat exchanger 10, the heat medium heated by heat exchange with the object to be cooled (described later) is discharged from the outlet side flow path 30 to the external pipeline through the discharge port 32. In addition, the supply port 28 and the discharge port 32 are located at opposite corners of the lower plate 14. In addition, the length and width of the inlet-side flow path 26 and the outlet-side flow path 30 are made to be approximately the same.

[0088] Multiple protrusions 34 are formed in the cooling flow path 16. The protrusions 34 are formed to project upwards from the bottom surface 35 of the cooling flow path 16. For example... Figure 2 As shown, the protrusion 34 is roughly V-shaped when viewed from the top surface. Specifically, the protrusion 34 has a pair of inclined portions 36 extending along both the length and width of the cooling flow path 16, with the inclination directions of these inclined portions 36 being different from each other. The pair of inclined portions 36 extend inclinedly from the center of the cooling flow path 16 in the width direction towards both sides and downstream, i.e., to the right. The protrusion 34 is formed such that the ridge line 38 connecting the apexes of the cross-section extends in a V-shape when viewed from the top surface.

[0089] Figure 4 This is a magnified view of the cross-section along the length of a flow path of a protrusion 34. Figure 4 In the cross-section shown, protrusion 34 is formed into a tapered cross-section shape with a narrow width towards the protruding front end. More specifically, inFigure 4 In the illustrated cross section, the protrusion 34 is formed in a cross-sectional shape that continuously has a protrusion top portion 40 curved in a circular arc shape, an upstream inclined portion 44 that extends obliquely toward the upstream side from an end portion on the upstream side of the protrusion top portion 40 toward the protrusion base portion 42 (lower end portion of the protrusion 34), and a downstream inclined portion 46 that extends obliquely toward the downstream side from an end portion on the downstream side of the protrusion top portion 40 toward the protrusion base portion 42. Further, the protrusion 34 is formed in a cross-sectional shape that is substantially constant in a cross section orthogonal to the ridge line 38, and is formed in a cross-sectional shape that is substantially constant in a cross section parallel to the ridge line 38. Figure 4 The cross-sectional shape in the flow path length direction of the front and rear center is substantially the same.

[0090] In Figure 4 In the illustrated cross section, the radius of curvature R of the protrusion top portion 40 including the ridge line 38 is in a range of 0.05 to 1.5 times the length dimension L in the flow path length direction of the protrusion base portion 42, and is more preferably formed in a range of 0.2 to 1.45 times. The radius of curvature R of the protrusion top portion 40 is 0.05 times or more the length dimension L of the protrusion base portion 42, whereby the protrusion top portion 40 is formed in a circular arc cross section that is smooth without becoming an actual corner portion. In addition, the radius of curvature R of the protrusion top portion 40 is 1.5 times or less the length dimension L of the protrusion base portion 42, whereby it is possible to prevent the length dimension in the flow path length direction of the protrusion 34 from becoming excessively long, and it is possible to sufficiently set the inclination angles a, b of the upstream inclined portion 44 and the downstream inclined portion 46 that are continuously smooth with the protrusion top portion 40 to be large.

[0091] The upstream inclined portion 44 can be curved, but in the present embodiment, it can also be formed in a straight line shape. The upper end portion of the upstream inclined portion 44 extends from the end portion on the upstream side of the protrusion top portion 40 in the tangential direction of the protrusion top portion 40, and is continuously smooth without a corner portion with the protrusion top portion 40. The lower end portion of the upstream inclined portion 44 is curved in a circular arc shape, and is continuously smooth without a corner portion with the bottom surface 35 of the cooling flow path 16.

[0092] The upstream inclined portion 44 has an inclination angle a with respect to the bottom surface 35 (bottom surface of the turbulent flow portion 48) of the cooling flow path 16 in a range of 20 to 70°, and is more preferably in a range of 30 to 60°. Further, in the case where the upstream inclined portion 44 is curved, for example, it is possible to grasp the inclination angle a of the upstream inclined portion 44 as an average value of the inclination angles of the upstream inclined portion 44.

[0093] The inclination angle α of the upstream inclined portion 44 is formed to be 20° or more, whereby the flow of the thermal medium from the upstream side of the protrusion 34 is effectively disturbed by the upstream inclined portion 44 formed to have a sufficiently large angle in the flow direction of the thermal medium, and an improvement in cooling performance due to the stirring effect is achieved. In addition, the inclination angle α of the upstream inclined portion 44 is formed to be 70° or less, whereby the flow of the thermal medium can be prevented from being excessively restricted by the protrusion 34.

[0094] The downstream inclined portion 46 can be curved, but is formed to be linear in the present embodiment. The upper end portion of the downstream inclined portion 46 extends from the end portion of the protrusion top portion 40 on the downstream side in the tangential direction of the protrusion top portion 40, and is smoothly continuous with the protrusion top portion 40 without an angle. The lower end portion of the downstream inclined portion 46 is curved in a circular arc shape, and is smoothly continuous with the bottom surface 35 of the cooling flow path 16 without an angle.

[0095] The inclination angle β of the downstream inclined portion 46 with respect to the bottom surface 35 of the cooling flow path 16 is in the range of 20 to 70°, and more preferably in the range of 30 to 60°. In addition, in the case where the downstream inclined portion 46 is curved, for example, the inclination angle β of the downstream inclined portion 46 can be grasped as an average value of the inclination angles of the downstream inclined portion 46.

[0096] The inclination angle β of the downstream inclined portion 46 is formed to be 20° or more, whereby the flow of the thermal medium that passes over the protrusion 34 is easily peeled off from the downstream inclined portion 46, and an effect of making the flow disturbed, such as a vortex, easy to occur on the downstream side of the protrusion 34 can be expected. In addition, the inclination angle β of the downstream inclined portion 46 is formed to be 70° or less, whereby the flow of the thermal medium along the downstream inclined portion 46 is also ensured, and effective stirring of the thermal medium by the confluence of the flow peeled off from the downstream inclined portion 46 is expected.

[0097] A plurality of protrusions 34 formed to have substantially the same shape and size are provided. In the present embodiment, a plurality of protrusions 34 are provided in a predetermined interval in the flow path length direction in one cooling flow path 16. In the present embodiment, the plurality of protrusions 34 provided in one cooling flow path 16 are arranged at substantially constant intervals, but the intervals can vary, for example, the intervals can narrow toward the downstream side, or the intervals narrow toward a portion of the middle in the flow path length direction.

[0098] The protrusion 34 of the present embodiment is provided in the downstream portion (right side portion) of the cooling flow path 16, and is not provided in the upstream portion (left side portion). Therefore, the downstream portion of the cooling flow path 16 is formed as a turbulent flow portion 48 in which the protrusion 34 is provided, and the upstream portion of the cooling flow path 16 is formed as a laminar flow portion 50 in which the protrusion 34 is not provided. As described above, the turbulent flow portion 48 in which the protrusion 34 is provided is formed in the downstream portion of the cooling flow path 16, and the laminar flow portion 50 in which the protrusion 34 is not provided is formed in the upstream portion of the cooling flow path 16. Figure 2As shown, the cooling flow path 16 of the present embodiment is configured such that the flow path length dimension of the turbulent flow portion 48 is larger than the flow path length dimension of the laminar flow portion 50. It is preferable that the flow path length dimension of the turbulent flow portion 48 be within a range of 1.5 times to 5 times, and more preferably within a range of 2 times to 3 times, the flow path length dimension of the laminar flow portion 50. Further, the position of the turbulent flow portion 48 is not necessarily limited to the downstream portion of the cooling flow path 16, and can be provided, for example, at a central portion in the flow path length direction of the cooling flow path 16.

[0099] The laminar flow portion 50 is configured such that the inner wall surface of the lower wall portion formed by the lower plate 14 is an inclined surface 52 that inclines upward from the upstream side toward the downstream side. Thus, the cooling flow path 16 has a flow path cross-sectional area that decreases toward the downstream side in the laminar flow portion 50. On the other hand, the turbulent flow portion 48 is configured such that the flow path cross-sectional area of the portion after the removal of the protrusion 34 is substantially constant in the flow path length direction. The bottom surface of the laminar flow portion 50 is formed as the inclined surface 52, and thus the depth dimension of the inlet-side flow path portion 26 on the upstream side of the laminar flow portion 50 is larger than the depth dimension of the outlet-side flow path portion 30 on the downstream side of the turbulent flow portion 48. Thus, the volume of the inlet-side flow path portion 26 is larger than the volume of the outlet-side flow path portion 30. Further, the portion of the side wall portion of the laminar flow portion 50 of the cooling flow path 16 that constitutes the outer peripheral fixed portion 20 and the partition wall portion 24 gradually decreases in the protrusion height dimension from the bottom surface 35 of the cooling flow path 16 toward the downstream side. In addition, the protrusion height dimension of the portion of the outer peripheral fixed portion 20 that constitutes the wall portion of the inlet-side flow path portion 26 from the bottom surface 35 of the cooling flow path 16 is increased compared to the portion that constitutes the wall portion of the outlet-side flow path portion 30.

[0100] The protrusions 34 are provided in the five cooling flow paths 16, the cooling flow path 16, the cooling flow path 16, the cooling flow path 16, and the cooling flow path 16, respectively. In the present embodiment, the same number of protrusions 34 are provided at substantially the same intervals with respect to the five cooling flow paths 16, the cooling flow path 16, the cooling flow path 16, the cooling flow path 16, and the cooling flow path 16. In addition, in the present embodiment, the positions and ranges in the flow path length direction in which the protrusions 34 are provided in the five cooling flow paths 16, the cooling flow path 16, the cooling flow path 16, the cooling flow path 16, and the cooling flow path 16 are also formed to be substantially the same as each other. Further, for example, depending on the heat generation site of the cooling target, or the like, the formation positions (positions of the turbulent flow portions 48) of the protrusions 34 in the five cooling flow paths 16, the cooling flow path 16, the cooling flow path 16, the cooling flow path 16, and the cooling flow path 16 can be different from each other. In addition, in the five cooling flow paths 16, the cooling flow path 16, the cooling flow path 16, the cooling flow path 16, and the cooling flow path 16, the number, shape, size, interval, or the like of the protrusions 34 can also be different from each other.

[0101] As shown in FIG. 6, the protrusion 34 is provided in the cooling flow path 16 of the present embodiment. The protrusion 34 is provided in the cooling flow path 16 of the present embodiment. The protrusion 34 is provided in the cooling flow path 16 of the present embodiment. The protrusion 34 is provided in the cooling flow path 16 of the present embodiment. The protrusion 34 is provided in the cooling flow path 16 of the present embodiment. Figure 5As shown, a protrusion 34 is provided continuously throughout the width direction of the cooling flow path 16, and its two ends are continuous with the sidewall portion of the cooling flow path 16 formed by the outer peripheral fixed portion 20 or the partition portion 24. That is, the two ends of the protrusion 34 in the width direction are formed as connecting ends 54 that are continuous with the outer peripheral fixed portion 20 or the partition portion 24. Since the protrusion 34 is set from the bottom surface 35 of the cooling flow path 16 to the middle in the depth direction, it can be seen that the protrusion 34 is provided continuously throughout the width direction of the cooling flow path 16 on the bottom surface 35 side in the depth direction of the cooling flow path 16, and the protrusion 34 may have connecting ends 54.

[0102] like Figure 5 As shown, the connecting end 54 is formed as a flow regulating portion 56, which extends along the length of the cooling flow path 16 in a shape that is recessed downward toward the bottom surface 35 of the cooling flow path 16. The bottom (upper surface) of the flow regulating portion 56 is formed by a concave curved surface, and the flow regulating portion 56 is smoothly and continuously connected to the inner sidewall of the cooling flow path 16 without corners. At least a portion of the flow regulating portion 56 in the flow path width direction is located on the side (lower side) of the bottom surface 35 of the cooling flow path 16 closer to the ridge 38 of the protrusion 34. The minimum height dimension h of the flow regulating portion 56 relative to the bottom surface 35 of the cooling flow path 16 is in the range of 0.05 to 0.8 times the height dimension H of the protrusion 34 in the ridge 38, more preferably in the range of 0.1 to 0.5 times. In addition, the width dimension w1 of the flow regulating portion 56 is smaller than the width dimension w2 of the middle portion after removing the flow regulating portion 56 in the protrusion 34. The width dimension w1 of the flow adjustment section 56 is in the range of 1 to 30% relative to the width dimension W of the protrusion 34, and more preferably in the range of 3 to 20%.

[0103] In this embodiment, the flow regulating section 56 is formed such that the inner portion in the flow path width direction slopes downwards linearly towards the outer portion in the flow path width direction, and the outer portion in the flow path width direction is formed into a concave shape recessed towards the bottom surface 35 of the cooling flow path 16. Furthermore, in this embodiment, the end of the flow regulating section 56 on the outer side of the flow path width direction, which is continuous with the sidewall portion of the cooling flow path 16, is located on a side higher than the end on the central side of the flow path width direction. The flow regulating section 56 extends linearly along the length direction of the flow path with a substantially constant cross-sectional shape.

[0104] The inner end of the flow regulating section 56 in the flow path width direction is located inside the corner R that connects the side wall surface of the cooling flow path 16 to the bottom surface 35 in the flow path width direction. In summary, the flow regulating section 56 is configured to extend in the flow path width direction up to the bottom surface 35 of the cooling flow path 16.

[0105] like Figure 3As shown, the cooling heat exchanger 10 formed in such a structure is used in a state where the cooling surface 18 of the upper plate 12 overlaps the battery pack 17 as a cooling target. For example, a plurality of battery packs 17 are arranged in the left-right direction along the flow path length direction of the cooling flow path 16.

[0106] In a state where the battery pack 17 overlaps the cooling surface 18, the low-temperature heat medium supplied from an external flow path not shown to the inlet-side flow path portion 26 flows in the cooling flow path 16, whereby the battery pack 17 is cooled by heat exchange with the upper plate 12 of the battery pack 17 via the heat medium. Further, the heat medium heated by the heat exchange with the battery pack 17 is discharged from the outlet-side flow path portion 30 to the external flow path not shown.

[0107] By the heat exchange with the battery pack 17, the heat medium increases in temperature as it goes downstream. Among them, the portion of the heat medium flowing in the upper portion of the cooling flow path 16 close to the battery pack 17 becomes high-temperature first, but if so, the temperature difference with the heat medium flowing in the upper portion of the cooling flow path 16 of the battery pack 17 becomes small, thereby the cooling performance decreases. Therefore, in the cooling heat exchanger 10, the protrusion 34 is provided in the cooling flow path 16, the heat medium flows over the protrusion 34, whereby the flow of the heat medium is disturbed, and thus the heat medium flowing in the upper portion of the cooling flow path 16 is mixed with the heat medium flowing in the lower portion. Thereby, the temperature of the heat medium flowing in the upper portion of the cooling flow path 16 decreases, and thus the temperature difference between the heat medium flowing in the upper portion and the battery pack 17 becomes large, and thus the heat exchange between the heat medium and the battery pack 17 can be efficiently generated, and thus the battery pack 17 can be more effectively cooled. In summary, not only the heat capacity of the heat medium flowing in the upper portion of the cooling flow path 16 can be utilized, but also the heat capacity of the entire heat medium flowing in the cooling flow path 16 can be utilized to effectively cool the battery pack 17.

[0108] The temperature of the heat medium flowing in the upper portion of the cooling flow path 16 increases as it goes to the downstream side of the cooling flow path 16 by the heat exchange with the battery pack 17, and on the downstream side of the cooling flow path 16, the temperature difference between the upper and lower heat mediums easily becomes large. Therefore, the cooling heat exchanger 10 of the present embodiment is such that the downstream portion of the cooling flow path 16 is formed as a turbulent portion 48 having the protrusion 34. Thereby, in the downstream portion of the cooling flow path 16 where the high-temperature of the upper portion of the heat medium affects the cooling performance, the stirring action of the heat medium by the protrusion 34 is exerted, whereby the temperature difference in the up-down direction in the cooling flow path 16 is reduced or even eliminated, and the high-temperature of the upper portion of the heat medium is suppressed.

[0109] In this embodiment, the cooling heat exchanger 10 has an upstream portion of the cooling flow path 16 formed as a laminar flow section 50 without protrusions 34. This prevents high temperatures in the upper part of the cooling flow path 16 from becoming a problem, suppresses disturbances in the flow of the cooling medium caused by the protrusions 34, and allows the cooling medium to flow smoothly. The bottom surface of the laminar flow section 50 in this embodiment is formed as an inclined surface 52 that slopes relative to the bottom surface of the turbulent flow section 48, and the cross-sectional area of ​​the cooling flow path 16 gradually decreases towards the downstream side in the laminar flow section 50. Therefore, the cooling medium flowing in the laminar flow section 50 becomes less prone to deceleration towards the downstream side, achieving smoother flow of the cooling medium more effectively. As a result, a lower-performance, lower-cost pump can also be used to circulate the cooling medium.

[0110] like Figure 2 As shown, the protrusion 34 is formed in a V-shape with a narrow width when viewed from the upper surface, facing upstream. The hot medium passing through the inclined portions 36 of the protrusion 34 in a direction approximately orthogonal to the ridge line 38 converges with each other on the downstream side of the protrusion 34, thereby sometimes strongly disturbing the flow and forming a vortex flow (vortex), and more effectively stirring the hot medium.

[0111] like Figure 5 As shown, a protrusion 34 is provided continuously throughout the width of the cooling flow path 16, forming a connecting end 54 at both ends and connecting the connecting end 54 to the side wall portion of the cooling flow path 16. This prevents the flow of hot medium that bypasses the protrusion 34 along the width of the flow path, thereby effectively utilizing the stirring effect of the hot medium caused by the passage of the protrusion 34.

[0112] However, the flow resistance of the hot medium flowing at both ends of the cooling flow path 16 increases due to its proximity to the sidewalls of the cooling flow path 16, which can easily cause flow disturbances or stagnation. Therefore, the heat exchanger 10 for cooling has a flow regulating section 56 formed by the connecting ends 54 of the two ends of the protrusion 34, which is recessed downwards. As a result, the flow resistance of the hot medium applied to it by the protrusion 34 is less at the two ends of the protrusion 34 than in the middle part. Therefore, even if the resistance from the sidewalls of the cooling flow path 16 comes into play, the flow of the hot medium will not be excessively hindered by the protrusion 3, thus achieving stable flow of the hot medium in the cooling flow path 16.

[0113] In this embodiment, the flow regulating section 56 is positioned such that its height from the bottom surface 35 is smaller on the outer sides of the connection with the sidewall of the cooling flow path 16 (i.e., in the flow path width direction) than on the central side. Therefore, in the portion closer to the sidewall of the cooling flow path 16, the flow resistance caused by the protrusion 34 is further suppressed, thereby achieving smooth flow of the heat medium.

[0114] The flow regulating portion 56 is such that the minimum height dimension h with respect to the bottom surface 35 of the cooling flow path 16 is in a range of 0.05 to 0.8 times, and more preferably in a range of 0.1 to 0.5 times, the height dimension H of the protrusion 34 in the ridge line 38. The minimum height dimension h of the flow regulating portion 56 is formed to be 0.05 times or more of the height dimension H of the protrusion 34 in the ridge line 38, and the stirring action of the heat medium is effectively exerted also in the heat medium flowing over the flow regulating portion 56. In addition, the minimum height dimension h of the flow regulating portion 56 is formed to be 0.8 times or less of the height dimension H of the protrusion 34 in the ridge line 38, whereby the flow of the heat medium over the flow regulating portion 56 is smoothly generated, and the disturbance, stagnation, or the like of the flow of the heat medium due to excessive flow resistance is effectively suppressed.

[0115] The flow regulating portion 56 is such that the width dimension w1 in the width direction of the cooling flow path 16 is smaller than the width dimension w2 of the intermediate portion after the removal of the flow regulating portion 56 in the protrusion 34. The width dimension w1 of the flow regulating portion 56 is preferably in a range of 1 to 30% with respect to the width dimension W of the protrusion 34, and more preferably in a range of 3 to 20%. Thus, by the flow regulating portion 56 locally provided at a position close to the side wall portion of the cooling flow path 16, the smooth flow of the heat medium in the end portion in the flow path width direction of the cooling flow path 16 is achieved, and the width dimension w2 of the intermediate portion of the protrusion 34 having a large protruding height dimension from the bottom surface 35 is sufficiently ensured, whereby the stirring action of the heat medium due to the protrusion 34 can be effectively obtained.

[0116] Figure 6 A portion of a cooling heat exchanger 70 as a second embodiment of the present application is shown. The cooling heat exchanger 70 has a structure in which protrusions 72 are formed in the cooling flow path 16. In the following description, the same reference numerals are annotated in the drawings for the members and portions that are actually the same as those of the first embodiment, and the description is omitted. In addition, the cooling heat exchanger 70 of the present embodiment is different from the cooling heat exchanger 10 of the first embodiment in the structure of the protrusions 72 described below, and thus the first embodiment can be referred to for the structures of other portions.

[0117] Like the protrusions 34 of the first embodiment, the protrusions 72 of the present embodiment are formed in a V shape when viewed from the upper surface, and are narrow in width in the front-rear direction toward the upstream. As shown in FIG. 6, the protrusions 72 are continuously provided throughout the entire flow path width direction of the cooling flow path 16, and both end portions of the protrusions 72 are formed as connection end portions 74 continuous with the side wall portions of the cooling flow path 16. Figure 6

[0118] ​The connecting end portion 74 of the protrusion 72 is formed as a flow regulating portion 76 that is formed in a shape recessed toward the bottom face 35 of the cooling flow path 16. The flow regulating portion 76 of the present embodiment is such that the end portion on the outer side in the flow path width direction is continuous with the protruding tip end, i.e., the upper end, of the outer peripheral fixed portion 20 and the partition wall portion 24 of the side wall portion (the protrusion 72) Figure 6 of the cooling flow path 16. Thus, the end portion on the outer side in the flow path width direction of the flow regulating portion 76 is located on the upper side than the ridge line 38 of the protrusion 72. Further, the middle portion in the flow path width direction of the flow regulating portion 76 is located on the lower side than the ridge line 38, and the minimum height dimension h' from the bottom face 35 of the cooling flow path 16 is smaller than the height dimension H of the protrusion 72 in the ridge line 38. In addition, the minimum height dimension h' of the flow regulating portion 76 in the protrusion 72 of the present embodiment is larger than the minimum height dimension h of the flow regulating portion 56 in the protrusion 34 of the first embodiment, and the difference with respect to the height dimension H of the protrusion 72 in the ridge line 38 is smaller than that of the first embodiment.

[0119] As with the cooling heat exchanger 10 of the first embodiment, the cooling heat exchanger 70 formed in the structure of the present embodiment as described above is used for cooling of a cooling target such as a battery pack. Also, as with the first embodiment, based on the stirring action of the heat medium and the like caused by the protrusions 72, effective cooling performance can be obtained up to the more downstream side of the cooling flow path 16.

[0120] In the present embodiment, the outer end portion in the flow path width direction of the flow regulating portion 76 is continuous with the upper end of the side wall portion of the cooling flow path 16. Thereby, for example as shown in FIG. 6, in the case where the side wall portion of the cooling flow path 16 is formed in a curved inclined shape, the protrusions 72 are provided over a larger range in the flow path width direction, and thus the stirring action of the heat medium by the protrusions 72 can be more favorably obtained. Figure 6

[0121] Further, when the both end portions (the connecting end portion 74, the connecting end portion 74) in the flow path width direction of the protrusion 72 are continuous with the upper end of the side wall portion of the cooling flow path 16, the height of the connecting end portion 74, the connecting end portion 74 of the protrusion 72 is likely to be higher with respect to the middle portion of the protrusion 72. Thus, the connecting end portion 74, the connecting end portion 74 of the protrusion 72 is provided as the concave flow regulating portion 76, and thereby even when the connecting end portion 74, the connecting end portion 74 of the protrusion 72 are continuous with the upper end of the side wall portion of the cooling flow path 16, it is possible to prevent the connecting end portion 74, the connecting end portion 74 from being excessively high.

[0122] ​The above describes the embodiments of the present application in detail, but the present application is not limited to the specific description. For example, the lower plate is preferably a stamped metal piece, but can also be a mold formed product. The lower plate of the mold formed product is not limited to metal, and can be, for example, a synthetic resin with a heat conductive filler.

[0123] The shape and size of the upper plate and the lower plate when viewed from the surface are not particularly limited, and can be appropriately changed depending on the arrangement space of the cooling heat exchanger ensured in the vehicle.

[0124] In the first embodiment, a structure in which a liquid seal region 22 (cooling flow path 16) is formed between the overlapping surfaces of the mutually independent upper plate 12 and the lower plate 14 is illustrated, but the member constituting the wall portion of such a liquid seal region is not limited to the independent upper plate and the lower plate. Specifically, for example, a liquid seal region (cooling flow path) can be formed inside by closing the opening portions of both axial sides of the cylindrical member with a cover member.

[0125] The number, size (flow path length, flow path width, flow path depth), arrangement, and the like of the cooling flow path can be appropriately changed. The flow path shape of the cooling flow path is not limited to the shape extending in a straight line as in the first embodiment, and can be, for example, a shape extending while bending or refracting in the flow path width direction.

[0126] The protrusion is not necessarily limited to the V-shaped shape, and can be, for example, an inverse V-shaped shape expanding toward the upstream side, a W-shaped or inverse W-shaped shape in which two V-shaped or inverse V-shaped shapes are arranged in the flow path width direction, a zigzag shape in which three V-shaped or inverse V-shaped shapes are arranged in the flow path width direction, an inclined straight line shape inclined in one direction in the flow path width direction toward the upstream side or the downstream side, a non-inclined straight line shape extending in the flow path width direction without being inclined in the flow path length direction, a curved shape such as a semicircular arc shape, or a wave shape extending in the flow path width direction while meandering.

[0127] The cross-sectional shape orthogonal to the ridge line of the protrusion is not limited to the mountain shape having the protrusion top portion 40, the upstream inclined portion 44, and the downstream inclined portion 46 of the small-diameter circular arc shape illustrated in the first embodiment. Specifically, for example, the protrusion top portion can be formed in a circular arc shape with a larger radius of curvature, and can be, for example, a shape in which the upstream end and the downstream end of the protrusion top portion are smoothly connected to the bottom surface of the cooling flow path in a curved surface. In addition, for example, the protrusion top portion can not have a circular arc shape, and the protruding tip end of the protrusion can be formed in a sharp shape in the orthogonal cross section of the ridge line.

[0128] The height dimension of the inclined portion of the protrusion changes at the inner side portion in the flow path width direction after the connection end portion (flow regulating portion) is removed. Specifically, for example, the end portion of the inclined portion of the protrusion in one of the flow path width directions is formed as a low protrusion having a small height dimension from the bottom surface of the cooling flow path, and the end portion of the inclined portion in the other of the flow path width directions is formed as a high protrusion having a large height dimension from the bottom surface of the cooling flow path. In addition, for example, a central low protrusion having a height dimension from the bottom surface of the cooling flow path that decreases on the central side in the flow path width direction and a central high protrusion having a height dimension from the bottom surface of the cooling flow path that increases on the central side in the flow path width direction can be alternately arranged in the flow path length direction, whereby effective stirring of the heat medium can be expected.

[0129] The height dimension of the plurality of protrusions arranged in the flow path length direction of the cooling flow path can change. Specifically, for example, the height dimension of the plurality of protrusions arranged in the flow path length direction of the cooling flow path can gradually increase toward the downstream side of the cooling flow path. Thereby, in the turbulent flow portion in which the protrusions are formed, the stirring action of the heat medium based on the protrusions can be more strongly obtained toward the downstream side. In addition, for example, the height dimension of the plurality of protrusions arranged in the flow path length direction of the cooling flow path can gradually increase toward the central side of the cooling flow path, whereby the central side of the cooling flow path in the flow path length direction, which is a cooling target that is high in temperature, can be effectively cooled. In addition, in a case where a plurality of cooling flow paths are arranged and provided, the number of protrusions can be set to be larger with respect to the cooling flow path located at the center in the flow path width direction than the cooling flow paths located at both ends in the flow path width direction. Thereby, the difference between the cooling flow path located at the center in the flow path width direction, for which cooling due to external air is difficult to expect, and the cooling flow paths located at both ends in the flow path width direction, for which cooling due to external air can be expected, can be reduced.

[0130] The interval of adjacent protrusions of the plurality of protrusions arranged in the flow path length direction of the cooling flow path can change in the flow path length direction. If the interval of adjacent protrusions is set to be narrow in the flow path length direction of the cooling flow path, the flow of the heat medium is more easily disturbed, and thus improvement in cooling performance due to stirring of the heat medium is achieved. In addition, if the interval of adjacent protrusions is set to be wide in the flow path length direction of the cooling flow path, the heat medium can flow smoothly.

[0131] The flow regulating portion of the protrusion can be formed in a shape that is recessed toward the bottom surface of the cooling flow path, and the upper surface (bottom portion) does not necessarily have to be formed in a curved shape. That is, the upper surface of the flow regulating portion can be a straight line shape, for example, the upper surface of the flow regulating portion can be formed in a V-shaped shape when viewed in the flow path length direction, and can be formed in a planar shape that extends substantially orthogonal to the up-down direction.

[0132] For example, the upper surface of the upper plate and the lower surface of the lower plate are formed as cooling surfaces, and the structure of the present application can be used in a cooling heat exchanger having a double-sided cooling structure in which inner fins are arranged between the opposing surfaces of the upper plate and the lower plate to divide the liquid seal region into two vertically. In the cooling heat exchanger having the double-sided cooling structure, the protrusions having the flow adjusting portions are formed on the inner fins in the case where the inner fins constitute the bottom wall portion and the side wall portion of the cooling flow path.

Claims

1. A cooling heat exchanger (10, 70) in which a cooling flow path (16) in which a cooling medium flows is formed inside, and a cooling object (17) overlapping a cooling surface (18) is cooled, wherein a protrusion (34, 72) that disturbs the flow of the cooling medium is provided protruding from a bottom surface (35) of the cooling flow path (16), the protrusion (34, 72) extends over the entire flow path width of the cooling flow path (16), both end portions of the protrusion (34, 72) are formed as connecting end portions (54, 74) that are continuous with side wall portions of the cooling flow path (16), respectively, the connecting end portions (54, 74) of the protrusion (34, 72) are formed as flow adjusting portions (56, 76) that extend in the flow path length direction of the cooling flow path (16) in a shape that is recessed toward the bottom surface (35) side.

2. The cooling heat exchanger (10, 70) according to claim 1, wherein a bottom portion of the flow adjusting portion (56, 76) that is formed in a concave shape is formed as a curved surface.

3. The cooling heat exchanger (70) according to claim 1 or 2, wherein a bottom portion of the flow adjusting portion (76) is directly continuous with a protruding front end of the side wall portion that protrudes from the bottom surface (35) of the cooling flow path (16).

4. The cooling heat exchanger (10, 70) according to claim 1 or 2, wherein the protrusion (34, 72) extends in the flow path width direction of the cooling flow path (16) while being inclined in the flow path length direction of the cooling flow path (16).

5. The cooling heat exchanger (10, 70) according to claim 4, wherein the protrusion (34, 72) extends obliquely toward either one of the upstream side and the downstream side of the cooling flow path (16) toward both sides in the flow path width direction of the cooling flow path (16).

6. The cooling heat exchanger (10, 70) according to claim 5, wherein the protrusion (34, 72) is formed in a V shape that extends obliquely toward the downstream side of the cooling flow path (16) toward both sides in the flow path width direction of the cooling flow path (16).

7. The cooling heat exchanger (10, 70) according to claim 1 or 2, wherein a width dimension (w1) of the flow adjusting portion (56, 76) in the flow path width direction of the cooling flow path (16) is in a range of 1 to 30% with respect to a width dimension (W) of the protrusion (34, 72) in the flow path width direction of the cooling flow path (16). ​

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