Cooling heat exchanger

Abstract

The utility model provides a heat exchanger for cooling. The heat exchanger for cooling has a novel structure and can more efficiently exert cooling performance. In a cooling heat exchanger (10) in which a cooling flow path (36) through which a cooling heat medium flows is formed, and which cools an object to be cooled (52) that overlaps a cooling surface (16), the cooling flow path (36) is provided with a parallel flow path section (38) comprising a plurality of flow path sections (40) that extend adjacent to each other and in parallel, the flow direction of the heat medium in the plurality of flow path sections (40) being the same, and the flow direction of the heat medium in the plurality of flow path sections (40) being the same as the flow direction of the heat medium in the plurality of flow path sections (40) being the same as the flow direction of the heat medium in the plurality of flow path sections (40). A plurality of protrusions (42) for disturbing the flow of the heat medium are formed in the parallel flow path section (38), and regions in which the effects of disturbing the flow of the heat medium generated by the protrusions (42) differ from each other are set in the parallel flow path section (38).

Description

TECHNICAL FIELD

[0001] The present utility model relates to a cooling heat exchanger used in cooling of a cooling object such as a battery used in an electric vehicle or the like. BACKGROUND

[0002] For example, in an electric vehicle such as an electric automobile or a hybrid automobile, a battery or the like as a cooling object has a large amount of heat generation due to miniaturization and high performance, and the importance of cooling performance increases. In the past, for example, as disclosed in U.S. Patent No. 10,355,331 (Patent Document 1), a cooling heat exchanger having a cooling flow path in which a cooling medium flows inside has been proposed. A cooling surface of the cooling heat exchanger overlaps with the cooling object such as a battery, and the cooling surface is cooled by the cooling medium flowing in the cooling flow path, whereby the cooling object is cooled.

[0003] PRIOR ART DOCUMENTS

[0004] PATENT DOCUMENTS

[0005] Patent Document 1: U.S. Patent No. 10,355,331 SUMMARY

[0006] PROBLEMS TO BE SOLVED BY THE INVENTION

[0007] Incidentally, as shown in FIG. 1 of Patent Document 1, the cooling flow path has a parallel flow path portion composed of a plurality of flow path portions extending in parallel and in which the cooling medium flows in the same direction as each other. By providing such a parallel flow path portion, partial widening of the cooling flow path corresponding to the width dimension of the cooling object can be achieved, and the flow of the cooling medium can be prevented from becoming uncontrollable at the widened portion. Figure 1

[0008] However, such a parallel flow path portion is provided, for example, at a portion directly contributing to heat exchange with the cooling object, and thus there is a problem that the temperature of the cooling medium easily varies depending on the temperature distribution of the cooling object, the position in the flow direction of the cooling medium, and the like, and the cooling performance becomes uneven.

[0009] In addition, the cooling medium flowing near the cooling object easily becomes hot due to heat exchange with the cooling object, and the cooling medium flowing away from the cooling object has difficulty in temperature rise due to heat exchange with the cooling object, and thus a temperature distribution corresponding to the distance from the cooling object easily occurs in the flow path cross section. As a result, it is also known that there is a problem that the cooling performance possessed by the entire amount of the cooling medium flowing in the parallel flow path portion cannot be utilized for cooling of the cooling object.

[0010] ​The utility model discloses a cooling heat exchanger with a novel structure that can more efficiently exert cooling performance in a cooling heat exchanger with parallel flow path portions.

[0011] Means for solving the problem

[0012] Hereinafter, preferred modes for mastering the utility model will be described, but each mode described below is described exemplarily, and can be adopted by being appropriately combined with each other, and as for the plurality of constituent elements described in each mode, can be recognized and adopted as independently as possible, and can be adopted by being appropriately combined with any constituent element described in other mode. Thus, in the utility model, it is not limited to the mode described below, and various other modes can be realized.

[0013] The first mode is a cooling heat exchanger, in which a cooling flow path for flowing a cooling medium is formed inside, and a cooling object overlapping a cooling surface is cooled, wherein the cooling flow path is provided with a parallel flow path portion, the parallel flow path portion is composed of a plurality of flow path portions extending adjacent to and in parallel to each other, the flow direction of the cooling medium in the plurality of flow path portions is the same, a plurality of protrusions disturbing the flow of the cooling medium are formed in the parallel flow path portion, and regions in which the effect of disturbing the flow of the cooling medium generated by the protrusions are different from each other are set in the parallel flow path portion.

[0014] According to the cooling heat exchanger formed in accordance with the structure of the present mode, by forming the protrusions in the parallel flow path portion, the cooling medium flowing in the parallel flow path portion is stirred by the protrusions, and the cooling medium is formed to have substantially the same temperature in the flow path cross section. Therefore, it is possible to prevent only a part of the cooling medium flowing near the cooling object from being heated to sharply and excessively reduce the heat exchange efficiency, thereby realizing the improvement of the cooling performance.

[0015] In addition, according to the different formation modes of the arrangement, formation number, formation density, shape, size, etc. of the protrusions, regions in which the effect of disturbing the flow of the cooling medium is different are set. Thus, for example, in a region in which the temperature rise of the cooling medium caused by heat exchange with the cooling object is large, the flow of the cooling medium is strongly disturbed by the protrusions, thereby realizing the uniformization of the temperature of the cooling medium, and in a region in which the temperature rise of the cooling medium is small and the stirring of the cooling medium is not required, by suppressing the effect of disturbing the flow of the cooling medium generated by the protrusions, the cooling medium can flow smoothly. It should be noted that in the case where three or more regions are set as regions exerting the effect of disturbing the flow of the cooling medium generated by the protrusions, at least one region can be different from the other regions in the effect of disturbing the flow of the cooling medium generated by the protrusions, and it is not necessary to make the effect of disturbing the flow of the cooling medium generated by the protrusions different among all regions.

[0016] The second method is based on the cooling heat exchanger described in the first method, and the regions in which the effects of disturbing the flow of the heat medium are different from each other are provided at different positions in the flow direction of the heat medium in at least one of the flow path portions constituting the parallel flow path portion.

[0017] According to the cooling heat exchanger formed in accordance with the present method, the effects of disturbing the flow of the heat medium generated by the protrusions are promoted in the flow direction of the heat medium, and thus, for example, in a portion in which the temperature difference of the heat medium between a position close to the cooling object and a position far from the cooling object in the parallel flow path portion easily becomes large, a region in which the effects of promoting the turbulence are strong is provided, whereby the temperature difference in the flow direction of the heat medium can be reduced.

[0018] In addition, in a portion in which the temperature difference of the heat medium between a position close to the cooling object and a position far from the cooling object in the parallel flow path portion easily becomes small, a region in which the disturbing of the flow of the heat medium generated by the protrusions is suppressed is provided, whereby smooth flow of the heat medium is achieved.

[0019] The third method is based on the cooling heat exchanger described in the second method, and the regions in which the effects of disturbing the flow of the heat medium are different from each other and are provided at different positions in the flow direction of the heat medium in the parallel flow path portion are provided such that the farther the region is on the downstream side, the stronger the effects of disturbing the flow of the heat medium generated by the protrusions.

[0020] According to the cooling heat exchanger formed in accordance with the present method, the effects of disturbing the flow of the heat medium generated by the protrusions are provided to be stronger on the downstream side than on the upstream side, and thus, in a region on the downstream side of the parallel flow path portion in which the temperature difference between the heat medium flowing at a position close to the cooling object and the heat medium flowing at a position far from the cooling object easily becomes large due to heat exchange with the cooling object, uniformization of the temperature is achieved by the stirring effects generated by the disturbing of the flow of the heat medium.

[0021] The fourth method is based on the cooling heat exchanger described in any one of the first to third methods, and the protrusions are provided throughout the flow path width of the flow path portions constituting the parallel flow path portion, and a narrow flow path portion through which the heat medium flows is provided on the protruding tip side of the protrusions.

[0022] According to the cooling heat exchanger formed in accordance with the present method, the heat medium flows over the protrusions and in the narrow flow path portion, and the effects of disturbing the flow of the heat medium generated by the protrusions are effectively exerted. In particular, when the heat medium flows over the protrusions, a vortex-like flow is easily generated in the heat medium, and thus, for example, in the case where a temperature difference of the heat medium is generated in the protruding direction of the protrusions, uniformization of the temperature of the heat medium is effectively achieved by the vortex-like flow.

[0023] Further, the flow path cross-sectional area of the flow path portion is locally reduced in the narrow flow path portion, whereby the flow rate is increased when the heat medium flows through the narrow flow path portion, and the effect of disturbing the flow of the heat medium can be more effectively obtained.

[0024] The fifth aspect is the cooling heat exchanger according to the fourth aspect, wherein the plurality of protrusions form a plurality of the narrow flow path portions, and the flow path cross-sectional area of at least one of the narrow flow path portions is different from the flow path cross-sectional area of the other narrow flow path portions.

[0025] According to the cooling heat exchanger formed in accordance with the present aspect, the flow rate of the heat medium flowing through the narrow flow path portion can be adjusted based on the difference in the flow path cross-sectional area of the narrow flow path portion. Therefore, for example, by locally reducing the flow path cross-sectional area of the narrow flow path portion to increase the flow rate, the effect of disturbing the flow of the heat medium by the protrusion can be more greatly obtained.

[0026] The sixth aspect is the cooling heat exchanger according to the fifth aspect, wherein the flow path cross-sectional area of the plurality of narrow flow path portions provided in one of the flow path portions is reduced from the upstream side toward the downstream side of the flow path portion.

[0027] According to the cooling heat exchanger formed in accordance with the present aspect, the effect of disturbing the flow of the heat medium by the heat medium after passing through the narrow flow path portion is effectively exerted on the downstream side.

[0028] The seventh aspect is the cooling heat exchanger according to the fifth aspect or the sixth aspect, wherein the protrusion has a ridge line extending obliquely with respect to the flow path length direction of the flow path portion.

[0029] The heat medium flowing in the flow path portion passes over the protrusion in a direction substantially orthogonal to the ridge line of the protrusion, and therefore, according to the cooling heat exchanger of the present aspect in which the ridge line of the protrusion extends obliquely with respect to the flow direction of the heat medium in the flow path portion, i.e., the flow path length direction of the flow path portion, 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 of the flow path portion. As a result, the heat medium after passing over the protrusion easily generates a change in the flow direction, and the disturbance of the flow of the heat medium can be more effectively generated.

[0030] The eighth aspect is the cooling heat exchanger according to any one of the first aspect to the seventh aspect, wherein the protrusion is locally provided with respect to the parallel flow path portions, and the region in which the protrusion is formed and the region in which the protrusion is not formed constitute the regions in which the effects of disturbing the flow of the heat medium are different from each other.

[0031] According to the cooling heat exchanger formed in the structure according to the present mode, by setting regions in which the effects of disturbing the flow of the heat medium differ from each other depending on the presence or absence of the protrusions, it is possible to further increase the difference in the effects of disturbing the flow of the heat medium. Therefore, it is possible to effectively set regions in which the flow of the heat medium is disturbed to achieve a reduction in temperature unevenness and regions in which the flow of the heat medium is smooth, respectively.

[0032] The ninth mode is based on the cooling heat exchanger of any one of the first mode to the eighth mode, the cooling heat exchanger is provided with a stacked structure in which a cooling surface constituting member constituting the cooling surface and a flow path member provided with a groove overlap each other, the groove of the flow path member is covered by the cooling surface constituting member to constitute the cooling flow path, and the plurality of protrusions protrude from the flow path member toward the cooling surface constituting member side.

[0033] According to the cooling heat exchanger formed in the structure according to the present mode, for example, it is possible to easily form protrusions that protrude toward the flow path portions of the parallel flow path portions. In particular, since the cooling surface constituting member provided with the cooling surface and the flow path member provided with the protrusions are provided in a structure in which they are provided as separate members and overlap each other, for example, it is possible to form the cooling surface constituting member from a material having a high heat transfer coefficient, and to form the flow path member from a material having excellent formability of the groove and the protrusions, and the like.

[0034] The tenth mode is based on the cooling heat exchanger of any one of the first mode to the ninth mode, and the regions in which the effects of disturbing the flow of the heat medium differ from each other are set in at least one group of adjacent flow path portions in the parallel flow path portions.

[0035] According to the cooling heat exchanger formed in the structure according to the present mode, for example, in the case where there is a difference in the amount of heat generation locally with respect to the cooling object arranged in a stacked manner with respect to the parallel flow path portions, the disturbance of the flow of the heat medium caused by the protrusions is set to be stronger at a portion of the cooling object where the amount of heat generation is large, and the disturbance of the flow of the heat medium caused by the protrusions is set to be weaker at a portion of the cooling object where the amount of heat generation is small, whereby it is possible to achieve stabilization of the cooling performance.

[0036] The eleventh mode is based on the cooling heat exchanger of any one of the first mode to the tenth mode, and the cooling object is a battery.

[0037] According to the cooling heat exchanger formed in the structure according to the present mode, for example, in the case of cooling a battery in which local temperature rise is likely to occur at the output terminal portion or the like, regions in which the effects of disturbing the flow of the heat medium differ from each other due to the heat generation mode of the battery are set, whereby it is possible to achieve efficient cooling.

[0038] The twelfth aspect is the cooling heat exchanger according to any one of the first to eleventh aspects, wherein the regions in which the effects of disturbing the flow of the heat medium are different from each other are set by differences in the intervals of the plurality of protrusions in the flow direction of the heat medium.

[0039] According to the cooling heat exchanger formed in the structure according to the present aspect, for example, a region in which the effect of disturbing the flow of the heat medium (turbulence promotion effect) is strong can be set by narrowing the intervals of the protrusions, and a region in which the turbulence promotion effect is weak can be set by widening the intervals of the protrusions. In this way, regions in which the effects of disturbing the flow of the heat medium are different from each other due to the differences in the intervals of the protrusions can be easily set.

[0040] The thirteenth aspect is the cooling heat exchanger according to any one of the first to twelfth aspects, wherein the regions in which the effects of disturbing the flow of the heat medium are different from each other are set by differences in the heights of the plurality of protrusions.

[0041] According to the cooling heat exchanger formed in the structure according to the present aspect, for example, a region in which the effect of disturbing the flow of the heat medium (turbulence promotion effect) is strong can be set by locally increasing the heights of the protrusions, and a region in which the turbulence promotion effect is weak can be set by locally decreasing the heights of the protrusions. In this way, regions in which the effects of disturbing the flow of the heat medium are different from each other due to the differences in the heights of the protrusions can be easily set.

[0042] The fourteenth aspect is a cooling effect adjustment method in a cooling heat exchanger that includes a cooling flow path inside which a heat medium for cooling flows, the cooling flow path including a plurality of flow path portions that extend adjacent to each other and in the same direction of flow of the heat medium, and a cooling surface on which a cooling target overlaps, in which a specific region in which the flow of the heat medium is disturbed is set in a different manner from other regions by changing the cross-sectional shape of the flow path portions in the plurality of flow path portions, and thereby adjusting the cooling efficiency based on the heat medium in the specific region.

[0043] According to the cooling effect adjustment method in the cooling heat exchanger formed in the structure according to the present aspect, the advantages brought about by the plurality of flow path portions, such as an improvement in cooling performance due to a substantial widening of the cooling flow path, an improvement in controllability of the flow of the heat medium, and the like, can be enjoyed, and adjustment of the cooling efficiency of each region can be easily achieved in the wide cooling surface realized by the plurality of flow path portions. For example, by disposing the specific region in which the cooling efficiency based on the heat medium is adjusted at a position corresponding to a portion of the cooling target in which the amount of heat generation is large, the cooling target can be effectively and efficiently cooled in a wide range.

[0044] The fifteenth aspect is the cooling heat exchanger according to any one of the first to thirteenth aspects, wherein the plurality of protrusions are arranged in the plurality of flow path portions of the parallel flow path portion in a flow direction of the heat medium, a side surface of an upstream side of the protrusion is formed as a first inclined surface on which a protruding height of the protrusion increases from the upstream side toward a downstream side, and a side surface of a downstream side of the protrusion is formed as a second inclined surface on which the protruding height of the protrusion decreases from the upstream side toward the downstream side.

[0045] According to the cooling heat exchanger formed in accordance with the present aspect, by forming the side surface of the upstream side of the protrusion as the first inclined surface, the heat medium is guided along the first inclined surface, and the heat medium easily flows over the protrusion. The heat medium flowing over the protrusion easily generates a vortex-like flow on the second inclined surface, and thus the heat medium is stirred, and the temperature difference of the heat medium decreases. As a result, the heat medium flowing only near the cooling object is prevented from becoming excessively high in temperature, the temperature difference of the cooling object and the heat medium flowing near the cooling object is ensured, and thus an improvement in cooling performance is achieved.

[0046] In addition, the flow path cross-sectional area of the flow path portion decreases toward the downstream side, and thus the flow rate of the heat medium flowing on the first inclined surface increases as it tends toward the downstream side. Therefore, the heat medium flowing on the second inclined surface at a large flow rate on the downstream side of the first inclined surface more effectively generates a vortex-like flow, and more favorably achieves uniformization of the temperature based on stirring of the heat medium.

[0047] The sixteenth aspect is the cooling heat exchanger according to the fifteenth aspect, wherein an inclination angle of the first inclined surface is smaller than an inclination angle of the second inclined surface.

[0048] According to the cooling heat exchanger formed in accordance with the present aspect, the heat medium easily flows along the first inclined surface having a small inclination angle, and the flow of the heat medium over the protrusion is favorably generated with less pressure loss. In addition, by making the inclination angle of the second inclined surface larger than that of the first inclined surface, the formation of the longitudinal vortex flow generated by the heat medium after passing over the protrusion is less likely to be hindered by the second inclined surface, and the stirring action of the heat medium by the longitudinal vortex flow is favorably obtained.

[0049] The seventeenth aspect is the cooling heat exchanger according to any one of the first to sixteenth aspects, wherein the protrusion has a ridge line extending obliquely with respect to a flow path length direction of the flow path portion.

[0050] According to the cooling heat exchanger formed in accordance with the structure of the present embodiment, the heat medium flowing in the flow path portion passes over the ridge line of the protrusion in a direction substantially orthogonal to the ridge line, and therefore, according to the cooling heat exchanger of the present embodiment in which the ridge line of the protrusion extends obliquely with respect to the flow direction of the heat medium in the flow path portion, that is, the flow path length direction of the flow path portion, the flow direction of the heat medium when passing over the protrusion easily becomes an oblique direction with respect to the flow path length direction of the flow path portion. As a result, the heat medium after passing over the protrusion easily changes the direction of flow, and the disturbance of the flow of the heat medium can be more effectively generated.

[0051] The eighteenth mode is based on the cooling heat exchanger described in the seventeenth mode, and the protrusion extends in a V shape obliquely toward both sides in the flow path width direction of the flow path portion.

[0052] According to the cooling heat exchanger formed in accordance with the structure of the present embodiment, since the protrusion has ridge lines having different oblique directions on both sides in the flow path width direction, the heat medium is effectively stirred by the flow passing over each ridge line, and the improvement of the cooling performance based on the stirring effect can be more favorably achieved. In particular, if the protrusion is formed in a V shape obliquely toward both sides in the flow path width direction toward the downstream side, the flow of the heat medium after passing over each ridge line of the protrusion flows into the inner side in the flow path width direction, respectively, and converges on the downstream side of the protrusion, and therefore, the generation of a vortex-like flow can also be expected, and the further improvement of the stirring effect can be achieved.

[0053] The nineteenth mode is based on the cooling heat exchanger described in any one of the first mode to the eighteenth mode, and the protrusion is provided only in the central portion in the flow path length direction of the flow path portion.

[0054] According to the cooling heat exchanger formed in accordance with the structure of the present embodiment, in the case where the heat generating portion of the cooling target is located in the central portion in the flow path length direction, the heat generating portion can be effectively cooled by the local improvement of the cooling performance by the protrusion provided only in the central portion in the flow path length direction. In addition, the central portion in the flow path length direction of the flow path portion is located away from the outside air with respect to both end portions in the flow path length direction, and therefore, it is difficult to expect cooling of the heat medium by heat exchange with the outside air, but the cooling performance can be effectively exerted by the stirring effect of the heat medium generated by the protrusion even in such a central portion.

[0055] The twentieth mode is based on the cooling heat exchanger described in any one of the first mode to the nineteenth mode, and the protrusion is provided only in the flow path portion constituting the central portion in the flow path width direction of the parallel flow path portion.

[0056] According to the cooling heat exchanger formed in the structure according to the present mode, in the case where the heat generating portion of the cooling object is located in the central portion in the flow path width direction, the heat generating portion can be effectively cooled by the local improvement of the cooling performance caused by the protrusions provided only in the central portion in the flow path width direction. In addition, the central portion in the flow path width direction in the flow path portion is located away from the outside air with respect to the both end portions in the flow path width direction, and thus it is difficult to expect cooling of the heat medium by heat exchange with the outside air, but the cooling performance can be effectively exerted by the stirring action of the heat medium caused by the protrusions even in such a central portion.

[0057] The twenty-first mode is based on the cooling heat exchanger according to any one of the first mode to the twentieth mode, and the plurality of protrusions are arranged in the flow path length direction of the flow path portion, and the interval of the protrusions located in the central portion in the flow path length direction of the flow path portion is smaller than the interval of the protrusions located in the both side portions in the flow path length direction of the flow path portion.

[0058] According to the cooling heat exchanger formed in the structure according to the present mode, in the flow path portion in which the plurality of protrusions arranged in the flow path length direction are provided, by narrowing the interval of the adjacent protrusions toward the center of the portion in which the plurality of protrusions are provided, the effect of improving the cooling performance based on the stirring action of the heat medium caused by the protrusions can be more favorably exerted as it tends toward the center of the portion in which the plurality of protrusions are provided.

[0059] The twenty-second mode is based on the cooling heat exchanger according to any one of the first mode to the twenty-first mode, and the width dimension of the protrusions in the flow path width direction of the flow path portion is 50% or more with respect to the flow path width dimension of the flow path portion.

[0060] According to the cooling heat exchanger formed in the structure according to the present mode, by making the width dimension of the protrusions sufficiently large with respect to the flow path width dimension of the flow path portion, the flow around the protrusions is limited, and the flow over the protrusions is easily generated. Thus, the stirring action of the heat medium caused by the protrusions is effectively exerted, and the improvement of the cooling performance is achieved by providing the protrusions.

[0061] The twenty-third mode is based on the cooling heat exchanger according to any one of the first mode to the twenty-second mode, and the flow path width dimension of the flow path portion is in the range of 0.3 to 30 times the width dimension of the partition wall portion that separates the adjacent flow path portions.

[0062] According to the cooling heat exchanger formed in the structure according to the present mode, by setting the flow path width dimension of the flow path portion to be 0.3 times or more of the width dimension of the partition wall portion, the flow path portion formed with a large area in the parallel flow path portions can efficiently cool the cooling surface, and an improvement in cooling performance can be achieved. Further, by setting the flow path width dimension of the flow path portion to be 30 times or less of the width dimension of the partition wall portion, the width dimension of the partition wall portion can be sufficiently ensured, the rigidity of the cooling heat exchanger against deformation can be improved, and the stabilization of the shape of the flow path portion can be achieved. Further, in the case where the cooling heat exchanger is, for example, a structure in which a member provided with a partition wall portion and a member provided with a cooling surface are fixed to each other with the members overlapping each other, by ensuring the width dimension of the partition wall portion, the fixed area of the two members can be made large, and peeling of the two members due to hydraulic pressure of the heat medium or the like can be less likely to occur.

[0063] The twenty-fourth mode is based on the cooling heat exchanger of any one of the first mode to the twenty-third mode, and a protrusion height dimension of the protrusion is within a range of 0.1 to 1.3 times a width dimension of the protrusion.

[0064] According to the cooling heat exchanger formed in the structure according to the present mode, by setting the protrusion height dimension of the protrusion to be 0.1 times or more of the width dimension of the protrusion, the stirring action on the heat medium generated by the flow over the protrusion can be effectively obtained. Further, by setting the protrusion height dimension of the protrusion to be 1.3 times or less of the width dimension of the protrusion, the flow of the heat medium in the flow path portion is prevented from being excessively restricted by the protrusion, and smooth flow of the heat medium can be achieved.

[0065] The twenty-fifth mode is based on the cooling heat exchanger of any one of the first mode to the twenty-fourth mode, and a laminar flow portion in which the flow path portion is not provided with the protrusion is provided in the flow path portion, and a flow path cross-sectional area of the flow path portion in the laminar flow portion decreases toward a downstream.

[0066] According to the cooling heat exchanger formed in the structure according to the present mode, in the laminar flow portion in which the protrusion is not provided, smooth flow of the heat medium can be achieved. Further, in the laminar flow portion, the flow path cross-sectional area of the flow path portion decreases toward the downstream, and thus a decrease in flow velocity on the downstream side is suppressed.

[0067] The twenty-sixth mode is based on the cooling heat exchanger of the twenty-fifth mode, and a flow path length of the laminar flow portion is shorter than a flow path length of a turbulent flow portion in which the protrusion is formed in a portion deviating from the laminar flow portion.

[0068] According to the cooling heat exchanger formed in the structure according to the present mode, the protrusion is formed in a larger range in the flow path length direction in the flow path portion, and an improvement in cooling performance due to the protrusion can be achieved.

[0069] The twenty-seventh aspect is the cooling heat exchanger according to the twenty-fifth or twenty-sixth aspect, wherein a portion of the flow path portion deviated from the laminar flow portion is formed with a turbulent flow portion having the protrusion, and a portion other than the protrusion in the turbulent flow portion is formed to have a constant cross section.

[0070] According to the cooling heat exchanger formed in accordance with the present aspect, the portion other than the protrusion in the turbulent flow portion is formed to have a constant cross section, and variation in flow velocity at the portion of the turbulent flow portion deviated from the protrusion is suppressed, and so forth, and thus, for example, the stirring action by the protrusion is easily controlled by the height, shape, arrangement pitch, and so forth of the protrusion.

[0071] The twenty-eighth aspect is the cooling heat exchanger according to any one of the first to twenty-seventh aspects, wherein an inlet-side flow path portion is provided on an upstream side of the parallel flow path portion, the plurality of flow path portions branch from the inlet-side flow path portion and extend toward a downstream side, and an outlet-side flow path portion in which the plurality of flow path portions converge is provided on a downstream side of the parallel flow path portion, and a volume of the inlet-side flow path portion is larger than a volume of the outlet-side flow path portion.

[0072] According to the cooling heat exchanger formed in accordance with the present aspect, the volume of the inlet-side flow path portion on the upstream side of the cooling flow path is larger than the volume of the outlet-side flow path portion on the downstream side, and thus, for example, the flow path cross-sectional area of the flow path portion constituting the parallel flow path portion connecting the inlet-side flow path portion and the outlet-side flow path portion is made smaller toward the downstream side, and the reduction in flow velocity of the heat medium on the downstream side of the flow path portion is also suppressed.

[0073] The twenty-ninth aspect is the cooling heat exchanger according to the thirteenth aspect, wherein the heights of the plurality of protrusions arranged in the flow path length direction in the flow path portion are made higher toward the downstream side, and thus, the regions in which the actions of disturbing the flow of the heat medium are different from each other are set in the flow path length direction of the flow path portion.

[0074] According to the cooling heat exchanger formed in accordance with the present aspect, by making the protrusion heights of the protrusions higher toward the downstream side, the action of disturbing the flow of the heat medium by the protrusions can be more strongly exerted on the downstream side. Thus, on the downstream side in which the temperature is easily made high due to heat exchange with the cooling target, the effect of improvement in cooling performance by the protrusions can be more favorably obtained.

[0075] The thirtieth aspect is the cooling heat exchanger according to the twenty-ninth aspect, wherein the intervals of the plurality of protrusions arranged in the flow path length direction in the flow path portion are made narrower toward the downstream side, and thus, the regions in which the actions of disturbing the flow of the heat medium are different from each other are set in the flow path length direction of the flow path portion.

[0076] According to the cooling heat exchanger formed in the structure according to the present mode, the height of the protrusions becomes higher toward the downstream side and the interval (pitch) between the protrusions becomes narrower, whereby the stirring action of disturbing the flow of the heat medium by the protrusions is more strongly exerted toward the downstream side. Therefore, according to the present mode, the improvement (maintenance) of the cooling performance on the downstream side can be more effectively achieved.

[0077] The thirty-first mode is based on the cooling heat exchanger described in the twelfth mode, and the interval of the plurality of protrusions arranged in the flow path length direction in the flow path portion becomes narrower toward the downstream, whereby the regions in which the actions of disturbing the flow of the heat medium are different from each other are set in the flow path length direction of the flow path portion.

[0078] According to the cooling heat exchanger formed in the structure according to the present mode, by making the interval between the protrusions arranged in the flow path length direction narrower toward the downstream, the action of disturbing the flow of the heat medium by the protrusions can be more strongly exerted on the downstream side. Thereby, on the downstream side which is likely to become high temperature due to heat exchange with the cooling object, the improvement effect of the cooling performance by the protrusions can be more favorably obtained.

[0079] The thirty-second mode is based on the cooling heat exchanger described in any one of the first mode to the thirty-first mode, the protrusion height of the protrusion varies in the flow path width direction of the flow path portion, either one of a low protrusion portion in which the protrusion height is low and a high protrusion portion in which the protrusion height is high is located at a central portion in the flow path width direction of the protrusion, and the other one of the low protrusion portion and the high protrusion portion is located at both end portions in the flow path width direction of the protrusion.

[0080] According to the cooling heat exchanger formed in the structure according to the present mode, the flow of the heat medium flowing over the central portion in the flow path width direction of the protrusion and the flow of the heat medium flowing over both end portions in the flow path width direction of the protrusion can be made different in the stirring action, the flow rate, and the like. Therefore, the influence of the protrusion on the cooling performance can be made different between the central portion and the both end portions in the flow path width direction, and the cooling performance can be adjusted in the flow path width direction.

[0081] The thirty-third mode is based on the cooling heat exchanger described in the thirty-second mode, and a plurality of the protrusions are arranged in the flow path length direction of the flow path portion, the plurality of the protrusions are configured by alternately arranging first protrusions and second protrusions in the flow path length direction of the flow path portion, the first protrusions are provided with the low protrusion portion at the central portion in the flow path width direction of the flow path portion and with the high protrusion portion at both end portions, and the second protrusions are provided with the high protrusion portion at the central portion in the flow path width direction of the flow path portion and with the low protrusion portion at both end portions.

[0082] According to the cooling heat exchanger formed in the structure according to the present mode, the first protrusions having the low protrusions provided at the central portions in the flow width direction and the second protrusions having the low protrusions provided at the both end portions in the flow width direction are alternately arranged in the flow length direction, whereby, for example, the flow of the heat medium connected by the low protrusions, which easily suppress the flow resistance, becomes meandering in the flow width direction, and it is possible to exert the effect of stirring the heat medium in the flow width direction. In addition, for example, the heat medium after the low protrusion of one protrusion flows toward the high protrusion of the next protrusion, whereby it is also possible to expect that the heat medium after the low protrusion is smoothly passed through the low protrusion and is efficiently stirred by the collision with the high protrusion with a relatively low flow resistance.

[0083] The thirty-fourth mode is based on the cooling heat exchanger of any one of the first mode to the thirty-third mode, and in the cross section in the flow length direction of the flow path portion, the protrusion is formed in a cross-sectional shape in which the tip end is tapered toward the protrusion tip end, and the protrusion tip portion, the upstream inclined portion which is obliquely extended from the protrusion tip portion toward the bottom surface side of the flow path portion, that is, the protrusion base portion, toward the upstream side of the flow path portion, and the downstream inclined portion which is obliquely extended from the protrusion tip portion toward the protrusion base portion toward the downstream side are continuously provided without an angle portion and smoothly.

[0084] According to the cooling heat exchanger formed in the structure according to the present mode, the surface of the protrusion is continuously provided smoothly in the cross section in the flow length direction, and the flow of the heat medium over the protrusion is smoothly generated.

[0085] The thirty-fifth mode is based on the cooling heat exchanger of the thirty-fourth mode, and in the cross section in the flow length direction of the flow path portion, the radius of curvature of the protrusion tip portion is in the range of 0.05 to 1.5 times with respect to the length dimension of the protrusion base portion, and in the cross section in the flow length direction of the flow path portion, the inclination angle of the upstream inclined portion with respect to the bottom surface of the flow path portion is in the range of 20 to 70°.

[0086] According to the cooling heat exchanger formed in the structure according to the present mode, by making the radius of curvature of the protrusion tip portion be 0.05 times or more with respect to the length dimension of the protrusion base portion, the protrusion tip portion is not formed as a substantial angle portion but formed as a smooth circular arc cross section. In addition, by making the radius of curvature of the protrusion tip portion be 1.5 times or less with respect to the length dimension of the protrusion base portion, it is possible to prevent the length dimension of the protrusion in the flow length direction from becoming too long, and it is possible to make the inclination angle of the upstream inclined portion and the downstream inclined portion which are continuously provided smoothly with respect to the bottom surface large enough.

[0087] By setting the inclination angle of the upstream inclined portion with respect to the bottom surface of the flow path portion to 20° or more, the flow of the heat medium from the upstream side toward the protrusion is effectively disturbed by the upstream inclined portion, and an improvement in cooling performance due to the stirring action is achieved. In addition, by setting the inclination angle of the upstream inclined portion with respect to the bottom surface of the flow path portion to 70° or less, it is possible to prevent the flow of the heat medium from being excessively restricted by the protrusion.

[0088] The thirty-sixth aspect is the cooling heat exchanger according to the thirty-fifth aspect, wherein the inclination angle of the upstream inclined portion with respect to the bottom surface of the flow path portion is 25° or less in the cross section in the flow path length direction of the flow path portion.

[0089] According to the cooling heat exchanger formed in accordance with the present aspect, by setting the inclination angle of the upstream inclined portion with respect to the bottom surface of the flow path portion to 25° or less, it is possible to set the pressure loss sufficiently small, and for example, it is also possible to use a cheap pump with lower performance to flow the heat medium.

[0090] The thirty-seventh aspect is the cooling heat exchanger according to any one of the first aspect to the thirty-sixth aspect, wherein the protrusion extends integrally over the flow path width of the flow path portion, and is continuous with the side wall portion of the flow path portion at both end portions.

[0091] According to the cooling heat exchanger formed in accordance with the present aspect, it is possible to prevent the flow of the heat medium flowing between the side wall portion of the flow path portion and the protrusion by bypassing the protrusion, and it is possible to achieve an efficient improvement in cooling performance. In addition, in the case where the protrusion is distant from the side wall portion of the flow path portion, the flow rate of the heat medium flowing between the side wall portion of the flow path portion and the protrusion tends to be fast, and thus there is a risk of cutting of the wall portion of the flow path portion and the protrusion. However, in the cooling heat exchanger according to the present aspect, the protrusion extends integrally over the flow path width and is continuous with the side wall portion of the flow path portion, and thus it is possible to prevent the flow of the heat medium between the side wall portion of the flow path portion and the protrusion, and it is possible to prevent the wall portion of the flow path portion and the protrusion from being cut by the faster flow.

[0092] The thirty-eighth aspect is the cooling heat exchanger according to the thirty-seventh aspect, wherein the protrusion is formed in a V shape that is inclinedly extended toward both sides in the flow path width direction of the cooling flow path toward the downstream side of the cooling flow path.

[0093] According to the cooling heat exchanger formed in the structure according to the present mode, since the ridgelines of the protrusions on both sides in the flow path width direction are inclined in different directions, the heat medium is effectively stirred by flowing over the ridgelines, and the improvement of the cooling performance by the stirring effect can be more favorably achieved. In particular, by providing the protrusions in a V shape inclined toward the downstream side on both sides in the flow path width direction, the heat medium after flowing over the ridgelines of the protrusions flows into the inner side in the flow path width direction and merges on the downstream side of the protrusions, respectively, and thus the generation of a vortex flow can be expected, and further improvement of the stirring effect can be achieved.

[0094] Practical effects

[0095] According to the present application, the cooling performance can be more effectively achieved in the cooling heat exchanger. BRIEF DESCRIPTION OF DRAWINGS

[0096] Figure 1 is an exploded perspective view of the cooling heat exchanger according to the first embodiment of the present application.

[0097] Figure 2 is a cross-sectional view of the cooling heat exchanger shown in Figure 1 , which is a view corresponding to the II-II cross section of Figure 4 .

[0098] Figure 3 is a III-III cross-sectional view of Figure 2 .

[0099] Figure 4 is a IV-IV cross-sectional view of Figure 2 .

[0100] Figure 5 is an enlarged cross-sectional view of the protrusion provided in the cooling heat exchanger shown in Figure 1 .

[0101] Figure 6 is a perspective view showing a state in which a battery pack is assembled in the cooling heat exchanger of Figure 1 .

[0102] Figure 7 is a graph showing the temperature distribution of the heat medium in the flow path portion in the cooling heat exchanger of Figure 1 .

[0103] Figure 8 is a cross-sectional view of the cooling heat exchanger according to the second embodiment of the present application.

[0104] Figure 9 is an exploded perspective view of the cooling heat exchanger according to the third embodiment of the present application.

[0105] Figure 10 is Figure 9 is a sectional view of the cooling heat exchanger shown in

[0106] Figure 11 is a sectional view of the cooling heat exchanger as a fourth embodiment of the present application.

[0107] Figure 12 is a sectional view of the cooling heat exchanger as a fifth embodiment of the present application.

[0108] Figure 13 is a sectional view of the cooling heat exchanger as a sixth embodiment of the present application.

[0109] Figure 14 is a sectional view of the cooling heat exchanger as a seventh embodiment of the present application, which is a view corresponding to the XIV-XIV section of Figure 15

[0110] Figure 15 is a sectional view of the cooling heat exchanger shown in Figure 14 is a view corresponding to the XV-XV section of Figure 14

[0111] Figure 16 is a main part sectional view of the cooling heat exchanger as an eighth embodiment of the present application.

[0112] Figure 17 is another main part sectional view of the cooling heat exchanger shown in Figure 16

[0113] Figure 18 is a main part sectional view of the cooling heat exchanger as another embodiment of the present application.

[0114] Explanation of Reference Numerals

[0115] ​​​10: cooling heat exchanger (first embodiment); 12: cooling surface constituting member; 14: flow path member; 16: cooling surface; 18: concave portion; 20: outer peripheral fixed portion; 22: supply hole; 24: supply port; 26: discharge hole; 28: discharge port; 30: inner peripheral fixed portion (partition wall portion); 32 (32a-32e): groove; 36: cooling flow path; 38: parallel flow path portion; 40 (40a-40e): flow path portion; 42: protrusion; 44: ridge line; 45a: protrusion top; 45b: protrusion base; 46: first inclined surface (upstream inclined portion); 48: second inclined surface (downstream inclined portion); 50: narrow flow path portion; 52: battery pack (cooling object); 54: terminal portion; 60: cooling heat exchanger (second embodiment); 62: flow path member; 64: concave portion; 66: central fixed portion; 68: cooling flow path; 70: parallel flow path portion; 72: parallel flow path portion; 74 (74a, 74b): flow path portion; 76 (76a, 76b): flow path portion; 78: intermediate confluence portion; 80: cooling heat exchanger (third embodiment); 82: flow path member; 84: columnar fixed portion; 90: cooling heat exchanger (fourth embodiment); 100: cooling heat exchanger (fifth embodiment); 110: cooling heat exchanger (sixth embodiment); 120: cooling heat exchanger (seventh embodiment); 121: flow path member; 122: turbulent flow portion; 124: first laminar flow portion (laminar flow portion); 126: second laminar flow portion; 128: inlet side flow path portion; 130: inclined bottom surface; 132: outlet side flow path portion; 140: cooling heat exchanger (eighth embodiment); 142: protrusion; 142a: first protrusion; 142b: second protrusion; 144: low protrusion portion; 146: high protrusion portion; 150: protrusion (another embodiment); 152: protrusion top; 154: first inclined surface (upstream inclined portion); 156: second inclined surface (downstream inclined portion); R: radius of curvature of protrusion top; L: length dimension of protrusion base; a: inclination angle of first inclined surface; b: inclination angle of second inclined surface. DETAILED DESCRIPTION

[0116] Embodiments of the present application will be described below with reference to the drawings.

[0117] Figures 1-3 A cooling heat exchanger 10 as a first embodiment of the present application is shown. The cooling heat exchanger 10 is formed in a laminated structure in which a cooling surface constituting member 12 and a flow path member 14 are overlaid on each other. In the following description, the up-down direction is the up-down direction in the drawing of FIG. 1, i.e., the direction in which the cooling surface constituting member 12 and the flow path member 14 are overlaid on each other, and the front-rear direction is the direction in which the plurality of flow path portions 40 described later are aligned. Figure 2 Figure 3 ​The left and right directions refer to the length direction of the flow path in the flow path section 40. Figure 2 The left and right directions within. Furthermore, in this embodiment, the upstream side of the flow path 40 is... Figure 2 The left side of the middle, and the downstream side is Figure 2 On the right side, the heat medium flows from left to right in the flow path section 40.

[0118] The cooling surface component 12 is a generally rectangular flat plate, with its length in the left-right direction being larger than its width in the front-back direction. The cooling surface component 12 is formed of a material with a high thermal conductivity, such as metal or a thermally conductive synthetic resin containing thermally conductive fillers. The cooling surface component 12 is preferably made of a metal with a high thermal conductivity, such as aluminum alloy, iron, stainless steel, or copper. In this embodiment, the upper surface of the cooling surface component 12 is formed as a cooling surface 16 that overlaps substantially entirely with the plurality of battery packs 52 described later.

[0119] The flow path component 14 is generally rectangular flat plate in shape, with a planar shape roughly corresponding to the cooling surface component 12, and its external dimensions when viewed from above are roughly the same as those of the cooling surface component 12. The flow path component 14 can be made of metals such as aluminum alloy or stainless steel, or synthetic resins such as polypropylene, polyethylene, polycarbonate, or polyamide. If the flow path component 14 is made of synthetic resin, it is expected to result in a lighter cooling heat exchanger 10, easier formation of the concave portion 18 (groove 32) and protrusion 42 (described later), greater freedom in the shape of the concave portion 18 (groove 32) and protrusion 42 (described later), and improved precision.

[0120] like Figure 4 As shown, the flow path member 14 includes a recessed portion 18 with an opening on its upper surface. In this embodiment, the recessed portion 18... Figure 4 In the top view, it is rectangular. Around the concave portion 18, a generally rectangular annular outer peripheral fixing portion 20 protruding upward from the bottom surface of the concave portion 18 is continuously provided all around the circumference.

[0121] A supply hole 22 extending vertically is formed at the front end of the concave portion 18, and a cylindrical supply port 24 protruding downward from the periphery of the supply hole 22 is provided. In this embodiment, the supply hole 22 is located at the left front corner of the concave portion 18. Furthermore, a discharge hole 26 extending vertically is formed at the rear end of the concave portion 18, and a cylindrical discharge port 28 protruding downward from the periphery of the discharge hole 26 is provided. In this embodiment, the discharge hole 26 is located at the right rear corner of the concave portion 18. Therefore, the supply hole 22 and the discharge hole 26 are located on opposite sides of the concave portion 18, which is approximately rectangular when viewed from above.

[0122] In the recessed portion 18, a plurality of inner circumferential fixed portions 30 are provided protruding upward from the bottom surface of the recessed portion 18. The inner circumferential fixed portions 30 extend linearly in the left-right direction, and the both end portions are separated toward the inner side in the left-right direction with respect to the outer circumferential fixed portion 20. In the present embodiment, four inner circumferential fixed portions 30, 30, 30, 30 are provided separated from each other in the front-rear direction. The distance between the adjacent inner circumferential fixed portions 30, 30 in the front-rear direction is substantially constant. Further, the interval distance in the front-rear direction between the inner circumferential fixed portions 30, 30 at both ends in the front-rear direction and the outer circumferential fixed portion 20 is substantially equal to the distance between the adjacent inner circumferential fixed portions 30, 30 in the front-rear direction. By forming such inner circumferential fixed portions 30, 30, 30, 30, the middle portion of the recessed portion 18 in the left-right direction is divided into five grooves 32a, 32b, 32c, 32d, 32e extending linearly in the left-right direction. The width dimension of the inner circumferential fixed portion 30 is preferably 4 mm or less. Thereby, the width dimension of the wall portion separating the adjacent grooves 32, 32 is preferably 4 mm or less. Note that the both end portions of the recessed portion 18 in the left-right direction are continuous in the front-rear direction without being divided by the inner circumferential fixed portions 30, 30, 30, 30. Further, the both end portions of the recessed portion 18 continuous in the front-rear direction are formed with the supply hole 22 and the discharge hole 26.

[0123] Further, the cooling surface constituting member 12 overlaps the flow path member 14 from above. The cooling surface constituting member 12 overlaps the flow path member 14 in the abutting state at the outer peripheral fixed portion 20 and the inner peripheral fixed portions 30, 30, 30, 30, and is fixed to the flow path member 14 at the outer peripheral fixed portion 20 and the inner peripheral fixed portions 30, 30, 30, 30. The cooling surface constituting member 12 can be fixed to the flow path member 14 at the outer peripheral fixed portion 20 and the inner peripheral fixed portions 30, 30, 30, 30 by the conventional means such as adhesion based on an adhesive, fusion, welding, brazing, or the like. In the present embodiment, the cooling surface constituting member 12 and the flow path member 14 are fixed to each other in the abutting state at the inner peripheral fixed portions 30 of the inner peripheral portions, and therefore, for example, even if the hydraulic pressure of the heat medium acts in the direction in which the cooling surface constituting member 12 and the flow path member 14 are separated from each other in the vertical direction, separation and deformation of the cooling surface constituting member 12 and the flow path member 14 can be prevented. Further, the cooling surface constituting member 12 can be fixed to the flow path member 14 by means such as mechanical engagement based on a hook, riveting, or the like. In this case, in order to ensure the liquid tightness between the cooling surface constituting member 12 and the overlapping surfaces of the outer peripheral fixed portion 20 and the inner peripheral fixed portions 30, 30, 30, 30, it is preferable that a sealing material such as sealing rubber or the like be arranged between these overlapping surfaces.

[0124] The cooling surface constituting member 12 mounted to the flow path member 14 is separated upward with respect to the bottom surface of the recessed portion 18. Thus, the cooling flow path 36 based on the recessed portion 18 is formed between the overlapping surfaces of the cooling surface constituting member 12 and the flow path member 14. The cooling flow path 36 is provided inside the cooling heat exchanger 10 and is formed as a flow path through which the heat medium for cooling flows. The cooling flow path 36 is a flow path that connects the supply hole 22 and the discharge hole 26 to each other, and is connected to an external flow path not shown through the supply port 24 and the discharge port 28. Further, the heat medium that flows into the cooling flow path 36 from the external flow path through the supply hole 22 flows from the left toward the right, and is discharged from the cooling flow path 36 to the external flow path through the discharge hole 26. Note that a cooling device for cooling the heat medium, such as an air cooling device or a liquid cooling device, or the like, such as a refrigerator or a radiator, is provided in the external flow path, and the heat medium cooled by the cooling device is supplied to the cooling flow path 36.

[0125] The cooling flow path 36 has a parallel flow path portion 38. The parallel flow path portion 38 is a portion in which a plurality of flow path portions 40 whose flow directions of the heat medium described later are the same as each other are adjacently arranged in parallel. In the present embodiment, the upper openings of the five grooves 32a, 32b, 32c, 32d, and 32e are covered by the cooling surface configuring member 12, and thus the parallel flow path portion 38 configured by the five flow path portions 40a, 40b, 40c, 40d, and 40e is provided to the middle portion of the cooling flow path 36. The parallel flow path portion 38 is provided to be substantially parallel to the cooling surface 16 in a portion other than the protrusion 42 described later.

[0126] The five flow path portions 40a to 40e have a substantially constant cross-sectional shape and cross-sectional area. In addition, with respect to the path length in the cooling flow path 36 from the supply hole 22 to the discharge hole 26, since the supply hole 22 and the discharge hole 26 are located diagonally, the path through any one of the five flow path portions 40a to 40e is substantially the same.

[0127] The flow directions of the heat medium flowing in the cooling flow path 36 are the same as each other in the five flow path portions 40a to 40e of the parallel flow path portion 38. Thus, when the heat medium receives heat from the battery pack 52 described later while flowing in the flow path portions 40a to 40e, the temperature difference of the heat medium flowing in the flow path portions 40a to 40e is small, and the heat exchange of the heat medium between the flow path portions 40a to 40e can be suppressed. Therefore, on the upstream side of the parallel flow path portion 38, the temperature change of the heat medium caused by the heat exchange between the flow path portions 40a to 40e is prevented, and the heat medium is kept at a low temperature.

[0128] The width dimension of the inner peripheral fixed portion 30 in the front-rear direction that separates the flow path portions 40 adjacent to each other in the front-rear direction is as small as 4 mm or less. Thus, in the left and right central portions of the cooling heat exchanger 10 in which the parallel flow path portion 38 is provided, the projected area of the flow path portions 40a to 40e in the vertical direction is ensured to be large. Thus, the reduction of the flow resistance of the heat medium in each flow path portion 40 can be achieved, and the area of the cooling surface configuring member 12 that directly contacts the heat medium is large, and the cooling surface 16 can be efficiently cooled. Note that since the flow directions of the heat medium in the flow path portions 40a to 40e are the same as each other, even if the distance between the adjacent flow path portions 40, 40 is shortened, the temperature rise of the heat medium caused by the heat exchange between these flow path portions 40, 40 is not a problem.

[0129] Preferably, the flow path width dimension of the flow path portion 40 is in the range of 0.3 to 30 times, more preferably in the range of 0.5 to 20 times, relative to the width dimension of the inner peripheral fixed portion 30 as the partition wall portion that separates the adjacent flow path portions 40, 40. Thereby, in the left and right central portions of the cooling heat exchanger 10 provided with the parallel flow path portions 38, the bonding area of the cooling surface constituting member 12 and the flow path member 14 can be sufficiently ensured, and the projected area of the flow path portions 40a to 40e in the vertical direction can be obtained more largely.

[0130] A plurality of protrusions 42 are provided in the parallel flow path portion 38. As shown in Figure 2 、 Figure 3 , the protrusions 42 protrude upward from the bottom surface of the groove 32 in the flow path member 14 toward the cooling surface constituting member 12. The protrusions 42 are provided throughout the front and rear flow path width of the flow path portion 40, and the end portions in the front and rear direction are continuous with the outer peripheral fixed portion 20 or the inner peripheral fixed portion 30 that constitutes the side wall portion of the flow path portion 40. The protrusions 42 are V-shaped when viewed from above as shown in Figure 4 , and are inclined to the right from the front and rear center toward the front and rear ends.

[0131] As shown in enlargement in Figure 5 , the protrusions 42 have a cross-sectional shape in which the front end becomes thin toward the protruding front end, and the portion that protrudes most upward forms a ridge line 44 that extends in a V shape. The ridge line 44 extends obliquely with respect to the flow path length direction of the flow path portion 40. The ridge line 44 can be an edge-shaped form that forms an angle, or can be constituted by a flat surface or a curved surface, and has a width in the flow path length direction. The protrusion 42 of the present embodiment has a cross-sectional shape in which the protrusion top portion 45a including the ridge line 44 is curved in an arc shape, and the uppermost end portion of the protrusion top portion 45a is the ridge line 44. The curvature radius R of the protrusion top portion 45a with respect to the length dimension L in the flow path length direction of the protrusion base portion 45b (the connecting end portion of the protrusion 42 with the bottom surface of the groove 32) is in the range of 0.05 times to 1.5 times, more preferably in the range of 0.25 times to 0.9 times.

[0132] The side surface of the protrusion 42 on the upstream side of the flow path portion 40 is formed as a first inclined surface 46 as an upstream inclined portion that inclines upward from the upstream side toward the downstream side to approach the cooling surface constituting member 12. In addition, the side surface of the protrusion 42 on the downstream side of the flow path portion 40 is formed as a second inclined surface 48 as a downstream inclined portion that inclines downward from the upstream side toward the downstream side to separate from the cooling surface constituting member 12. The protrusion height of the protrusion 42 from the bottom surface of the groove 32 gradually increases on the portion on the upstream side of the ridge line 44 (protrusion top 45a) constituting the first inclined surface 46 as the protrusion height approaches the downstream side from the upstream side, and gradually decreases on the portion on the downstream side of the ridge line 44 (protrusion top 45a) constituting the second inclined surface 48 as the protrusion height approaches the downstream side from the upstream side. Note that the magnitude relationship of the inclination angle a of the first inclined surface 46 and the inclination angle β of the second inclined surface 48 can be any one of a < β, a = β, a > β.

[0133] In summary, the protrusion 42 has a cross-sectional shape of a substantially triangular shape in which the tip end is tapered toward the protruding tip end in the cross section in the flow path length direction. The protrusion 42 is formed to continuously have a cross-sectional shape of the protrusion top 45a curved in a circular arc shape, the first inclined surface 46 that extends obliquely upward from the end portion on the upstream side of the protrusion top 45a toward the protrusion base 45b, and the second inclined surface 48 that extends obliquely downward from the end portion on the downstream side of the protrusion top 45a toward the protrusion base 45b. Note that the ridge line 44 is formed by continuously connecting the upper end of the protrusion top 45a in the flow path width direction, and has a V shape constituted by two inclined straight line portions when viewed from above.

[0134] The first inclined surface 46 can also be curved, but is provided as a flat surface in the present embodiment. The upper end portion of the first inclined surface 46 extends from the end portion on the upstream side of the protrusion top 45a in a tangential direction, and is continuously connected to the protrusion top 45a without an angle and smoothly. The lower end portion of the first inclined surface 46 can also be curved in a circular arc shape, in which case it is preferable that the lower end portion of the first inclined surface 46 be continuously connected to the bottom surface of the groove 32 without an angle and smoothly.

[0135] The inclination angle a of the first inclined surface 46 with respect to the bottom surface of the groove 32 constituting the flow path portion 40 is in the range of 20° to 70°, and more preferably in the range of 30° to 60°. Note that in the case where the first inclined surface 46 is curved, the inclination angle a of the first inclined surface 46 with respect to the bottom surface of the groove 32 can be grasped, for example, as an average value of the inclination angle of the first inclined surface 46 with respect to the bottom surface of the groove 32.

[0136] The second inclined surface 48 can also be curved, but is planar in this embodiment. The upper end of the second inclined surface 48 extends from the end of the protrusion top 45a on the downstream side in a tangential direction, and is continuous smoothly without a corner with respect to the protrusion top 45a. The lower end of the second inclined surface 48 can also be curved in an arc shape, in which case it is preferable that it be continuous smoothly without a corner with respect to the bottom surface of the flow path portion 40c (the groove 32).

[0137] The inclination angle β of the second inclined surface 48 with respect to the bottom surface of the groove 32 is in the range of 20° to 70°, and more preferably in the range of 30° to 60°. In this embodiment, the inclination angle α of the first inclined surface 46 and the inclination angle β of the second inclined surface 48 are substantially the same as each other, but for example, the inclination angle α of the first inclined surface 46 can be larger than the inclination angle β of the second inclined surface 48, or the like, and can be different from each other. Note that in the case where the second inclined surface 48 is curved, the inclination angle β of the second inclined surface 48 with respect to the bottom surface of the groove 32 can be grasped, for example, as an average of the inclination angles of the second inclined surface 48 with respect to the bottom surface of the groove 32.

[0138] The protrusion height dimension of the protrusion 42 with respect to the width dimension of the protrusion 42 in the flow path width direction is preferably in the range of 0.1 times to 1.3 times, and more preferably in the range of 0.25 times to 0.9 times. Thereby, the stirring action on the heat medium by the flow over the protrusion 42 can be effectively obtained, and the flow of the heat medium is prevented from being excessively restricted by the protrusion 42, and smooth flow of the heat medium is achieved.

[0139] Note that, regarding the cross-sectional shape of the protrusion 42, the cross-sectional shape of the protrusion 42 in the flow path length direction through the center of the flow path width direction is represented by a circle, an ellipse, a polygonal shape, or the like. Figure 5 The cross-sectional shape of the protrusion 42 in the flow path length direction through the center of the flow path width direction is represented by a circle, an ellipse, a polygonal shape, or the like, as described above, but the arbitrary cross-sectional shape of the protrusion 42 orthogonal to the ridge line 44 is formed to be the same as the cross-sectional shape of the protrusion 42 in the flow path length direction through the center of the flow path width direction. Figure 5 The same cross-sectional shape is preferably applied to each of the arbitrary cross-sectional shapes orthogonal to the ridge line 44.

[0140] The protrusions 42 are respectively provided in the flow path portion 40a, the flow path portion 40b, the flow path portion 40d, and the flow path portion 40e. The protrusions 42 are arranged in the flow path length direction of the heat medium in each of these flow path portions 40.

[0141] By protruding the protrusions 42 from the bottom surface of the grooves 32 in the flow path member 14 toward the cooling surface constituting member 12, the formed portions of the protrusions 42 in the flow path portions 40 are formed as narrow flow path portions 50 in which the flow path cross-sectional area is reduced. The flow path cross-sectional area of the narrow flow path portions 50 gradually decreases toward the downstream side on the first inclined surface 46 of the protrusion 42, and the flow path cross-sectional area gradually increases toward the downstream side on the second inclined surface 48 of the protrusion 42, with the flow path cross-sectional area being the smallest at the ridge line 44 of the protrusion 42.

[0142] Further, in the flow path portion 40a, the flow path portion 40b, the flow path portion 40d, and the flow path portion 40e in which a plurality of protrusions 42 are provided, a plurality of narrow flow path portions 50 are formed by the plurality of protrusions 42. Also, in the flow path portion 40a, the flow path portion 40b, the flow path portion 40d, and the flow path portion 40e, the higher the protrusion 42 is on the downstream side, the higher the protrusion height is, and the smaller the narrow flow path portion 50 is on the downstream side, the smaller the minimum flow path cross-sectional area is. Thus, the flow rate of the heat medium passing through the narrow flow path portions 50 can be sufficiently increased on the downstream side.

[0143] The maximum protrusion height dimension of the protrusion 42, that is, the protrusion height dimension at the ridge line 44, is preferably 30% or more, and more preferably 50% or more, of the up-and-down depth dimension of the flow path portion 40. In addition, the length dimension of the protrusion 42 in the flow path length direction of the flow path portion 40 is preferably equal to or less than the flow path width dimension of the flow path portion 40, and more preferably 75% or less of the flow path width dimension of the flow path portion 40. In addition, it is preferable that the length dimension (left-right dimension) of the protrusion 42 be smaller than the width dimension (front-rear dimension).

[0144] The heat medium flowing in the parallel flow path portions 38 flows over the protrusions 42, thereby generating turbulence such as longitudinal vortex flow, and the flow is disturbed and stirred. Thus, in the flow path cross section (cross section orthogonal to the flow path length) of each flow path portion 40, the temperature boundary is eliminated, the temperature unevenness of the heat medium is reduced, and thus temperature uniformization can be achieved.

[0145] As shown in Figs. 1 and 2, the protrusions 42 are provided in the flow path portions 40a, 40b, 40c, 40d, and 40e. The protrusions 42 are formed by protruding the ridge line 44 of the V-shaped protrusion 42 from the bottom surface of the grooves 32 in the flow path member 14 toward the cooling surface constituting member 12. Figure 1 , Figure 4 As shown in Figs. 1 and 2, the protrusions 42 are provided in the flow path portions 40a, 40b, 40c, 40d, and 40e. The protrusions 42 are formed by protruding the ridge line 44 of the V-shaped protrusion 42 from the bottom surface of the grooves 32 in the flow path member 14 toward the cooling surface constituting member 12.

[0146] Here, as shown in Figs. 1 and 2, the protrusions 42 are provided in the flow path portions 40a, 40b, 40c, 40d, and 40e. The protrusions 42 are formed by protruding the ridge line 44 of the V-shaped protrusion 42 from the bottom surface of the grooves 32 in the flow path member 14 toward the cooling surface constituting member 12. Figures 1-4As shown, the protrusions 42 are not provided integrally in the parallel flow path portions 38, but are provided locally to be arranged in a manner having a specific bias. In this way, by the presence of portions provided with the protrusions 42 and portions not provided with the protrusions 42 in the parallel flow path portions 38, the effects of disturbing the flow of the heat medium by the protrusions 42 are set to be strong and weak, and regions in which the effects of disturbing the flow of the heat medium by the protrusions 42 are different from each other are set.

[0147] That is, the protrusions 42 are provided in a manner in which the number increases from the center in the front-rear direction toward the outer sides. In the present embodiment, the flow path portion 40c at the center in the front-rear direction is not provided with the protrusions 42. In addition, the flow path portion 40b and the flow path portion 40d adjacent to the flow path portion 40c in the outer sides in the front-rear direction are each provided with four protrusions 42, 42, 42, 42, and the flow path portion 40a and the flow path portion 40e at both ends in the front-rear direction adjacent to the flow path portion 40b and the flow path portion 40d are each provided with seven protrusions 42, 42,..., 42. Thus, the effect of disturbing the flow of the heat medium is set to be the weakest in the flow path portion 40c at the center in the front-rear direction, and the effect of disturbing the flow of the heat medium is set to be the strongest in the flow path portions 40a and 40e at both ends in the front-rear direction. In addition, the effects of disturbing the flow of the heat medium are set to be stronger than in the flow path portion 40c and weaker than in the flow path portions 40a and 40e in the flow path portions 40b and 40d. In this way, in the cooling heat exchanger 10 of the present embodiment, the flow path portions 40a and 40e and the flow path portions 40b and 40d and the flow path portion 40c are formed as regions in which the effects of disturbing the flow of the heat medium by the protrusions 42 are different from each other. Each of the groups of the flow path portions 40a and 40b, 40b and 40c, 40c and 40d, and 40d and 40e is provided with regions in which the effects of promoting turbulence are different from each other.

[0148] Note that in the flow path portions 40a, 40b, 40d, and 40e, the plurality of protrusions 42 are arranged at positions separated from each other in the flow path length direction. Thus, between the protrusions 42, 42 of each flow path portion 40, there is a portion in which the lower surface is flat without the protrusions 42.

[0149] Further, the protrusions 42 are provided on the downstream side of the parallel flow path portions 38, and are not provided on the upstream side. More specifically, the protrusions 42 are provided on the right side, which is the downstream side of the center in the flow path length direction (left-right direction) of the parallel flow path portions 38, and are not provided on the left side, which is the upstream side. Thus, in the region on the downstream side where the protrusions 42 are provided, the effect of disturbing the flow of the heat medium is set to be stronger than in the region on the upstream side where the protrusions 42 are not provided. In other words, in the parallel flow path portions 38, regions in which the effect of disturbing the flow of the heat medium by the protrusions 42 is different from each other are set in the flow direction of the heat medium in a manner in which the upstream side (region where the protrusions 42 are not provided) and the downstream side (region where the protrusions 42 are provided) are arranged. Note that the protrusions 42 are not provided to the downstream end of the parallel flow path portions 38, but are disposed on the left side of the right end of the inner peripheral fixed portion 30.

[0150] Further, in the flow path portions 40a, 40b, 40d, 40e, the protrusions 42 are disposed so that the interval in the flow path length direction, that is, the left-right direction, of each of the flow path portions 40 becomes narrower as it approaches the right side, which is the downstream side of the parallel flow path portions 38. Thus, in the flow path portions 40a, 40b, 40d, 40e, the effect of disturbing the flow of the heat medium by the protrusions 42 is set to be stronger as it approaches the downstream side. Thus, in the present embodiment, regions in which the turbulence promotion effect is different between the upstream side and the downstream side are set according to the presence or absence of the protrusions 42, and on this basis, the region on the downstream side is composed of regions in which the turbulence promotion effect is different according to the interval of the protrusions 42. Two or more regions in which the interval of the protrusions 42 is different, which constitute the region on the downstream side, are set to be arranged in the flow direction of the heat medium. Specifically, it can also be recognized in a manner in which, for example, in the flow path portion 40a, an upstream region from the end portion on the upstream side to the first protrusion 42, a middle region from the first protrusion 42 to the fourth protrusion 42, and a downstream region from the fourth protrusion 42 to the seventh protrusion 42 are set to be regions in which the turbulence promotion effect is different from each other. Note that it is not necessary to make the interval of all the protrusions 42 narrower as it approaches the right side, and for example, a portion in which the same interval is set, or a portion in which the interval on the right side becomes wider can also be included.

[0151] Further, when the heat medium flows over the protrusions 42, it passes through the narrow flow path portions 50 in which the flow path cross-sectional area is small, and thus the flow velocity becomes large. Thus, in the heat medium that flows over the protrusions 42, the effect of disturbing the flow can be more effectively exerted. In particular, in the present embodiment, the narrower the narrow flow path portions 50 on the downstream side, the smaller the flow path cross-sectional area. Thus, when passing through the narrow flow path portions 50, the flow velocity of the heat medium can also be sufficiently increased on the downstream side, and the flow of the heat medium can be effectively disturbed.

[0152] As Figure 6As shown, the battery pack 52 as a cooling target is attached to the cooling heat exchanger 10 having the above structure. The battery pack 52 is, for example, a battery for an electric vehicle, a hybrid vehicle, or the like. The battery pack 52 has, for example, a substantially rectangular parallelepiped shape as a whole, and a front-rear width dimension is larger than a left-right length dimension. Further, a terminal portion 54 protruding upward is provided at both end portions of the battery pack 52 in the front-rear direction. The terminal portion 54 is an output terminal for outputting a large current through a bus bar not shown. Thus, in the battery pack 52 of the present embodiment, the front-rear both end portions having the terminal portion 54 are more likely to become high temperature than the front-rear central portions in the use state.

[0153] As shown, a plurality of battery packs 52 are arranged in the left-right direction, and lower surfaces of these battery packs 52 overlap with a cooling surface 16 constituted by an upper surface of the cooling surface-constituting member 12. In the present embodiment, 15 battery packs 52 are attached to one cooling surface 16. Figure 6

[0154] The cooling heat exchanger 10 makes the cooling surface 16 low temperature by heat exchange between the cooling surface-constituting member 12 and the heat medium flowing in the cooling flow path 36 for cooling. Further, the battery pack 52 generating heat at the time of operation is disposed on the cooling surface 16, and the battery pack 52 is cooled by heat exchange between the cooling surface-constituting member 12 having the cooling surface 16 and the battery pack 52. In other words, the battery pack 52 is cooled by heat exchange between the battery pack 52 and the heat medium flowing in the cooling flow path 36 via the cooling surface-constituting member 12.

[0155] The heat medium is raised in temperature by receiving heat from the battery pack 52. In particular, the heat medium flowing in the upper portion of the cooling flow path 36 near the battery pack 52 is raised in temperature. On the other hand, the heat medium flowing in the lower portion of the cooling flow path 36 away from the battery pack 52 is suppressed in temperature rise as compared with the upper portion. Thus, in the heat medium in the cooling flow path 36, a temperature distribution in which the temperature is higher as it goes to the upper side is easily generated by heat exchange with the battery pack 52. As a result, the temperature difference between the battery pack 52 and the high-temperature heat medium flowing in the upper portion is small, and the efficiency of heat exchange between the battery pack 52 and the heat medium is reduced.

[0156] Thus, in the cooling heat exchanger 10, the protrusion 42 is provided at the parallel flow path portion 38 of the cooling flow path 36, and the heat medium is stirred when passing over the protrusion 42, thereby reducing the temperature difference in the up-down direction of the heat medium. Thereby, the heat medium flowing in the upper portion in the vicinity of the battery pack 52 is prevented from becoming high temperature, the temperature difference between the battery pack 52 and the heat medium in the upper portion is ensured to be large, and thus the heat exchange efficiency between the battery pack 52 and the heat medium can be improved.

[0157] ​Furthermore, as the heat medium flows from upstream to downstream and exchanges heat with multiple battery packs 52, it becomes hotter on the downstream side, which can easily reduce the efficiency of heat exchange with the battery packs 52. Therefore, in the cooling heat exchanger 10, a protrusion 42 is provided only on the downstream side where the temperature rise in the upper part of the heat medium becomes problematic due to the reduction in heat exchange efficiency. The protrusion 42 stirs the heat medium on the downstream side to suppress the temperature rise in the upper part of the heat medium. As a result, not only on the upstream side, which is the inflow side of the low-temperature heat medium, but also on the downstream side, which is the discharge side of the high-temperature heat medium, the temperature difference between the battery packs 52 and the heat medium flowing nearby can be maintained, thus preserving cooling performance.

[0158] like Figure 6 As shown, when multiple battery packs 52 are arranged in the flow path length direction (i.e., left-right direction) of the parallel flow path section 38, the cooling of the downstream battery packs 52 is often insufficient, and performance degradation due to deterioration in the downstream battery packs 52 is likely to occur. Moreover, if the performance of a portion of the downstream battery packs 52 deteriorates, there is a problem specific to battery cooling, where the overall performance of the battery cell composed of multiple battery packs 52 is reduced due to the deteriorated battery packs 52. Here, according to the cooling heat exchanger 10 of this embodiment, the downstream battery packs 52 are also effectively cooled by the stirring effect of the heat medium generated by the protrusions 42, thus suppressing the deterioration of only a portion of the multiple battery packs 52 and preventing the overall performance degradation of the battery cell.

[0159] It should be noted that since there is no protrusion 42 on the upstream side of the parallel flow path section 38, the temperature rise caused by the heat exchange between the hot medium flowing in the lower part away from the battery pack 52 and the battery pack 52 when flowing in the upstream side is small, and it remains at a low temperature. Therefore, by stirring the hot medium reaching the downstream side through the protrusion 42, the temperature of the hot medium flowing in the upper part is greatly reduced, and effective cooling performance can also be obtained on the downstream side.

[0160] Furthermore, in the cooling heat exchanger 10 of this embodiment, the plurality of protrusions 42 are arranged such that their spacing narrows as they move downstream. Therefore, the effect of disrupting the flow of the heat medium is set to be stronger towards the downstream side, and cooling performance can be maintained even downstream where the efficiency of heat exchange with the battery pack 52 is prone to decrease due to the temperature rise of the heat medium. Moreover, in this embodiment, the protrusion height of the protrusions 42 increases towards the downstream side, thus exerting a stronger stirring effect on the heat medium generated by the protrusions 42 on the downstream side.

[0161] As described above, in the cooling heat exchanger 10, the configuration, number, and the like of the protrusions 42 are set in consideration of the flow direction of the heat medium in the parallel flow path portion 38, and thus the cooling performance can be maintained over a large range of the flow direction of the heat medium.

[0162] Note that, from the simulation results of the temperature distribution of the heat medium in the flow path portion 40 shown in FIG. 8, it is also known that the temperature of the heat medium decreases by passing over the protrusions 42. In the flow path portion 40, the temperature distribution of the heat medium flowing in the upper portion of one flow path portion 40 is indicated by the difference in hue. According to the simulation results of the temperature distribution of the heat medium in the flow path portion 40 shown in FIG. 8, it is known that the temperature of the heat medium changes on the upstream side and the downstream side with respect to the protrusions 42. That is, the temperature of the heat medium decreases on the downstream side from the ridge line 44 of the protrusions 42 by the heat medium passing over the ridge line 44 of the protrusions 42 from the upstream side to the downstream side. It is considered that this is because, on the downstream side of the ridge line 44 of the protrusions 42, the heat medium generates turbulence, the heat medium is stirred, and the low-temperature heat medium flowing in the lower portion of the flow path portion 40 mixes with the heat medium flowing in the upper portion, and thus the temperature of the heat medium decreases in the upper portion of the flow path portion 40. Figure 7 Figure 7 According to the simulation results of the temperature distribution of the heat medium in the flow path portion 40 shown in FIG. 8, it is known that the temperature of the heat medium changes on the upstream side and the downstream side with respect to the protrusions 42. That is, the temperature of the heat medium decreases on the downstream side from the ridge line 44 of the protrusions 42 by the heat medium passing over the ridge line 44 of the protrusions 42 from the upstream side to the downstream side. It is considered that this is because, on the downstream side of the ridge line 44 of the protrusions 42, the heat medium generates turbulence, the heat medium is stirred, and the low-temperature heat medium flowing in the lower portion of the flow path portion 40 mixes with the heat medium flowing in the upper portion, and thus the temperature of the heat medium decreases in the upper portion of the flow path portion 40. Figure 7 According to the temperature distribution of the heat medium in the flow path portion 40 shown in FIG. 8, it is known that the narrower the interval of the protrusions 42, the more the temperature of the heat medium flowing in the upper portion of the flow path portion 40 decreases. Thus, it is also confirmed from the simulation results of the temperature distribution of the heat medium in the flow path portion 40 shown in FIG. 8 that, by narrowing the interval of the protrusions 42, the protrusions 42 can more effectively disturb the flow of the heat medium.

[0163] Figure 7 According to the temperature distribution of the heat medium in the flow path portion 40 shown in FIG. 8, it is known that the narrower the interval of the protrusions 42, the more the temperature of the heat medium flowing in the upper portion of the flow path portion 40 decreases. Thus, it is also confirmed from the simulation results of the temperature distribution of the heat medium in the flow path portion 40 shown in FIG. 8 that, by narrowing the interval of the protrusions 42, the protrusions 42 can more effectively disturb the flow of the heat medium. Figure 7

[0164] In addition, in the battery group 52, the heat generation amount of the front and rear end portions where the terminal portions 54 are provided is large, and the front and rear end portions are more likely to become high temperature than the front and rear central portions, and thus the heat medium flowing in the parallel flow path portion 38 is more likely to become high temperature as it goes to the outside in the front and rear directions. Therefore, in the cooling heat exchanger 10, of the five flow path portions 40a to 40e that constitute the parallel flow path portion 38, the more the flow path portion 40 is located on the outside in the front and rear directions, the more the protrusions 42 are provided. That is, the flow path portions 40a and 40e located directly below the front and rear end portions of the battery group 52 are provided with the most seven protrusions 42, and most strongly exert the stirring action of disturbing the flow of the heat medium by these protrusions 42, and prevent the decrease in the heat exchange efficiency caused by the temperature increase of the heat medium in the upper portion. In addition, the flow path portions 40b and 40d close to the front and rear end portions of the battery group 52 are provided with four protrusions 42, which is less than the flow path portions 40a and 40e and more than the flow path portions 40c, and effectively prevent the temperature increase of the heat medium in the local portion by these protrusions 42.

[0165] ​​​Thus, in the cooling heat exchanger 10, the configuration, number, and the like of the protrusions 42 are set in consideration of the temperature distribution (heat generation pattern) of the battery pack 52 as a cooling target, and thus the battery pack 52 can be efficiently cooled.

[0166] In the cooling heat exchanger 10, the protrusions 42 that disturb the flow of the heat medium in the parallel flow path portions 38 are provided in the required portions, and on the other hand, are not provided in the unnecessary portions. Thus, the flow of the heat medium is not unnecessarily disturbed, and the improvement of the cooling performance can be achieved while the smooth flow of the heat medium is achieved.

[0167] In the present embodiment, the region on the downstream side of the specific region is set in a different manner from the region on the upstream side of the other region in that the protrusions 42 are provided. Also, in the region on the downstream side of the specific region, the cross-sectional shape of the flow path portion 40 is changed according to the protrusions 42, and the adjustment of the cooling efficiency of the heat medium is achieved based on the turbulence promotion effect of the heat medium generated by the protrusions 42. Also, in the region on the downstream side, the interval of the protrusions 42 is not uniformly narrowed toward the downstream side, and thus the region on the downstream side can also be regarded as a plurality of regions, and in this case, the regions are set in different manners from each other in terms of the interval of the protrusions 42.

[0168] In the present embodiment, the regions on the front and rear outer sides of the specific region are set in a different manner from the regions on the front and rear inner sides of the other region in that the number of the protrusions 42 is large. Also, in the regions on the front and rear outer sides of the specific region, the adjustment of the cooling efficiency of the heat medium is achieved based on the turbulence promotion effect of the heat medium generated by the protrusions 42. In the present embodiment, for example, from the viewpoint of the presence or absence of the protrusions 42, the flow path portions 40a, 40b, 40d, and 40e on the front and rear sides on which the protrusions 42 are provided can be regarded as the specific region, and the flow path portion 40c in the center on which the protrusions 42 are not provided can be regarded as the other region, and for example, the flow path portions 40a to 40e can be regarded as different specific regions from each other in terms of the number of the protrusions 42.

[0169] According to the adjustment method of the cooling effect of the cooling heat exchanger 10 in which the cooling efficiency based on the heat medium is adjusted in the specific region, for example, by setting the specific region in the portion of the battery pack 52 in which the amount of heat generation is large, efficient cooling of the battery pack 52 can be achieved.

[0170] The curvature radius R of the protrusion top 45a of the protrusion 42 is preferably in the range of 0.05 times to 1.5 times with respect to the length dimension L in the flow path length direction of the protrusion base 45b (the connecting end portion of the protrusion 42 to the bottom surface of the groove 32). By making the curvature radius R of the protrusion top 45a 0.05 times or more with respect to the length dimension L of the protrusion base 45b, the protrusion top 45a is not formed as a substantial corner portion but as a smooth circular arc cross section. In addition, by making the curvature radius R of the protrusion top 45a 1.5 times or less with respect to the length dimension L of the protrusion base 45b, it is possible to prevent the length dimension in the flow path length direction of the protrusion 42 from becoming too long, and it is possible to set the inclination angles a, β of the first inclined surface 46 and the second inclined surface 48, which are smoothly continuous with the protrusion top 45a, to be sufficiently large. Note that in the present embodiment, the curvature radius R of the protrusion top 45a is in the range of 0.05 times to 0.5 times with respect to the length dimension L of the protrusion base 45b.

[0171] In addition, the inclination angle a of the first inclined surface 46 with respect to the bottom surface of the groove 32 that constitutes the flow path portion 40 is in the range of 20° to 70°. By setting the inclination angle a of the first inclined surface 46 to 20° or more, the flow of the heat medium from the upstream side toward the protrusion 42 is effectively disturbed by the first inclined surface 46 at a sufficiently large angle with respect to the flow direction of the heat medium, and an improvement in cooling performance based on the stirring effect is achieved. In addition, by setting the inclination angle a of the first inclined surface 46 to 70° or less, it is possible to prevent the flow of the heat medium from being excessively restricted by the protrusion 42.

[0172] The inclination angle β of the second inclined surface 48 with respect to the bottom surface of the groove 32 is in the range of 20° to 70°. By setting the inclination angle β of the second inclined surface 48 to 20° or more, the flow of the heat medium over the protrusion 42 is easily peeled off from the second inclined surface 48, and an effect of easily generating a disturbed flow such as a vortex on the downstream side of the protrusion 42 can be expected. In addition, by setting the inclination angle β of the second inclined surface 48 to 70° or less, it is also possible to secure the flow of the heat medium along the second inclined surface 48, and a highly efficient stirring of the heat medium by merging with the flow peeled off from the second inclined surface 48 can be expected.

[0173] Figure 8 A cooling heat exchanger 60 as a second embodiment of the present application is shown. In the following description, for the members and portions that are substantially the same as those of the first embodiment, the description is omitted by labeling the same reference numerals in the drawings.

[0174] The cooling heat exchanger 60 has a flow path member 62. The flow path member 62 is a rectangular plate as a whole, and has a concave portion 64 that is open toward the upper side. The concave portion 64 has a groove 32 that is open toward the lower side in the concave portion 64. Figure 8The illustrated inverted U-shaped in plan view is provided with a central fixed portion 66 extending out to the left from the right portion of the outer peripheral fixed portion 20. The central fixed portion 66 is provided as one body in continuation with the outer peripheral fixed portion 20, and the upper surface of the central fixed portion 66 is located on substantially the same plane as the outer peripheral fixed portion 20. The left end of the central fixed portion 66 does not reach the left portion of the outer peripheral fixed portion 20, and is separated to the right from the left portion of the outer peripheral fixed portion 20.

[0175] In the present embodiment, the cooling flow path 68 formed by the cooling face constituting member (not shown) covering the upper opening portion of the recessed portion 64 has an inverted U-shaped flow path shape extending straight to the left from the right end portion, and the front end extending out bending to the rear extending straight to the right. In the present embodiment, the supply hole 22 is formed in the right front corner portion of the recessed portion 64, and the discharge hole 26 is formed in the right rear corner portion of the recessed portion 64.

[0176] In addition, the two end portions of the cooling flow path 68 extending in the left-right direction are formed as parallel flow path portions 70, 72. The upstream side parallel flow path portions 70 are each constituted by two flow path portions 74a, 74b extending straight in the left-right direction, and the heat medium flows in the same direction from the right toward the left in these two flow path portions 74a, 74b. Between the two flow path portions 74a, 74b, an inner peripheral fixed portion 30 extending straight in the left-right direction is provided. The downstream side parallel flow path portions 72 are each constituted by two flow path portions 76a, 76b extending straight in the left-right direction, and the heat medium flows in the same direction from the left toward the right in these two flow path portions 76a, 76b. Between the two flow path portions 76a, 76b, an inner peripheral fixed portion 30 extending straight in the left-right direction is provided.

[0177] Between the upstream side parallel flow path portions 70 and the downstream side parallel flow path portions 72 in the cooling flow path 68, an intermediate confluence portion 78 connecting these parallel flow path portions 70, 72 in series is provided. The intermediate confluence portion 78 constitutes the left end portion of the recessed portion 64, and extends in the front-rear direction at a position to the left of the central fixed portion 66. Furthermore, the heat medium flows separately in the flow path portions 74a, 74b of the upstream side parallel flow path portions 70, converges in the intermediate confluence portion 78, and further flows separately in the flow path portions 76a, 76b of the downstream side parallel flow path portions 72.

[0178] A plurality of protrusions 42 are provided in the parallel flow path portions 70 on the upstream side. The protrusions 42 are formed in both the flow path portions 74a and 74b. The protrusions 42 are provided on the downstream side of the flow path portions 74a and 74b, and are not provided on the upstream side. The protrusions 42 are arranged in each of the flow path portions 74 in such a manner that the interval in the flow path length direction (left-right direction) becomes narrower as it approaches the downstream side. In addition, the flow path portion 74a located on the front and rear outer sides (front side) has a larger number of protrusions 42 than the flow path portion 74b located on the front and rear inner sides. Note that the protrusions 42 located at the downstream end of the flow path portion 74a and the protrusions 42 located at the downstream end of the flow path portion 74b are provided at substantially the same position in the flow path length direction of these flow path portions 74a and 74b. In addition, the flow path portion 74a is provided with the protrusions 42 from a position further on the upstream side than the flow path portion 74b.

[0179] A plurality of protrusions 42 are also provided in the parallel flow path portions 72 on the downstream side. The protrusions 42 are formed in both the flow path portions 76a and 76b. The protrusions 42 are provided on the downstream side of the flow path portions 76a and 76b, and are not provided on the upstream side. The protrusions 42 are arranged in each of the flow path portions 76 in such a manner that the interval in the flow path length direction (left-right direction) becomes narrower as it approaches the downstream side. In addition, the flow path portion 76a located on the front and rear outer sides (rear side) has a larger number of protrusions 42 than the flow path portion 76b located on the front and rear inner sides. Note that the protrusions 42 located at the downstream end of the flow path portion 76a and the protrusions 42 located at the downstream end of the flow path portion 76b are provided at substantially the same position in the flow path length direction of these flow path portions 76a and 76b. In addition, the flow path portion 76a is provided with the protrusions 42 from a position further on the upstream side than the flow path portion 76b.

[0180] According to the cooling heat exchanger 60 formed in such a structure, as with the cooling heat exchanger 10 of the first embodiment, it is possible to maintain an effective cooling performance over a wider area of the cooling flow path 68, and it is possible to set a cooling performance corresponding to the temperature distribution and the like of the battery pack (not shown) that is the cooling target.

[0181] In addition, an intermediate merging portion 78 that connects the parallel flow path portions 70 on the upstream side and the parallel flow path portions 72 on the downstream side in series is provided, and the heat medium flowing in the flow path portions 74a and 74b that constitute the parallel flow path portions 70 on the upstream side merges and mixes in the intermediate merging portion 78. Therefore, the temperature unevenness of the heat medium is further suppressed in the intermediate merging portion 78, and the heat medium as a whole is formed at a relatively low temperature, so it is possible to achieve an improvement in the cooling performance in the parallel flow path portions 72 on the downstream side.

[0182] Note that the intermediate merging portion 78 is not essential, and for example, the flow path portion 74a, the flow path portion 76a, and the flow path portion 74b, the flow path portion 76b can also be provided independently without merging with each other.

[0183] Figure 9 、 Figure 10 A cooling heat exchanger 80 as a third embodiment of the present application is shown. The cooling heat exchanger 80 has a laminated structure in which a cooling surface constituting member 12 and a flow path member 82 overlap each other.

[0184] The flow path member 82 is provided with a plurality of columnar fixed portions 84 protruding upward from the bottom surfaces of the five grooves 32a to 32e. The columnar fixed portions 84 are formed in a substantially cylindrical shape, and their upper surfaces are located on the same plane as the respective upper surfaces of the outer peripheral fixed portions 20 and the inner peripheral fixed portions 30. The columnar fixed portions 84 are provided at positions away from the protrusions 42 in the flow path length direction, and are provided independently of the protrusions 42. The same number of columnar fixed portions 84 are provided in the five grooves 32a to 32e, and these columnar fixed portions 84 are arranged at substantially the same positions in the flow path length direction.

[0185] Further, when the cooling surface constituting member 12 and the flow path member 82 are overlapped and fixed, the lower surface of the cooling surface constituting member 12 is also overlapped in an abutting state with the respective upper surfaces of the columnar fixed portions 84 on the basis of the respective upper surfaces of the outer peripheral fixed portions 20 and the inner peripheral fixed portions 30 being overlapped in an abutting state (see FIG. 6). Figure 10 The columnar fixed portions 84 are fixed to the cooling surface constituting member 12 by means such as adhesion, similarly to the outer peripheral fixed portions 20 and the inner peripheral fixed portions 30.

[0186] In the cooling heat exchanger 80 formed in such a structure, the cooling surface constituting member 12 and the flow path member 82 are also fixed at the columnar fixed portions 84, so that the cooling surface constituting member 12 and the flow path member 82 can be joined more firmly. Therefore, occurrence of an adverse condition in which the cooling surface constituting member 12 and the flow path member 82 are separated, for example, due to the action of the hydraulic pressure of the heat medium flowing in the cooling flow path 36, the action of the bending force of the cooling heat exchanger 80, or the like, can be prevented.

[0187] In addition, the columnar fixed portions are not necessarily limited to a cylindrical shape, and for example, can be an elliptical cylindrical shape, a polygonal cylindrical shape, a special-shaped cylindrical shape, or the like.

[0188] Figure 11 A cooling heat exchanger 90 as a fourth embodiment of the present application is shown. The cooling heat exchanger 90 is provided with protrusions 42 in the four flow path portions 40a, 40b, 40d, 40e, similarly to the cooling heat exchanger 10 of the first embodiment.

[0189] In the cooling heat exchanger 10 of the first embodiment, in the flow path portions 40a and 40e, the same number of protrusions 42 are provided at the same intervals and arrangement, and the effects of disturbing the flow of the heat medium (turbulence promotion effects) are substantially the same. Also, in the flow path portions 40b and 40d, the same number of protrusions 42 are provided at the same intervals and arrangement, and the turbulence promotion effects are substantially the same. In contrast, in the cooling heat exchanger 90 of the present embodiment, in the five flow path portions 40a to 40e, the numbers of protrusions 42 formed are all different, and the turbulence promotion effects are all different from each other.

[0190] Specifically, for example, in the flow path portions 40a and 40e located at the front and rear ends, the numbers of protrusions 42 formed are different from each other, and the turbulence promotion effects generated by the protrusions 42 are different from each other between the flow path portions 40a and 40e. Also, in the flow path portions 40b and 40d, the numbers of protrusions 42 formed are different from each other, and the turbulence promotion effects generated by the protrusions 42 are different from each other between the flow path portions 40b and 40d. Note that the flow path portions 40a to 40e of the present embodiment are, in order from the side with the larger number of protrusions 42 provided, the flow path portion 40e, the flow path portion 40a, the flow path portion 40d, the flow path portion 40b, and the flow path portion 40c.

[0191] By making the numbers of protrusions 42 formed in the flow path portions 40a to 40e different from each other, regions in which the turbulence promotion effects are different from each other are respectively set between the flow path portions 40a to 40e. Regarding the cooling efficiency based on the heat medium in each of the flow path portions 40 of the cooling heat exchanger 90, the more the number of protrusions 42 formed in the flow path portion 40, the higher the cooling efficiency. High cooling performance is exerted at the front and rear end portions of the cooling heat exchanger 90, and particularly, higher cooling performance is exerted at the rear end portion.

[0192] According to the cooling heat exchanger 90 of the present embodiment, for example, in the case where the heat generation amounts of the battery pack (52) are different from each other at the front and rear terminal portions (54, 54), it is possible to provide cooling performance corresponding to the heat generation amount of each terminal portion (54). In the present embodiment, in the case where the heat generation amount of the terminal portion (54) on the rear side is larger than the heat generation amount of the terminal portion (54) on the front side, it is possible to further reduce the temperature difference of the battery pack (52) as a whole by cooling corresponding to the heat generation amount.

[0193] Note that the present embodiment shows an example in which the regions in which the turbulence promotion effect is set to be different for each flow path portion 40 are set in accordance with the number of protrusions 42 formed between the flow path portions 40, but the difference in the turbulence promotion effect can also be set in accordance with the difference in the height, shape, interval, arrangement, etc. of the protrusions 42 between the flow path portions 40. Also, as described above, the difference in the turbulence promotion effect between the regions can also be set by appropriately combining the difference in the number of protrusions 42 formed, the difference in the height, shape, interval, arrangement, etc. of the protrusions 42. Incidentally, for example, in the above-described embodiment shown in FIG. 1, the regions in which the turbulence promotion effect is set to be different for each flow path portion 40 are set in accordance with the difference in the presence or absence of the protrusions 42, the difference in the interval of the protrusions 42, etc. in the flow path portions 40, and the same applies to the following embodiments. Figure 11 In the above-described embodiment shown in FIG. 1, the regions in which the turbulence promotion effect is set to be different for each flow path portion 40 are set in accordance with the difference in the presence or absence of the protrusions 42, the difference in the interval of the protrusions 42, etc. in the flow path portions 40, and the same applies to the following embodiments.

[0194] Figure 12 A cooling heat exchanger 100 according to a fifth embodiment of the present application is shown. The cooling heat exchanger 100 is provided with protrusions 42 in flow path portions 40a to 40c, and is not provided with protrusions 42 in flow path portions 40d and 40e. The protrusions 42 are arranged so as to be biased toward the front in the parallel flow path portions 38.

[0195] In addition, a plurality of protrusions 42 are provided in the flow path portions 40a to 40c. The protrusions 42 in the flow path portions 40a to 40c are each located in the middle of the flow path length direction (left-right direction), and regions in which no protrusions 42 are provided are set at the end on the upstream side and the end on the downstream side. Thus, in the present embodiment, in the parallel flow path portions 38, the plurality of protrusions 42 are arranged so as to be partially biased toward the front end and the central portion in the left-right direction. In addition, in the flow path portions 40a to 40c, the number of protrusions 42 formed increases as it goes toward the front.

[0196] The interval of the six protrusions 42 provided in the flow path portion 40a widens as it goes toward the outer sides (the upstream side and the downstream side) in the flow path length direction of the flow path portion 40a. Similarly, the interval of the four protrusions 42 provided in the flow path portion 40b widens as it goes toward the outer sides (the upstream side and the downstream side) in the flow path length direction of the flow path portion 40b. On the other hand, the interval of the three protrusions 42 provided in the flow path portion 40c is substantially constant in the flow path length direction of the flow path portion 40c.

[0197] Note that the minimum interval of the protrusions 42 in the flow path portion 40a is smaller than the minimum interval of the protrusions 42 in the flow path portion 40b. Also, the protrusions 42 located at the outer end in the flow path length direction of the flow path portion 40a are located at positions further outward in the flow path length direction than the protrusions 42 located at the outer end in the flow path length direction of the flow path portion 40b. Further, the protrusions 42 located at the outer end in the flow path length direction of the flow path portion 40b are located at positions further outward in the flow path length direction than the protrusions 42 located at the outer end in the flow path length direction of the flow path portion 40c.

[0198] According to the cooling heat exchanger 100 of the present embodiment, in the left and right central portions of the front end portion in which the protrusions 42 are concentrated, more excellent cooling performance can be exerted. Therefore, in a case where the amount of heat generation of the cooling target is large in the left and right central portions of the front end portion, the portion in which the amount of heat generation is large can be effectively cooled.

[0199] Note that, in the present embodiment, a structure in which the protrusions 42 are concentrated in the left and right central portions of the front end portion to locally improve the cooling performance is exemplarily shown, but the position at which the cooling performance is locally improved by the protrusions 42 is appropriately set in consideration of the distribution of the amount of heat generation of the cooling target or the like, and is not limited to the left and right central portions of the front end portion. Also, the portion in which the cooling performance is improved by the protrusions 42 is set only at one place in the present embodiment, but can be set at a plurality of places.

[0200] Figure 13 A cooling heat exchanger 110 as a sixth embodiment of the present application is shown. The shapes of the protrusions 42, the sizes including the heights, the configurations, the intervals, and the like of the five flow path portions 40a to 40e of the cooling heat exchanger 110 are substantially the same as each other. Thus, in the present embodiment, the effects of disturbing the flow of the heat medium are substantially the same as each other between the flow path portions 40a to 40e. Also, the plurality of protrusions 42 are provided at substantially the same configurations and intervals as the flow path portions 40a and 40e in the first embodiment in each of the flow path portions 40, and thus regions in which the effects of disturbing the flow of the heat medium by the protrusions 42 provided in the flow path length direction of the flow path portions 40 are different from each other are provided in the flow path length direction of the flow path portions 40.

[0201] As shown in the present embodiment, the effect of disturbing the flow of the heat medium does not necessarily need to be different between the plurality of flow path portions 40 constituting the parallel flow path portion 38, but can be different only in the flow path length direction (flow direction of the heat medium) of the parallel flow path portion 38. According to the cooling heat exchanger 110 according to the present embodiment, for example, in a case where the entire left and right of the battery pack (52) is heated as a whole, cooling can be performed over the entire left and right of the battery pack (52), and even on the downstream side where the temperature of the heat medium is likely to rise due to heat exchange with the battery pack (52), effective cooling performance can be obtained by the promotion effect of the turbulence generated by the protrusions 42.

[0202] Figure 14 A cooling heat exchanger 120 according to a seventh embodiment of the present application is shown. As shown in Figure 15 the present embodiment, the cooling heat exchanger 120 according to the present embodiment has a structure in which the cooling surface constituting members 12 are fixed to the flow path member 121 so as to overlap each other, and the cooling flow path 36 is formed between the overlapping surfaces of these cooling surface constituting members 12 and the flow path member 121. The flow path member 121 according to the present embodiment is constituted by a stamped metal piece, and the outer peripheral fixed portion 20, the supply port 24, the discharge port 28, the inner peripheral fixed portion 30, and the like are provided as one body by stamping.

[0203] As shown in Figure 14 the present embodiment, the cooling heat exchanger 120 has protrusions 42 formed only in the flow path portions 40c constituting the central portions in the flow path width direction of the parallel flow path portion 38, and does not have protrusions 42 in the other flow path portions 40a, 40b, 40d, and 40e. In addition, the protrusions 42 are formed only in the central portions in the flow path length direction of the flow path portions 40c, and are not formed in the upstream portions and the downstream portions of the flow path portions 40c. The central portions in the flow path length direction of the flow path portions 40c are formed as turbulence portions 122 in which the protrusions 42 are formed, the portions on the upstream side of the turbulence portions 122 are formed as first laminar flow portions 124 which are laminar flow portions in which the protrusions 42 are not formed, and the portions on the downstream side of the turbulence portions 122 are formed as second laminar flow portions 126 in which the protrusions 42 are not formed. Note that the cross-sectional shape of the surface of the protrusion 42 exposed in the flow path portion 40c is the same as that of the first embodiment.

[0204] In the turbulence portion 122, a plurality of protrusions 42 are arranged in the flow path length direction. As shown in Figure 15 the present embodiment, the protrusion height dimension of the plurality of protrusions 42 arranged in the turbulence portion 122 increases as it approaches the central side in the flow path length direction. Thus, the protrusion height dimension of the plurality of protrusions 42 arranged in the length direction gradually increases toward the center, and then gradually decreases toward the downstream side from the center. Note that the plurality of protrusions 42 are arranged in the turbulence portion 122 so as to be spaced apart from each other in the flow path width direction. Figure 15In the cross-section along the length of the flow path shown, the shapes are similar to each other in this embodiment, but for example, the length of the base end (protruding base 45b) can be set to be constant, so that the shapes are different.

[0205] like Figure 14 , Figure 15 As shown, the plurality of protrusions 42 provided in the turbulent flow section 122 narrow in the flow path length direction as they move towards the center. The spacing between adjacent protrusions 42 in the central portion of the flow path length direction is narrower than that at the two ends. Therefore, after the spacing between adjacent protrusions 42 in the length direction gradually narrows towards the center, it gradually widens from the center towards the downstream side. It should be noted that in the flow path section 40c of this embodiment, the same number of protrusions 42 are provided on the upstream side and the downstream side relative to the center of the flow path length direction.

[0206] The upstream side of the first laminar flow section 124, which lacks protrusion 42, is connected to the inlet-side flow path section 128, which has a supply port 24, and the downstream side is connected to the turbulent flow section 122. The flow path length of the first laminar flow section 124 is smaller than that of the turbulent flow section 122. Figure 15 As shown, the bottom surface of the first laminar flow section 124 is formed as an inclined bottom surface 130 that slopes upward toward the downstream direction and approaches the lower surface of the cooling surface constituting member 12 as it moves downstream. Consequently, the cross-sectional area of ​​the flow path of the first laminar flow section 124 decreases as it moves downstream. The inclination angle of the inclined bottom surface 130 can vary in the flow path length direction and the flow path width direction (among the multiple flow path sections 40), but in this embodiment, it is set to a constant inclination angle and is formed by a plane that is inclined relative to the lower surface of the cooling surface constituting member 12. It should be noted that the lower surface of the cooling surface constituting member 12 is a plane that is approximately parallel to the cooling surface 16, which serves as the upper surface; therefore, the inclined bottom surface 130 is also inclined relative to the cooling surface 16.

[0207] The upstream side of the second laminar flow section 126, which does not have protrusions 42, is connected to the turbulent flow section 122, and the downstream side is connected to the outlet flow path section 132, which has a discharge port 28. The flow path length of the second laminar flow section 126 is smaller than that of the turbulent flow section 122. The second laminar flow section 126 extends along the flow path length with a substantially constant cross-section. It should be noted that the turbulent flow section 122, except for the protrusions 42, i.e., between adjacent protrusions 42, has a substantially constant cross-section similar to that of the second laminar flow section 126. Therefore, the lower surfaces of both the second laminar flow section 126 and the turbulent flow section 122 are formed as planes that extend substantially parallel to the lower surface of the cooling surface constituting member 12.

[0208] The inlet-side flow path portion 128 is provided on the upstream side of the parallel flow path portion 38, and the plurality of flow path portions 40 branch from the inlet-side flow path portion 128 and extend downstream. In addition, the outlet-side flow path portion 132 is provided on the downstream side of the parallel flow path portion 38, and the plurality of flow path portions 40 converge.

[0209] The volume of the inlet-side flow path portion 128 and the outlet-side flow path portion 132 of the present embodiment are different from each other. That is, the volume of the inlet-side flow path portion 128 is larger than that of the outlet-side flow path portion 132. In the present embodiment, the flow path depth dimension of the inlet-side flow path portion 128 is larger than that of the outlet-side flow path portion 132. Note that the flow path length dimension and the flow path width dimension of the inlet-side flow path portion 128 and the outlet-side flow path portion 132 can also be different from each other, respectively, but are substantially the same in the present embodiment.

[0210] According to the cooling heat exchanger 120 of the present embodiment, the protrusions 42 are provided only in the central portions in the width direction and the length direction in the parallel flow path portion 38, whereby in a case where the heat generation sites of the cooling target such as the battery pack, which overlap the cooling surface 16, are located in the central portions in the width direction and the length direction of the cooling surface 16, the cooling target can be efficiently cooled. In addition, by increasing the cooling performance of only the portions corresponding to the heat generation sites of the cooling target by the protrusions 42, it is possible to prevent a decrease in the local cooling performance caused by the heat generation of the cooling target, and it is possible to more uniformly cool the entire cooling target. Therefore, it is possible to effectively prevent deterioration caused by local high temperature of the cooling target.

[0211] In addition, in the present embodiment, the plurality of protrusions 42 arranged in the flow path length direction of the flow path portion 40c are formed so that the protrusion height dimension becomes larger toward the center in the flow path length direction. The higher the protrusion height of the protrusion 42, the stronger the stirring action of the heat medium by the protrusion 42, and therefore in the present embodiment, it is possible to more strongly obtain the effect of increasing the cooling performance by the stirring of the heat medium toward the center in the flow path length direction of the flow path portion 40c.

[0212] In addition, in the present embodiment, the plurality of protrusions 42 arranged in the flow path length direction of the flow path portion 40c are arranged so that the interval between the adjacent protrusions 42 becomes narrower toward the center in the flow path length direction. The narrower the interval between the protrusions 42, the stronger the stirring action of the heat medium by the protrusions 42, and therefore in the present embodiment, it is possible to more strongly obtain the effect of increasing the cooling performance by the stirring of the heat medium toward the center in the flow path length direction of the flow path portion 40c.

[0213] In the present embodiment, the turbulent flow portion 122 in which the protrusions 42 are formed in the flow path portion 40c is provided only in the central portion in the flow path length direction, and the first laminar flow portion 124 in which the protrusions 42 are not provided is provided on the upstream side of the turbulent flow portion 122, and the second laminar flow portion 126 in which the protrusions 42 are not provided is provided on the downstream side of the turbulent flow portion 122. Thus, in the upstream portion and the downstream portion other than the central portion in which the improvement of the cooling performance is to be achieved, the heat medium flows smoothly without being hindered by the protrusions 42.

[0214] The bottom surface of the first laminar flow portion 124 on the upstream side of the turbulent flow portion 122 is formed as an inclined bottom surface 130, and the flow path cross-sectional area decreases toward the downstream side. Thus, the flow rate of the heat medium flowing in the first laminar flow portion 124 increases toward the downstream side. Also, by causing the heat medium after the increase in the flow rate to flow into the turbulent flow portion 122, it is easier to cause the disturbance of the flow due to the protrusions 42, and it is possible to more favorably exert the effect of the improvement of the cooling performance due to the stirring action of the heat medium.

[0215] In the turbulent flow portion 122, the flow path cross section of the portion other than the protrusions 42 is substantially constant. Thus, in the portion in which the protrusions 42 are not provided, it is less likely to cause the change in the flow rate of the heat medium or the like due to the change in the flow path cross section, and it is easy to control the change in the flow of the heat medium due to the provision of the protrusions 42.

[0216] In the cooling heat exchanger 120 of the present embodiment, the volume of the inlet side flow path portion 128 is larger than the volume of the outlet side flow path portion 132. Therefore, for example, by making the flow path cross-sectional area of the flow path portions 74, 76 that constitute the parallel flow path portions 70, 72 connecting the inlet side flow path portion 128 and the outlet side flow path portion 132 decrease toward the downstream side, it is also possible to suppress the decrease in the flow rate of the heat medium on the downstream side of the flow path portions 74, 76.

[0217] Figure 16 、 Figure 17 A cooling heat exchanger 140 as an eighth aspect of the present application is shown. The protrusions 142 provided in the flow path portion 40 of the cooling heat exchanger 140 are constituted by first protrusions 142a and second protrusions 142b that are different in shape when viewed in the flow path length direction. Note that the protrusions 142 are also substantially V-shaped when viewed in the vertical direction, like the protrusions 42 of the seventh embodiment.

[0218] As Figure 16As shown, the protrusion height of the first protrusion 142a is smallest at the central portion in the flow path width direction of the flow path portion 40, and gradually increases towards both sides in the flow path width direction. In summary, the central portion of the first protrusion 142a in the flow path width direction is formed as a low protrusion 144 with a small protrusion height, and the two ends in the flow path width direction are formed as high protrusions 146 with large protrusion heights. The rate of change of the protrusion height of the first protrusion 142a can vary in the flow path width direction, but in this embodiment, it increases with a constant rate of change towards both sides in the flow path width direction, and the ridge 44 is formed as a straight line. In this embodiment, the two ends of the highest first protrusion 142a are continuously integrated with the side wall portion (outer peripheral fixed portion 20 or inner peripheral fixed portion 30) of the flow path portion 40, and the first protrusion 142a is continuously provided throughout the flow path width direction of the flow path portion 40.

[0219] like Figure 17 As shown, the protrusion height of the second protrusion 142b is largest at the center of the flow path width direction of the flow path portion 40, and gradually decreases towards both sides of the flow path width direction. In summary, the central portion of the second protrusion 142b in the flow path width direction is formed as a high protrusion 146 with a large protrusion height, while the two ends in the flow path width direction are formed as low protrusions 144 with small protrusion heights. The rate of change of the protrusion height of the second protrusion 142b can also vary in the flow path width direction, but in this embodiment, it decreases at a constant rate towards both sides of the flow path width direction, and the ridge 44 is a straight line. In this embodiment, the two ends of the lowest second protrusion 142b are integrally connected to the sidewall portion of the flow path portion 40, and the second protrusion 142b is continuously provided throughout the flow path width direction of the flow path portion 40.

[0220] Multiple first protrusions 142a and second protrusions 142b are arranged in the length direction of the flow path portion 40, and are positioned at different locations in the flow path length direction of the flow path portion 40. In this embodiment, the first protrusions 142a and second protrusions 142b are alternately arranged in an adjacent manner in the flow path length direction. Therefore, in the central portion of the flow path width direction of the flow path portion 40, the low protrusions 144 of the first protrusion 142a and the high protrusions 146 of the second protrusion 142b are alternately arranged in the flow path length direction. In addition, in the two end portions of the flow path width direction of the flow path portion 40, the high protrusions 146 and 146 of the first protrusion 142a and the low protrusions 144 and 144 of the second protrusion 142b are alternately arranged in the flow path length direction.

[0221] Further, the heat medium flowing in the flow path length direction of the flow path portion 40 is disturbed in flow and stirred by passing over the high projection portions 146 of the first projection 142a and the second projection 142b. In particular, the flow of the heat medium is more strongly disturbed by passing over the high projection portions 146 of the first projection 142a and the high projection portions 146 of the second projection 142b, and the effect of improvement in cooling performance due to stirring of the heat medium is exerted.

[0222] The heat medium avoids the high projection portions 146 of the first projection 142a and the high projection portions 146 of the second projection 142b, which have large flow resistance, and preferentially flows through the low projection portions 144 of the first projection 142a and the low projection portions 144 of the second projection 142b, which have small flow resistance. Thus, in the present embodiment, the high projection portions 146 of the first projection 142a and the low projection portions 144 of the second projection 142b are alternately arranged in the flow path length direction, and the low projection portions 144 of the first projection 142a and the high projection portions 146 of the second projection 142b are alternately arranged in the flow path length direction. Thus, the heat medium after passing through the low projection portions 144 of the first projection 142a flows toward the high projection portions 146 of the second projection 142b on the downstream side, and thus the stirring action of the heat medium by the high projection portions 146 of the second projection 142b is more strongly exerted. Further, the heat medium after passing through the low projection portions 144 of the second projection 142b flows toward the high projection portions 146 of the first projection 142a on the downstream side, and thus the stirring action of the heat medium by the high projection portions 146 of the first projection 142a is more strongly exerted. In this way, by alternately arranging the first projection 142a and the second projection 142b in the flow path length direction of the flow path portion 40, the effect of improvement in cooling performance based on the stirring action of the heat medium and the like can be advantageously obtained.

[0223] Note that the first projection 142a and the second projection 142b are preferably alternately arranged in the flow path length direction, but for example, a plurality of first projections 142a can be arranged adjacent to each other in the flow path length direction, or a plurality of second projections 142b can be arranged adjacent to each other in the flow path length direction. Further, the number of the first projections 142a and the second projections 142b can be different from each other. Further, the heights of the low projection portions 144 of the first projection 142a and the second projection 142b can be different from each other, and the heights of the high projection portions 146 of the first projection 142a and the second projection 142b can be different from each other.

[0224] 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 number of flow path portions 40 constituting the parallel flow path portion 38 is not particularly limited, and can be two or more. In addition, the plurality of flow path portions 40 constituting the parallel flow path portion 38 can be arranged side by side, and need not be strictly arranged in parallel, but can be arranged in a wavy manner or can be inclined to each other. As such, the flow direction of the heat medium in the plurality of flow path portions 40 constituting the parallel flow path portion 38 is not limited to the case where the flow directions are strictly the same, but can be the case where the heat medium flows in the same direction as a whole. Specifically, for example, in the adjacent flow path portions 40 constituting the parallel flow path portion 38, even if the flow directions of the heat medium are relatively inclined within a range of 15 degrees or less, the flow directions can be considered the same.

[0225] The specific shape of the protrusion is not particularly limited, and can be, for example, a point-like semispherical shape, a conical shape, a truncated conical shape, a columnar shape, or the like. The protrusion can not necessarily be provided to the entire flow path width of the flow path portion 40. The protrusion is preferably V-shaped when viewed from above, as in the above-described embodiment, but can extend orthogonally with respect to the flow path length direction of the flow path portion 40, or can extend in a one-sided slip manner inclined to one direction. In addition, in the case of the protrusion that is V-shaped when viewed from above, in the above-described embodiment, the protrusion is formed in a V shape inclined to the downstream side from the center in the front-rear direction toward both ends, but can be formed in a V shape inclined to the upstream side from the center in the front-rear direction toward both ends (inverted V shape). In addition, the side surfaces on both sides in the flow path length direction of the protrusion need not necessarily be constituted by inclined surfaces, but can be constituted by flat surfaces orthogonal to the flow path length direction, stepped surfaces, or the like.

[0226] For example, the protrusion 150 shown in FIG. 15 can be used. That is, the protrusion 150 is provided such that the curvature radius of the protrusion top portion 152 is large, and the side surface on the upstream side, that is, the first inclined surface 154 as the upstream inclined portion and the side surface on the downstream side, that is, the second inclined surface 156 as the downstream inclined portion are both constituted by curved surfaces, and the protrusion top portion 152 is connected to the bottom surface of the flow path portion 40 in a manner in which there is no corner portion and the connection is smooth. Thus, the entire profile of the protrusion 150 in the flow path length direction is a continuous curved shape. In addition, in the protrusion 150 of FIG. 15, the curvature radius of the protrusion top portion 152 in the circular arc shape in the cross section in the flow path length direction is preferably 0.7 times or more, and more preferably 1 time or more, with respect to the length dimension L of the protrusion base portion 45b. In addition, the inclination angle a of the first inclined surface 154 of the present embodiment with respect to the bottom surface of the flow path portion 40 is 25 degrees or less, and the inclination angle β of the second inclined surface 156 of the present embodiment is 25 degrees or less. In summary, the protrusion 150 of the present embodiment and the protrusion 42 shown in the first embodiment (refer to FIG. 2) are different in that the protrusion top portion 152 is constituted by a curved surface, but the inclination angles a and β of the first inclined surface 154 and the second inclined surface 156 are the same. Figure 18 Figure 5 ​​Figure 5 In contrast, in a cross section in the flow path length direction, the protrusion 150 is formed in a flat shape in which the ratio of the protrusion height dimension to the length dimension L of the protrusion base 45b is small. According to such a protrusion 150, the rate of change in the flow path cross-sectional area caused by the protrusion 150 is small, and thus the pressure loss when the heat medium passes over the protrusion 150 can be suppressed, and thus a less expensive pump with relatively low performance can be used to circulate the heat medium.

[0227] The protrusions do not necessarily need to be continuously provided throughout the entire flow path width direction of the flow path portion, but the width dimension of the protrusions in the flow path width direction is preferably 50% or more, and more preferably 70% or more, of the flow path width dimension of the flow path portion. Thus, the flow that bypasses the protrusions is restricted, and the flow that passes over the protrusions is easily generated, and thus the effect of disturbing the flow of the heat medium by the protrusions can be effectively exerted.

[0228] The plurality of protrusions can also be composed of a plurality of kinds that differ in shape, size, and the like. According to such a difference in the shape, size, and the like of the protrusions, regions in which the effect of disturbing the flow of the heat medium by the protrusions differs can also be set.

[0229] Specifically, for example, in the cooling heat exchanger 10 of the first embodiment, the protrusion height dimension of the protrusions 42 provided in the flow path portion 40a can also be made larger than the protrusion height dimension of the protrusions 42 provided in the flow path portion 40e. Thus, the effect of disturbing the flow of the heat medium in the flow path portion 40a in which the protrusions 42 with a large protrusion height dimension are provided and the effect of disturbing the flow of the heat medium in the flow path portion 40e in which the protrusions 42 with a small protrusion height dimension are provided can also be made different from each other, and regions in which the effects of disturbing the flow of the heat medium differ from each other can be set in the flow path portion 40a and the flow path portion 40e. In addition, in a case in which a plurality of protrusions 42 are provided in one flow path portion 40, by making the protrusion height dimensions of these plurality of protrusions 42 different, a plurality of regions in which the effect of disturbing the flow of the heat medium differs in one flow path portion 40 can also be set in the flow path length direction. That is, by making the protrusion height dimension of the protrusions 42 gradually larger toward the downstream side, the effect of disturbing the flow of the heat medium can also be exerted more strongly on the downstream side than on the upstream side.

[0230] In addition, for example, if a wide protrusion that is provided throughout the entire flow path width of the flow path portion and a narrow protrusion that is provided only in a portion of the flow path width in the flow path portion are combined, the effect of disturbing the flow of the heat medium by the protrusions can be obtained more greatly in the region in which the wide protrusion is formed than in the region in which the narrow protrusion is formed.

[0231] Note that the "region in which the effects of disturbing the flow of the heat medium differ" and the "particular region in which the cross-sectional shape of the flow path portion is changed to disturb the flow of the heat medium" are preferably grasped as a length region in which the plurality of protrusions or the cross-sectional shape of the flow path portion repeatedly changes, for example, in a predetermined regularity. The predetermined regularity described herein is not limited to, for example, "a manner in which the same protrusion is formed at a certain interval", "a manner in which the same change in the cross-sectional shape of the flow path is provided at a certain interval", but includes "a protrusion, an interval, and a period of the cross-sectional shape of the flow path that change regularly" in which the interval of the protrusion or the period of the change in the cross-sectional shape of the flow path gradually narrows in the flow path direction, and / or "a protrusion, a shape, and a size of the cross-sectional shape of the flow path that change regularly" in which the protrusion or the cross-sectional shape of the flow path gradually increases in the flow path direction. In addition, the "length region in which the plurality of protrusions or the cross-sectional shape of the flow path portion repeatedly changes in the predetermined regularity" described above is preferably restored to the constant basic cross-sectional shape (including the size) of the flow path portion between the changes in the cross-sectional shape of the flow path portion between the changes. Note that the change in the cross-sectional shape of the flow path portion is not limited to the protrusion, and for example, a recess can be provided, and the entire periphery can be narrowed, and the like.

[0232] In addition, the "region in which the effects of disturbing the flow of the heat medium differ due to the protrusions" can be at least two, and one of the plurality of regions can be a region in which there is no protrusion. The plurality of regions compared as the "region in which the effects of disturbing the flow of the heat medium differ due to the protrusions" are preferably regions of the same flow path length, but for example, can be regions in which the flow path lengths are aligned based on the shortest flow path length of the plurality of regions compared. Similarly, the "particular region in which the cross-sectional shape of the flow path portion is changed to disturb the flow of the heat medium" can be recognized by providing at least one particular region, and the presence of the particular region in which the cooling efficiency is adjusted compared to the other regions, and the place, the number, the length, and the like of the particular region are not limited.

[0233] The position, the number (the arrangement density), the shape, the size, and the like of the protrusion 42 described in each of the embodiments described above are merely examples, and are appropriately set, for example, in consideration of the temperature distribution of the battery group 52, the amount of heat generated by the battery group 52, the flow direction of the heat medium, and the like. Specifically, for example, in the case of cooling the battery group in which the terminal portion 54 is provided to the central portion in the front-rear direction, by arranging the protrusion 42 in a manner in which the protrusion 42 of the flow path portion 40c located at the center in the front-rear direction is the most, and the protrusion 42 of the flow path portion 40a and the flow path portion 40e located at both ends in the front-rear direction is the least, the front-rear central portion of the battery group in which the amount of heat generated is large can be effectively cooled.

[0234] In the above-described embodiment, the structure in which a small number of protrusions 42 are provided sparsely with respect to the parallel flow path portions 38 is exemplified, but for example, the protrusions 42 can be arranged substantially uniformly throughout substantially the entire parallel flow path portions 38, and portions in which the protrusions 42 are not provided can be locally provided in the parallel flow path portions 38. Further, for example, a plurality of protrusions that differ in the effect of disturbing the flow of the heat medium due to differences in shape or size can be provided throughout the entire parallel flow path portions 38.

[0235] In the above-described embodiment, the structure in which the protrusions 42 are separated downward from the cooling surface constituting member 12, and the narrow flow path portions 50 are formed between the protrusions 42 and the cooling surface constituting member 12 is exemplified, but for example, the protrusions 42 can locally abut against the cooling surface constituting member 12.

[0236] The narrow flow path portions 50 are preferably, as exemplified in the above-described embodiment, smaller in flow path cross-sectional area as they tend toward the downstream side in the flow direction of the heat medium, but for example, the flow path cross-sectional area of the narrow flow path portion on the downstream side can be made larger than that of the narrow flow path portion on the upstream side at least in some portions. Further, the flow path cross-sectional area of all of the narrow flow path portions can be made substantially constant. Further, the flow path cross-sectional areas of a plurality of narrow flow path portions that are provided in parallel at the same position in the flow direction of the heat medium can be different from each other.

[0237] In the above-described embodiment, an example in which the flow path cross-sectional areas of the narrow flow path portions 50 are made different depending on the heights of the protrusions 42 is shown, but for example, a protruding portion that protrudes toward the lower surface can be provided in the portion of the cooling surface constituting member 12 that corresponds to the protrusion 42, and the flow path cross-sectional area of the narrow flow path portion that is formed between the protrusion 42 and the protruding portion that is inserted into the groove 32 can be adjusted. In this case, by making the protruding heights of the plurality of protruding portions of the cooling surface constituting member 12 different, it is also possible to make the flow path cross-sectional areas of the narrow flow path portions different while making the protruding heights of the protrusions 42 constant. Further, for example, the height position of the protruding tip end of the protrusion 42 can be changed in the extension direction of the ridge line 44 or the like, and the separation distance between the protrusion 42 and the cooling surface constituting member 12 can be changed, whereby it is also possible to make the maximum protruding height of the protrusion 42 constant, and adjust the flow path cross-sectional area of the narrow flow path portion by the height and width of the portion of the protrusion 42 that deviates from the maximum protruding portion.

[0238] Further, the flow path lengths of the narrow flow path portions provided on the plurality of protrusions 42 need not be constant, and can be appropriately set respectively. For example, by making the flow path lengths of the narrow flow path portions different, it is also possible to adjust the flow resistances of the heat medium with respect to each other.

[0239] For example, the cooling surface constituting member 12 can also be made of synthetic resin, and the flow path member 14 can also be made of metal. Note that the cooling surface constituting member 12 made of synthetic resin is preferably formed of a thermally conductive synthetic resin obtained by mixing a thermally conductive filler such as alumina, silica, silicon carbide, or the like in a synthetic resin material such as polyphenylene sulfide (PPS), polyamide, polypropylene, polybutylene terephthalate (PBT), or the like, in order to ensure a high heat transfer coefficient.

[0240] The cooling target is not necessarily limited to a battery for an electrically powered vehicle, and can be, for example, a stationary battery for industrial use or the like. Also, in the first embodiment described above, an example is shown in which a plurality of battery packs 52 are arranged on the cooling surface 16 of one cooling heat exchanger 10, but for example, one battery pack 52 can be arranged on the cooling surface 16 of one cooling heat exchanger 10. Also, for example, one battery pack 52 can be arranged across a plurality of cooling heat exchangers 10.

Claims

1. A cooling heat exchanger (10, 60, 80, 90, 100, 110, 120, 140) in which a cooling flow path (36, 68) in which a cooling medium flows is formed inside, and a cooling object overlapping a cooling surface (16) is cooled, wherein the cooling flow path (36, 68) is provided with a parallel flow path portion (38, 70, 72) composed of a plurality of flow path portions (40, 74, 76) extending adjacent to and in parallel with each other, the flow direction of the cooling medium in the plurality of flow path portions (40, 74, 76) being the same, a plurality of protrusions (42, 142, 150) that disturb the flow of the cooling medium are formed in the parallel flow path portion (38, 70, 72), regions in which the effect of disturbing the flow of the cooling medium by the protrusions (42, 142, 150) is different from each other are provided in the parallel flow path portion (38, 70, 72). The regions in which the effect of disturbing the flow of the cooling medium is different from each other and which are provided at different positions in the flow direction of the cooling medium in at least one of the flow path portions (40, 74, 76) that compose the parallel flow path portion (38, 70, 72) are provided so that the further downstream the region is, the stronger the effect of disturbing the flow of the cooling medium by the protrusions (42) is.

2. The cooling heat exchanger (10, 60, 80, 90, 100, 110, 120, 140) according to claim 1, wherein, The protrusions (42) are provided throughout the entire flow path width of the flow path portions (40) that compose the parallel flow path portion (38), and narrow flow path portions (50) in which the cooling medium flows are provided on the protruding tip side of the protrusions (42).

3. The cooling heat exchanger (10, 80, 90, 110) according to claim 2, wherein 5. The cooling heat exchanger (10) according to claim 4, wherein 4. The cooling heat exchanger (10) according to claim 1 or 2, wherein a plurality of the narrow flow path portions (50) are formed by the plurality of protrusions (42), the flow path cross-sectional area of at least one of the narrow flow path portions (50) is different from the flow path cross-sectional area of the other narrow flow path portions (50). The flow path cross-sectional area of the plurality of narrow flow path portions (50) provided in one of the flow path portions (40) decreases from the upstream side toward the downstream side of the flow path portion (40). The protrusions (42) have a ridge line (44) that extends obliquely with respect to the flow path length direction of the flow path portion (40).

6. The cooling heat exchanger (10) according to claim 5, wherein 8. The cooling heat exchanger (10) according to claim 1 or 2, wherein 7. The cooling heat exchanger (10) according to claim 5, wherein the protrusions (42) are provided locally with respect to the parallel flow path portion (38), the regions in which the effect of disturbing the flow of the cooling medium is different from each other are composed of a region in which the protrusions (42) are formed and a region in which the protrusions (42) are not formed.

9. The cooling heat exchanger (10) according to claim 1 or 2, wherein ​ ​ The cooling heat exchanger (10) is provided in a laminated structure in which a cooling surface constituting member (12) constituting the cooling surface (16) and a flow path member (14) provided with a groove (32) are overlapped, the groove (32) of the flow path member (14) being covered by the cooling surface constituting member (12) to constitute the cooling flow path (36), The plurality of protrusions (42) protrude from the flow path member (14) toward the cooling surface constituting member (12) side.

10. The cooling heat exchanger (10, 60, 80, 90, 100, 110, 120, 140) according to claim 1 or 2, wherein, The regions in which the flow of the heat medium is disturbed are provided in at least one group of adjacent flow path portions (40, 74, 76) in the parallel flow path portions (38, 70, 72) so as to have different effects.

11. The cooling heat exchanger (10, 60, 80, 90, 100, 110, 120, 140) according to claim 1 or 2, wherein, The cooling object is a battery.

12. The cooling heat exchanger (10, 60, 80, 90, 100, 110, 120, 140) according to claim 1 or 2, wherein, The regions in which the flow of the heat medium is disturbed are provided by differences in the intervals of the plurality of protrusions (42, 142, 150) in the flow direction of the heat medium.

13. The cooling heat exchanger (10, 60, 80, 90, 100, 110, 120, 140) according to claim 1 or 2, wherein, The regions in which the flow of the heat medium is disturbed are provided by differences in the heights of the plurality of protrusions (42, 142, 150).

14. The cooling heat exchanger (10) according to claim 7, wherein, The protrusions (42) extend in a V-shape inclined toward both sides in the flow path width direction of the flow path portions (40) in the flow path length direction.

15. The cooling heat exchanger (10) according to claim 1 or 2, wherein The protrusions (42) have ridge lines (44) extending obliquely with respect to the flow path length direction of the flow path portions (40).

16. The cooling heat exchanger (10) according to claim 15, wherein The protrusions (42) extend in a V-shape inclined toward both sides in the flow path width direction of the flow path portions (40) in the flow path length direction.

17. The cooling heat exchanger (10) according to claim 8, wherein, The protrusions (42) have ridge lines (44) extending obliquely with respect to the flow path length direction of the flow path portions (40).

18. The cooling heat exchanger (10) according to claim 17, wherein The protrusions (42) extend in a V-shape inclined toward both sides in the flow path width direction of the flow path portions (40) in the flow path length direction.

19. The cooling heat exchanger (10) according to claim 10, wherein, The protrusions (42) have ridge lines (44) extending obliquely with respect to the flow path length direction of the flow path portions (40).

20. The cooling heat exchanger (10) according to claim 19, wherein The protrusions (42) extend in a V-shape inclined toward both sides in the flow path width direction of the flow path portions (40) in the flow path length direction.

21. The cooling heat exchanger (100) according to claim 1 or 2, wherein The protrusions (42) are provided only in the central portion in the flow path length direction of the flow path portions (40).

22. The cooling heat exchanger (120) according to claim 1 or 2, wherein The protrusions (42) are provided only in the central portion in the flow path width direction of the flow path portions (40) constituting the parallel flow path portions (38).

23. The cooling heat exchanger (120) according to claim 1 or 2, wherein The plurality of protrusions (42) are arranged in the flow path length direction of the flow path portions (40), and the intervals of the protrusions (42) located in the central portion in the flow path length direction of the flow path portions (40) are smaller than the intervals of the protrusions (42) located in both side portions in the flow path length direction of the flow path portions (40).

24. The cooling heat exchanger (140) according to claim 1 or 2, wherein The width dimension of the protrusions (150) in the flow path width direction of the flow path portions (40) is 50% or more of the flow path width dimension of the flow path portions (40).

25. The cooling heat exchanger (10, 60, 80, 90, 100, 110, 120, 140) according to claim 1 or 2, wherein, The flow path width dimension of the flow path portions (40, 74, 76) is within a range of 0.3 to 30 times the width dimension of the partition wall portions (30) separating adjacent flow path portions (40, 74, 76).

26. The cooling heat exchanger (10, 60, 80, 90, 100, 110, 120, 140) according to claim 1 or 2, wherein, The protrusion height dimension of the protrusions (42, 142, 150) is in the range of 0.1 to 1.3 times the width dimension of the protrusions (42, 142, 150).

27. The cooling heat exchanger (120) according to claim 1 or 2, wherein A laminar flow portion (124) in which the protrusions (42) are not provided is provided in the flow path portion (40), The flow path cross-sectional area of the flow path portion (40) in the laminar flow portion (124) decreases toward the downstream.

28. The cooling heat exchanger (120) according to claim 27, wherein The flow path length of the laminar flow portion (124) is shorter than the flow path length of a turbulent flow portion (122) in which the protrusions (42) are formed in a portion deviating from the laminar flow portion (124).

29. The cooling heat exchanger (120) according to claim 28, wherein In the turbulent flow portion (122) in which the protrusions (42) are formed in a portion deviating from the laminar flow portion (124) in the flow path portion (40), a portion other than the protrusions (42) is formed as a constant cross section.

30. The cooling heat exchanger (120) according to claim 1 or 2, wherein An inlet-side flow path portion (128) is provided on the upstream side of the parallel flow path portion (38), and the plurality of flow path portions (40) branch from the inlet-side flow path portion (128) and extend toward the downstream, and an outlet-side flow path portion (132) in which the plurality of flow path portions (40) converge is provided on the downstream side of the parallel flow path portion (38), The volume of the inlet-side flow path portion (128) is larger than the volume of the outlet-side flow path portion (132).

31. The cooling heat exchanger (10, 60, 80, 90, 100, 110, 120, 140) according to claim 13, wherein, The height of the plurality of protrusions (42, 142, 150) arranged in the flow path length direction in the flow path portion (40, 74, 76) increases toward the downstream, and the regions in which the protrusions (42, 142, 150) have different effects on disturbing the flow of the heat medium are provided in the flow path length direction of the flow path portion (40, 74, 76).

32. The cooling heat exchanger (10, 60, 80, 90, 110) according to claim 31, wherein The interval of the plurality of protrusions (42) arranged in the flow path length direction in the flow path portion (40, 74, 76) narrows toward the downstream, and the regions in which the protrusions (42) have different effects on disturbing the flow of the heat medium are provided in the flow path length direction of the flow path portion (40, 74, 76).

33. The cooling heat exchanger (10, 60, 80, 90, 110) according to claim 12, wherein, The interval of the plurality of protrusions (42) arranged in the flow path length direction in the flow path portion (40, 74, 76) narrows toward the downstream, and the regions in which the protrusions (42) have different effects on disturbing the flow of the heat medium are provided in the flow path length direction of the flow path portion (40, 74, 76).

34. The cooling heat exchanger (140) according to claim 1 or 2, wherein The protrusion height of the protrusion (142) varies in the flow path width direction of the flow path portion (40), and either one of a low protrusion portion (144) having a low protrusion height and a high protrusion portion (146) having a high protrusion height is located at a central portion in the flow path width direction of the protrusion (142), and the other one of the low protrusion portion (144) and the high protrusion portion (146) is located at both end portions in the flow path width direction of the protrusion (142).

35. The cooling heat exchanger (140) according to claim 34, wherein A plurality of the protrusions (142) are arranged in the flow path length direction of the flow path portion (40), The plurality of protrusions (142) are configured by alternately arranging first protrusions (142a) and second protrusions (142b) in the flow path length direction of the flow path portion (40), the first protrusions (142a) being provided with the low protrusion portions (144) at the central portions in the flow path width direction of the flow path portion (40) and the high protrusion portions (146) at both end portions, and the second protrusions (142b) being provided with the high protrusion portions (146) at the central portions in the flow path width direction of the flow path portion (40) and the low protrusion portions (144) at both end portions.

36. The cooling heat exchanger (10) according to claim 1 or 2, wherein The protrusion (42) is formed in a cross-sectional shape in which the tip end is tapered toward the protrusion tip end in the flow path length direction of the flow path portion (40), and a protrusion tip portion (45a) in an arc shape, an upstream inclined portion (46) that extends obliquely toward the upstream side of the flow path portion (40) from the protrusion tip portion (45a) toward a bottom surface side of the flow path portion (40), that is, a protrusion base portion (45b), and a downstream inclined portion (48) that extends obliquely toward the downstream side from the protrusion tip portion (45a) toward the protrusion base portion (45b) are continuously provided without corners and smoothly.

37. The cooling heat exchanger (10) according to claim 36, wherein In a cross section in the flow path length direction of the flow path portion (40), the radius of curvature of the protrusion tip portion (45a) is in a range of 0.05 to 1.5 times the length dimension of the protrusion base portion (45b), and in a cross section in the flow path length direction of the flow path portion (40), the inclination angle of the upstream inclined portion (46) with respect to the bottom surface of the flow path portion (40) is in a range of 20° to 70°.

38. The cooling heat exchanger (10) according to claim 36, wherein In a cross section in the flow path length direction of the flow path portion (40), the inclination angle of the upstream inclined portion (46) with respect to the bottom surface of the flow path portion (40) is 25° or less.

39. The cooling heat exchanger (10, 60, 80, 90, 100, 110, 120, 140) according to claim 1 or 2, wherein, The protrusions (42, 142, 150) extend integrally over the flow path width of the flow path portion (40, 74, 76) and continuously with the side wall portions of the flow path portion (40, 74, 76) at both end portions.

40. The cooling heat exchanger (10, 60, 80, 90, 100, 110, 120, 140) according to claim 39, wherein, The protrusions (42, 142, 150) are formed in a V shape that extends obliquely toward the downstream side of the cooling flow path (36, 68) toward both sides in the flow path width direction of the cooling flow path (36, 68).

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