Cooling heat exchanger

Abstract

The utility model provides a new cooling heat exchanger, it is with simple structure to realize the double -sided cooling structure with the cooling surface in both sides, and can stably get excellent cooling performance. A kind of cooling heat exchanger (10), cooling flow path (28) for the flow of cooling heat medium is formed in inside, cooling object (62) overlapping with the cooling surface (32) arranged on surface is cooled, hollow outer wall member (12) with cooling flow path (28) in inside is provided, a pair of cooling wall portions (30,30) with cooling surface (32) in surface are provided in mutually opposite portion in outer wall member (12), in the internal area (28) of outer wall member (12), internal fin (34) of plate shape is arranged, which divides internal area (28) into two parts in the opposite direction of a pair of cooling wall portions (30,30), first protrusion (48a) and second protrusion (48b) projecting in each one side surface are integrally formed in internal fin (34).

Description

TECHNICAL FIELD

[0001] The present application relates to a cooling heat exchanger used in cooling of a cooling object such as a battery for an electric vehicle. BACKGROUND

[0002] Conventionally, a cooling heat exchanger used in cooling of a battery, an inverter is known. For example, as disclosed in Japanese Patent No. 7000777 (Patent Literature 1), the cooling heat exchanger has a structure in which a cooling flow path through which a heat medium flows is formed inside an outer wall member. Further, it is formed so that a cooling object such as a battery is overlapped with cooling surfaces provided on both surfaces, and the cooling object is cooled by heat exchange between the cooling object and the heat medium.

[0003] In addition, the cooling heat exchanger of Patent Literature 1 is formed so that a pair of cooling wall portions constituting the outer wall member are arranged in opposition to each other, and cooling surfaces are provided on both outer surfaces of the pair of cooling wall portions, and a double-sided cooling structure capable of cooling a cooling object overlapped with the cooling surfaces provided on both surfaces.

[0004] PRIOR ART DOCUMENTS

[0005] PATENT LITERATURE

[0006] Patent Literature 1: Japanese Patent No. 7000777 SUMMARY

[0007] PROBLEMS TO BE SOLVED BY THE INVENTION

[0008] However, in Patent Literature 1, in order to obtain a large contact area with the heat medium and improve the cooling efficiency of the cooling surface based on the heat medium, an inner fin is housed inside the outer wall member. In Patent Literature 1, in order to achieve efficient double-sided cooling, the inner space of the outer wall member is divided in the direction in which the pair of cooling wall portions oppose each other by an intermediate plate, and the inner fins are arranged on both sides of the intermediate plate.

[0009] However, in the structure of Patent Literature 1, since the intermediate plate and two inner fins are required, there is a problem that the number of components increases and the structure becomes complex.

[0010] In addition, the heat medium flowing only near the cooling object becomes high temperature by heat exchange with the cooling object, and thus there is a risk that the cooling performance based on heat exchange with the heat medium flowing near the cooling object decreases. Furthermore, the heat medium flowing away from the cooling object indirectly cools the cooling object via the intermediate plate and the inner fins, and thus there is a risk that the heat exchange efficiency easily decreases compared to the heat medium flowing near the cooling object, and the heat capacity of the entire heat medium cannot be effectively utilized, and the cooling performance decreases.

[0011] The cooling heat exchanger of the present application is capable of achieving a double-sided cooling structure with a simple structure, and has excellent cooling performance.

[0012] Means for solving the problem

[0013] Hereinafter, preferred modes for implementing the present application will be described, but each mode described below is an example, and can be appropriately combined with each other, and can be independently recognized and adopted within a possible range, and can be appropriately combined with any of the components described in other modes. Therefore, in the present application, it is not limited to the modes described below, and various other modes can be implemented.

[0014] The first mode is a cooling heat exchanger in which a cooling flow path for flowing a cooling heat medium is formed inside, and a cooling object overlapping a cooling surface provided on a surface is cooled, in which the cooling heat exchanger is provided with a hollow outer wall member having the cooling flow path inside, a pair of cooling wall portions having the cooling surface on the surface are provided at mutually opposite portions in the outer wall member, a plate-shaped inner fin that divides an inner region of the outer wall member into two portions in the opposite direction of the pair of cooling wall portions is provided in the inner region, and a first protrusion and a second protrusion protruding from each of the surfaces are integrally formed in the inner fin.

[0015] According to the cooling heat exchanger formed in the structure according to the present mode, by dividing the cooling flow path into two portions by one inner fin in the opposite direction of the pair of cooling wall portions, a cooling flow path suitable for double-sided cooling can be achieved with a simple structure. In addition, for example, by providing the inner fin in the inner region of the outer wall member, the contact area with the heat medium becomes large, and therefore the pair of cooling wall portions is also cooled by indirect heat exchange with the heat medium through the inner fin, and the cooling performance of the cooling object is improved.

[0016] Further, first and second protrusions protruding from each of the faces are integrally formed in the inner fins. Therefore, the heat medium flowing on both sides of the inner fins is guided to the cooling wall portion side, etc. by changing the flow direction thereof through the first and second protrusions, for example, by generation of a vortex, turbulence, separation of the heat medium from the inner fins, etc., thereby agitating the heat medium. Also, the heat medium flowing at a position close to the cooling wall portion heated by heat exchange with the cooling object and the heat medium flowing at a position away from the cooling wall portion maintained at a relatively low temperature (a position close to the inner fins) are agitated, and these heat media having a temperature difference are mixed. Thus, a decrease in heat exchange efficiency with the cooling object due to a local temperature rise of the heat medium is prevented, and the heat capacity of the entire heat medium is effectively utilized for cooling of the cooling object, thereby achieving an improvement in cooling performance.

[0017] The first and second protrusions are provided protruding from both faces of the inner fins that partition the cooling flow path, and thus agitation effects based on the protrusions can be obtained in the flow paths on both sides of the inner fins with a small number of components and manufacturing steps.

[0018] The second aspect is based on the cooling heat exchanger of the first aspect described above, and the cooling flow path includes a parallel flow path portion composed of a plurality of flow path portions that are adjacent to each other and extend in parallel in the flow path width direction partitioned by the inner fins, and the flow directions of the heat medium in the plurality of flow path portions that constitute the parallel flow path portion are the same.

[0019] According to the cooling heat exchanger formed in accordance with the present aspect, by forming the parallel flow path portion composed of a plurality of flow path portions in parallel by the inner fins, the inner fins can also function as a flow regulating fin that regulates the flow of the heat medium. Further, the flow path cross-sectional area of each flow path portion can be easily adjusted and set by the inner fins, and by adjusting the flow rate and flow velocity of the heat medium in each flow path portion, the cooling performance as the object can be achieved.

[0020] The inner fins constitute wall portions that partition adjacent flow path portions, and thus the contact area of the inner fins with the heat medium becomes larger, and indirect cooling via the cooling surface of the inner fins is more efficiently achieved.

[0021] The size in the flow path width direction of the parallel flow path portion composed of a plurality of flow path portions can be adjusted by the number of flow path portions, and thus, for example, by providing the parallel flow path portion at a position corresponding to the cooling surface, the flow path cross-sectional area of each flow path portion can be appropriately set, and the size of the cooling surface in the flow path width direction can be set with greater freedom.

[0022] In the plurality of flow path portions that constitute the parallel flow path portion, the flow directions of the heat medium are set to be the same as each other, and thus a decrease in cooling performance due to heat exchange between adjacent flow path portions is less likely to occur.

[0023] The third aspect is based on the cooling heat exchanger according to any one of the first to third aspects, wherein the outer wall member is formed in a structure in which a first member constituting one of the pair of cooling wall portions and a second member constituting the other of the pair of cooling wall portions are overlapped with each other in the direction in which the pair of cooling wall portions face each other, and the inner fin is disposed between the facing surfaces of the first and second members.

[0024] According to the cooling heat exchanger formed in the structure according to the present aspect, by disposing the inner fin between the overlapped surfaces of the first and second members, the inner fin can be simply housed and disposed in the inner region of the outer wall member.

[0025] The fourth aspect is based on the cooling heat exchanger according to any one of the first to third aspects, wherein the inner fin has a sawtooth-shaped or wavy cross section that is folded back in the direction in which the pair of cooling wall portions face each other, and the first and second protrusions are formed between the top portions of adjacent folds in the inner fin.

[0026] According to the cooling heat exchanger formed in the structure according to the present aspect, the inner region of the outer wall member can be divided by the inner fin of a simple shape. In particular, by forming the inner fin in a sawtooth-shaped or wavy cross section, a plurality of flow path portions separated by the inner fin can also be formed.

[0027] Further, by providing the inner fin with a sawtooth-shaped or wavy cross section that is folded back, the deformation rigidity of the inner fin can be easily ensured, and, for example, thinning of the inner fin can also be achieved. Moreover, by forming the first and second protrusions between the top portions of the folds in the inner fin, the deformation rigidity of the inner fin can be further improved.

[0028] The fifth aspect is based on the cooling heat exchanger according to any one of the first to third aspects, wherein the inner fin includes an intermediate partition portion that is disposed separately from both of the pair of cooling wall portions in the outer wall member, divides the facing surfaces of the pair of cooling wall portions into two portions in the direction in which the pair of cooling wall portions face each other, and has the first and second protrusions formed therein, and the inner fin includes a partition wall portion that protrudes to both sides from the intermediate partition portion toward the pair of cooling wall portions, and by the partition wall portion, the inner region of the outer wall member is divided into a plurality of flow path portions in the flow path width direction of the cooling flow path.

[0029] According to the cooling heat exchanger formed in the structure according to the present aspect, by one inner fin, the inner region of the outer wall member is not only divided in the direction in which the pair of cooling wall portions face each other, but also divided in the flow path width direction of the cooling flow path to constitute a plurality of flow path portions. Thus, the number of flow path portions, the flow path cross-sectional area, and the like can be simply set with a large degree of freedom by the interval and number of the partition wall portions provided in one inner fin.

[0030] The first protrusion and the second protrusion are provided in the intermediate partition portion, so that a protrusion-based turbulence promotion effect is exerted in each flow path region, and excellent cooling performance is achieved.

[0031] The sixth aspect is the cooling heat exchanger according to any one of the first to fifth aspects, wherein the first protrusion and the second protrusion are formed in a V-shape on the surface of the inner fin, and are formed to be narrower in width toward the upstream side of the cooling flow path.

[0032] According to the cooling heat exchanger formed in the structure according to the present aspect, when the heat medium passes over the V-shaped first protrusion or the second protrusion, the heat medium flows in a direction in which the flow path width direction is inclined toward the center of the V-shape in a manner in which the flow resistance is reduced. Thus, the flows of the heat medium that have passed over the first protrusion or the second protrusion converge, and a vortex or turbulence occurs on the downstream side of the first protrusion or the second protrusion. As a result, the heat medium is stirred more efficiently, and an improvement in cooling performance based on a reduction in the temperature difference of the heat medium (uniformization of the temperature) is achieved.

[0033] The seventh aspect is the cooling heat exchanger according to any one of the first to sixth aspects, wherein the inner fin is arranged locally in the flow path length direction of the cooling flow path.

[0034] According to the cooling heat exchanger formed in the structure according to the present aspect, for example, by removing the inner fin in a portion in which two-sided cooling is not required, weight reduction and cost reduction are achieved. The inner fin provided with the first protrusion and the second protrusion is arranged in a portion in which two-sided cooling is required, and thus high cooling performance based on stirring of the heat medium can be expected.

[0035] The eighth aspect is the cooling heat exchanger according to any one of the first to seventh aspects, wherein in the cooling flow path, regions in which effects of disturbing the flow of the heat medium by at least one of the plurality of first protrusions and the plurality of second protrusions are different from each other are provided.

[0036] According to the cooling heat exchanger formed in the structure according to the present aspect, for example, in a case where portions in which required cooling performance is different exist in a cooling surface, by enhancing the effects of disturbing the flow of the heat medium in a portion in which higher cooling performance is required, local improvement in cooling performance based on promotion of turbulence can be achieved.

[0037] The ninth aspect is the cooling heat exchanger according to the eighth aspect, wherein 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 cooling flow path in the flow direction of the heat medium.

[0038] According to the cooling heat exchanger formed in the structure according to the present aspect, the turbulence-promoting effects that disturb the flow of the heat medium differ in the flow direction of the heat medium, whereby, for example, in a case where a portion where the temperature difference between the heat medium close to the cooling object and the heat medium away from the cooling object easily becomes large and a portion where the temperature difference between these heat media does not easily become large are located at different positions in the flow direction of the cooling flow path, by providing a region where the turbulence-promoting effect is strong at the portion where the temperature difference between the heat medium close to the cooling object and the heat medium away from the cooling object easily becomes large, it is possible to reduce the temperature difference in the flow direction of the heat medium.

[0039] In addition, at the portion where the temperature difference between the heat medium close to the cooling object and the heat medium away from the cooling object in the cooling flow path does not easily become large, by providing a region where the disturbance of the flow of the heat medium is suppressed, it is possible to achieve smooth flow of the heat medium.

[0040] The tenth aspect is the cooling heat exchanger according to the ninth aspect, in which the regions where the effects of disturbing the flow of the heat medium differ and are provided at different positions in the flow direction of the heat medium in the cooling flow path are provided so that the further downstream the region is, the stronger the effect of disturbing the flow of the heat medium is.

[0041] According to the cooling heat exchanger formed in the structure according to the present aspect, in the downstream side where the temperature difference between the heat medium flowing close to the cooling object and the heat medium flowing away from the cooling object easily becomes large, by achieving uniformization of the temperature of the heat medium based on the stirring effect that disturbs the flow of the heat medium, it is possible to exhibit high cooling performance.

[0042] The eleventh aspect is the cooling heat exchanger according to any one of the eighth to tenth aspects, in which the cooling flow path includes a parallel flow path portion that is composed of a plurality of flow path portions that are adjacent to each other and extend in parallel, the flow direction of the heat medium in the plurality of flow path portions that constitute the parallel flow path portion is the same, and at least one set of adjacent flow path portions in the parallel flow path portion is provided with the regions where the effects of disturbing the flow of the heat medium differ.

[0043] According to the cooling heat exchanger formed in the structure according to the present aspect, for example, in a case where there is a difference in the amount of heat generation in the flow path width direction of the cooling object, it is possible to more strongly provide disturbance of the flow of the heat medium at a portion of the cooling object where the amount of heat generation is large and more weakly provide disturbance of the flow of the heat medium at a portion of the cooling object where the amount of heat generation is small, and it is possible to achieve stabilization of the cooling performance.

[0044] The twelfth aspect is the cooling heat exchanger according to any one of the eighth 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 at least one of a difference in distance between the first protrusions and a difference in distance between the second protrusions in the flow direction of the heat medium.

[0045] 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 shortening the distance between the first protrusions and / or the distance between the second protrusions in the flow direction of the heat medium, and a region in which the turbulence promotion effect is weak can be set by increasing the distance between the first protrusions and / or the distance between the second protrusions. In this way, by providing a difference in the interval of the first protrusions and / or the second protrusions, regions in which the effects of disturbing the flow of the heat medium are different from each other can be easily set.

[0046] The thirteenth aspect is the cooling heat exchanger according to any one of the eighth 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 at least one of a difference in height between the first protrusions and a difference in height between the second protrusions.

[0047] 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 height of the first protrusions and / or the second protrusions, and a region in which the turbulence promotion effect is weak can be set by locally decreasing the height of the first protrusions and / or the second protrusions. In this way, by providing a difference in the height between the first protrusions and / or the second protrusions, regions in which the effects of disturbing the flow of the heat medium are different from each other can be easily set.

[0048] The fourteenth aspect is the cooling heat exchanger according to any one of the first to thirteenth aspects, wherein the cooling target is a battery.

[0049] According to the cooling heat exchanger formed in the structure according to the present aspect, for example, when a battery in which a local temperature rise of the output terminal portion or the like easily occurs is cooled, by adjusting the arrangement of the first protrusions and / or the second protrusions, the high-temperature portion of the battery can be efficiently cooled. Also, for example, in the case of cooling a battery unit composed of a plurality of batteries, by adjusting the arrangement of the first protrusions and / or the second protrusions, all of the plurality of batteries can be efficiently cooled, and a decrease in performance of the battery unit as a whole due to deterioration of a specific battery can be prevented.

[0050] The fifteenth aspect is the cooling heat exchanger according to any one of the first to fourteenth aspects, wherein the inner fins are provided with elastic deformation portions that allow deformation of the pair of cooling wall portions to approach each other by elastic deformation.

[0051] According to the cooling heat exchanger formed in the structure according to the present aspect, for example, in a case where the battery as the cooling target is deformed by bulging due to heating or the like caused by charging and discharging, deformation of the pair of cooling wall portions to the side of approaching each other following bulging deformation of the battery is allowed by elastic deformation of the elastic deformation portions of the inner fins disposed between the opposing surfaces of the pair of cooling wall portions. Therefore, even in the structure in which the inner fins are disposed between the opposing surfaces of the pair of cooling wall portions, following deformation of the cooling wall portions with respect to the surface shape of the cooling target prevents adverse situations such as separation of the overlapping surface of the cooling target and the cooling surface due to deformation of the cooling target, and stable cooling performance is exerted.

[0052] The sixteenth aspect is the cooling heat exchanger according to any one of the first to fifteenth aspects, wherein the first protrusions and the second protrusions each extend throughout the entire flow path width of the cooling flow path, and are continuous with the side wall portions of the cooling flow path at both end portions.

[0053] According to the cooling heat exchanger formed in the structure according to the present aspect, it is possible to prevent the flow of the heat medium that flows between the side wall portions of the cooling flow path and the first protrusions and the second protrusions while bypassing the first protrusions and the second protrusions, and to achieve efficient improvement of cooling performance. In addition, in a case where the first protrusions and the second protrusions are separated from the side wall portions of the cooling flow path, the flow rate of the heat medium that flows between the side wall portions of the cooling flow path and the first protrusions and the second protrusions tends to be fast, and thus there is a risk of occurrence of abrasion of the wall portions of the cooling flow path, the first protrusions, and the second protrusions. However, in the cooling heat exchanger according to the present aspect, the first protrusions and the second protrusions extend throughout the entire flow path width and are continuous with the side wall portions of the cooling flow path, and thus it is possible to prevent the flow of the heat medium between the side wall portions of the cooling flow path and the first protrusions and the second protrusions, and to prevent abrasion of the wall portions of the cooling flow path, the first protrusions, and the second protrusions.

[0054] The seventeenth aspect is the cooling heat exchanger according to any one of the first to sixteenth aspects, wherein the protrusion height of at least one of the first protrusions and the second protrusions varies in the flow path width direction of the cooling flow path, and either a low protrusion portion having a low protrusion height or a high protrusion portion having a high protrusion height is located at a central portion in the flow path width direction, and the other of the low protrusion portion and the high protrusion portion is located at each of both end portions in the flow path width direction of the first protrusions and the second protrusions.

[0055] 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 the both end portions in the flow path width direction of the first protrusion and / or the second protrusion are different in the stirring action, the flow rate, and the like. Therefore, the influence of the first protrusion and / or the second protrusion on the cooling performance is 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.

[0056] The eighteenth mode is based on the cooling heat exchanger described in the seventeenth mode, and at least one of the plurality of first protrusions and the second protrusions arranged in the flow path length direction of the cooling flow path is configured as a central low protrusion in which the low protrusion portion is provided in the central portion in the flow path width direction of the cooling flow path and the high protrusion portion is provided in the both end portions, and a central high protrusion in which the high protrusion portion is provided in the central portion in the flow path width direction of the cooling flow path and the low protrusion portion is provided in the both end portions, are alternately arranged in the flow path length direction of the cooling flow path.

[0057] According to the cooling heat exchanger formed in the structure according to the present mode, the central low protrusion in which the low protrusion portion is provided in the central portion in the flow path width direction, and the central high protrusion in which the low protrusion portion is provided in the both end portions in the flow path width direction, are alternately arranged in the flow path length direction, whereby the flow of the heat medium connected to the low protrusion portion, for example, in which the flow resistance is easily suppressed, is meandering in the flow path width direction, and an action of stirring the heat medium in the flow path width direction can be exerted. In addition, the heat medium flowing through the low protrusion portion of one protrusion toward the high protrusion portion of the next protrusion, for example, can also be expected to be efficiently stirred by the collision of the heat medium that has smoothly passed through the low protrusion portion with a high flow resistance with the high protrusion portion.

[0058] The nineteenth mode is based on the cooling heat exchanger described in any one of the first to eighteenth modes, and at least one of the first protrusions and the second protrusions is formed in a cross-sectional shape in which the cross section in the flow path length direction of the cooling flow path is tapered toward the protrusion tip end, and the protrusion tip portion, the upstream inclined portion that extends obliquely from the protrusion tip portion toward the bottom surface side of the cooling flow path, that is, the protrusion base portion, and the downstream inclined portion that extends obliquely from the protrusion tip portion toward the protrusion base portion are continuously provided without corners and smoothly.

[0059] According to the cooling heat exchanger formed in the structure according to the present mode, the surface of the protrusion is continuously smooth in the cross section in the flow path length direction, and the flow of the heat medium over the protrusion is smoothly generated.

[0060] The twentieth aspect is based on the cooling heat exchanger according to the nineteenth aspect, wherein a curvature radius of the protrusion top with respect to a length dimension of the protrusion base is within a range of 0.05 to 1.5 times in a cross section in a flow path length direction of the cooling flow path, and an inclination angle of the upstream inclined portion with respect to the bottom surface of the cooling flow path is formed within a range of 20 to 70 degrees in the cross section in the flow path length direction of the cooling flow path.

[0061] According to the cooling heat exchanger formed in the structure according to the present aspect, by the curvature radius of the protrusion top with respect to the length dimension of the protrusion base being 0.05 times or more, the protrusion top is formed into a smooth circular arc cross section without being a substantial corner. In addition, by the curvature radius of the protrusion top with respect to the length dimension of the protrusion base being 1.5 times or less, it is possible to prevent a case where the length dimension in the flow path length direction of the protrusion is excessively long, and it is possible to set the inclination angle with respect to the bottom surface of the upstream inclined portion and the downstream inclined portion, which are smoothly continuous with the protrusion top, to be sufficiently large.

[0062] By the inclination angle of the upstream inclined portion with respect to the bottom surface of the cooling flow path being 20 degrees or more, the flow of the heat medium from the upstream side toward the protrusion is efficiently disturbed by the upstream inclined portion, and an improvement in cooling performance based on the stirring action is achieved. In addition, by the inclination angle of the upstream inclined portion with respect to the bottom surface of the cooling flow path being 70 degrees or less, it is possible to prevent a case where the flow of the heat medium is excessively restricted by the protrusion.

[0063] The twenty-first aspect is based on the cooling heat exchanger according to the nineteenth aspect, wherein an inclination angle of the upstream inclined portion with respect to the bottom surface of the cooling flow path is formed to be 25 degrees or less in a cross section in a flow path length direction of the cooling flow path.

[0064] According to the cooling heat exchanger formed in the structure according to the present aspect, by the inclination angle of the upstream inclined portion with respect to the bottom surface of the cooling flow path being 25 degrees or less, it is possible to set the pressure loss to be sufficiently small, and for example, it is also possible to flow the heat medium using a cheap pump having a lower performance.

[0065] The twenty-second aspect is based on the cooling heat exchanger according to any one of the first to twenty-first aspects, wherein a protrusion height of at least one of the first protrusion and the second protrusion arranged in the flow path length direction in the cooling flow path is higher toward the downstream.

[0066] According to the cooling heat exchanger formed in the structure according to the present mode, by making the protrusion height of the first protrusion and / or the second protrusion arranged in the flow path length direction higher toward the downstream side, the effect of disturbing the flow of the heat medium based on the protrusion can be made to act more strongly on the downstream side. Thus, the heat medium flowing near the cooling target is easily made to be high-temperature on the downstream side by heat exchange, and the effect of improving the cooling performance based on the protrusion can be more favorably obtained.

[0067] The twenty-third mode is based on the cooling heat exchanger of any one of the first to the twenty-second modes, and in at least one of the first protrusion and the second protrusion arranged in the flow path length direction in the cooling flow path, the interval in the flow path length direction of the cooling flow path is narrowed toward the downstream side.

[0068] According to the cooling heat exchanger formed in the structure according to the present mode, by making the protrusion height of the first protrusion and / or the second protrusion arranged in the flow path length direction higher toward the downstream side, the effect of disturbing the flow of the heat medium based on the protrusion can be made to act more strongly on the downstream side. Thus, the heat medium flowing near the cooling target is easily made to be high-temperature on the downstream side by heat exchange, and the effect of improving the cooling performance based on the protrusion can be more favorably obtained.

[0069] The twenty-fourth mode is based on the cooling heat exchanger of any one of the first to the twenty-third modes, and in at least one of the first protrusion and the second protrusion arranged in the flow path length direction in the cooling flow path, the protrusion height is made higher toward the downstream side, and the interval in the flow path length direction of the cooling flow path is narrowed toward the downstream side.

[0070] According to the cooling heat exchanger formed in the structure according to the present mode, by making the protrusion height of the first protrusion and / or the second protrusion arranged in the flow path length direction higher toward the downstream side, the effect of disturbing the flow of the heat medium based on the protrusion can be made to act more strongly on the downstream side. Thus, the heat medium flowing near the cooling target is easily made to be high-temperature on the downstream side by heat exchange, and the effect of improving the cooling performance based on the protrusion can be more favorably obtained.

[0071] Invention effect

[0072] According to the present application, in the cooling heat exchanger, a double-sided cooling structure having a cooling surface on both sides can be realized with a simple structure, and excellent cooling performance can be stably obtained. BRIEF DESCRIPTION OF DRAWINGS

[0073] Figure 1 is an exploded perspective view of a cooling heat exchanger as a first embodiment of the present application.

[0074] Figure 2 is Figure 1 is a cross-sectional view of the cooling heat exchanger shown in Figure 3The diagram of section II-II.

[0075] Figure 3 yes Figure 2 Sectional view III-III.

[0076] Figure 4 It constitutes Figure 1 A top view of the inner fins of a cooling heat exchanger.

[0077] Figure 5 Yes Figure 4 The diagram shows an enlarged representation of the VV cross section.

[0078] Figure 6 It is indicated by the assembly status of the battery pack. Figure 1 A three-dimensional view of a heat exchanger used for cooling.

[0079] Figure 7 This is an exploded perspective view of a cooling heat exchanger as a second embodiment of the present invention.

[0080] Figure 8 This is an exploded perspective view of a cooling heat exchanger as a third embodiment of the present invention.

[0081] Figure 9 This is a top view of the inner fins constituting the cooling heat exchanger according to the fourth embodiment of this utility model.

[0082] Figure 10 This is a top view of the inner fins constituting the cooling heat exchanger according to the fifth embodiment of this utility model.

[0083] Figure 11 yes Figure 10 The cross-sectional view of the inner fin shown is a... Figure 11 A magnified representation of a portion of section XIII-XIII.

[0084] Figure 12 It is equivalent to Figure 10 Enlarged sectional view of section XII-XII.

[0085] Figure 13 It is equivalent to Figure 10 Enlarged sectional view of section XIII-XIII.

[0086] Figure 14 This is a top view of the inner fins constituting the cooling heat exchanger according to the sixth embodiment of this utility model.

[0087] Figure 15 It is equivalent to Figure 14 An enlarged sectional view of the XV-XV section.

[0088] Figure 16 is an enlarged sectional view of the cross section XVI-XVI corresponding to Figure 14

[0089] Figure 17 is a sectional view showing a part of an inner fin constituting a cooling heat exchanger of a seventh embodiment of the present application.

[0090] Figure 18 is a sectional view showing a part of an inner fin constituting a cooling heat exchanger of another embodiment of the present application.

[0091] BRIEF DESCRIPTION OF REFERENCE NUMERALS

[0092] 10: cooling heat exchanger (first embodiment); 12: outer wall member; 14: first member; 16: second member; 18: recess; 20: supply hole; 22: discharge hole; 24: supply port; 26: discharge port; 28: cooling flow path; 30: cooling wall portion; 32: cooling surface; 34: inner fin; 35: end wall portion; 36: end wall connecting portion; 37: end wall main portion; 38: intermediate partition portion; 40: protrusion forming portion; 42: partition wall portion; 44: partition wall main portion; 46: partition wall connecting portion; 48: protrusion; 48a: first protrusion; 48b: second protrusion; 50: upstream side inclined surface; 52: downstream side inclined surface; 54: ridge line; 56: flow path portion; 58: parallel flow path portion; 60a: first narrow flow path; 60b: second narrow flow path; 62: battery pack (cooling object); 64: terminal portion; 70: cooling heat exchanger (second embodiment); 72: inner fin; 74: inclined plate portion; 76: top portion; 78: protrusion; 78a: first protrusion; 78b: second protrusion; 80: cooling heat exchanger (third embodiment); 82: inner fin; 84: protrusion; 84a: first protrusion; 84b: second protrusion; 90: inner fin (fourth embodiment); 100: inner fin (fifth embodiment); 102: protrusion; 102a: first protrusion; 102b: second protrusion; 104: protrusion top portion; 106: protrusion base portion; 108: upstream inclined portion; 110: downstream inclined portion; 112: low protrusion portion; 114: high protrusion portion; 116: central low protrusion; 118: central high protrusion; 120: inner fin (sixth embodiment); 122: protrusion; 122a: first protrusion; 122b: second protrusion; 124: convex portion; 130: inner fin (seventh embodiment); 140: protrusion (another embodiment); 142: protrusion top portion; 144: upstream inclined portion; 146: downstream inclined portion; 148: protrusion base portion; R: radius of curvature of protrusion top portion; L: length dimension of protrusion base portion; a: inclination angle of upstream inclined portion; β: inclination angle of downstream inclined portion. DETAILED DESCRIPTION​

[0093] Hereinafter, an embodiment of the present application will be described with reference to the drawings.

[0094] In Figures 1-3 , a cooling heat exchanger 10 as a first embodiment of the present application is shown. As shown in Figure 2 , Figure 3 , the cooling heat exchanger 10 is provided with a hollow outer wall member 12, which is composed of a first member 14 and a second member 16. In the following description, in principle, the upward and downward direction refers to the upward and downward direction in Figure 2 , the left and right direction refers to the left and right direction in Figure 2 , and the front and rear direction refers to the left and right direction in Figure 3 . In addition, the upward, leftward, rightward, and frontward directions mentioned here are convenient directions for explanation. Therefore, for example, the vertical upward and downward direction in the use state of the cooling heat exchanger 10 can be the upward and downward direction in the above-described embodiment, or the left and right direction or the front and rear direction, or a direction that is not consistent with any of the upward, leftward, rightward, and frontward directions.

[0095] The first member 14 is formed in a substantially rectangular plate shape, and is formed to have a length dimension in the left and right direction that is larger than a width dimension in the front and rear direction. The first member 14 is preferably formed of a material having a high thermal conductivity, such as an aluminum alloy, stainless steel, a copper alloy, or the like. The first member 14 may, for example, also be formed as a composite plate in which a base material is laminated with a filler metal. In the case where the first member 14 is a composite plate, the base material may, for example, be formed of an Al-Mn aluminum alloy in which manganese is added to aluminum, and the filler metal may, for example, be formed of an Al-Si aluminum alloy in which silicon is added to aluminum. Alternatively, the first member 14 may, for example, also be formed as a composite plate in which a base material composed of stainless steel is combined with a filler metal composed of a nickel alloy. The composite plate can be obtained by a known manufacturing method such as press bonding of the base material and the filler metal, or blowing of the filler metal with respect to the base material.

[0096] The second member 16 is formed in an open rectangular box shape having a recess 18 that is open toward the lower side, and integrally has a substantially rectangular plate-shaped upper bottom wall and a rectangular cylindrical peripheral wall that protrudes from the outer peripheral end of the upper bottom wall toward the lower side. The second member 16 is preferably formed of a material having a high thermal conductivity, such as an aluminum alloy, stainless steel, a copper alloy, or the like, similarly to the first member 14.

[0097] A supply hole 20 that penetrates the upper bottom wall of the recess 18 in the up-down direction is formed in the left end portion of the second member 16, and a discharge hole 22 that penetrates the upper bottom wall of the recess 18 in the up-down direction is formed in the right end portion of the second member 16. The second member 16 has a substantially cylindrical supply port 24 that protrudes upward from the upper bottom wall of the recess 18 at the opening peripheral portion of the supply hole 20, and a substantially cylindrical discharge port 26 that protrudes upward from the upper bottom wall of the recess 18 at the opening peripheral portion of the discharge hole 22.

[0098] As shown in Figure 2 , Figure 3 The first member 14 and the second member 16 are fixedly joined to each other in the up-down direction. The protruding front end surface of the peripheral wall of the recess 18 in the second member 16 abuts against the outer peripheral end portion of the first member 14, and is brazed by, for example, brazing filler of the first member 14 that is formed as a composite plate, whereby the first member 14 and the second member 16 are fixedly joined to each other. In this way, the outer wall member 12 is formed by the first member 14 and the second member 16 being fixedly joined to each other.

[0099] A cooling flow path 28 is formed in the inside of the outer wall member 12 by the opening of the recess 18 of the second member 16 being covered by the first member 14. The cooling flow path 28 is a flow path for a heat medium such as a liquid of water, an aqueous ethylene glycol solution, or the like, or a gas of air or the like to flow. In the cooling flow path 28, the heat medium that is formed at a low temperature is supplied from the outside through the supply hole 20, and the heat medium that becomes high in temperature due to heat exchange is discharged to the outside through the discharge hole 22. Therefore, the supply hole 20 is provided at the end portion on the upstream side of the cooling flow path 28, and the discharge hole 22 is provided at the end portion on the downstream side of the cooling flow path 28. Further, the cooling flow path 28 for the heat medium to flow is formed in the inside of the outer wall member 12, whereby the joint portion of the first member 14 and the second member 16 has fluid tightness that can prevent leakage of the heat medium.

[0100] A pair of cooling wall portions 30, 30 is provided in the outer wall member 12. That is, in the first member 14, the portion that constitutes the wall portion of the cooling flow path 28 is formed as the lower cooling wall portion 30. In addition, the bottom wall of the recess 18 in the second member 16 is formed as the upper cooling wall portion 30. Therefore, the mutually opposing portions in the up-down direction in the outer wall member 12 are formed as the pair of cooling wall portions 30, 30. The cooling wall portion 30, the cooling wall portion 30 are cooled by heat exchange with the heat medium that flows in the cooling flow path 28. The cooling wall portion 30, the cooling wall portion 30 are formed as planes that expand in the up-down direction substantially orthogonally to the up-down outer surfaces that are formed as cooling surfaces 32, respectively.

[0101] The inner fin 34 is housed in the cooling flow path 28 between the opposing faces of the bottom walls of the recesses 18 formed in the first member 14 and the second member 16. As shown in Figs. 1 and 2, the inner fin 34 is formed as a substantially rectangular plate shape having a greater length dimension in the left-right direction than a width dimension in the front-rear direction. Figure 4 Figure 5 The inner fin 34 is formed as a substantially rectangular plate shape having a greater length dimension in the left-right direction than a width dimension in the front-rear direction. The inner fin 34 is formed of, for example, a metal such as an aluminum alloy, stainless steel, or a synthetic resin. The inner fin 34 of the present embodiment is formed as a stamped metal piece made of an aluminum alloy. Preferably, the inner fin 34 is formed of a material having a high thermal conductivity, like the first member 14 and the second member 16. The inner fin 34 is formed in a shape and size that enables insertion into the recess 18 of the second member 16.

[0102] End wall portions 35 projecting in the upward-downward direction are provided at both ends in the front-rear direction of the inner fin 34. The end wall portion 35 projects upward and then downward at the front end projecting upward, thereby projecting to both sides in the upward-downward direction. More specifically, the end wall portion 35 integrally includes an end wall link portion 36 projecting upward, and an end wall main portion 37 projecting downward from an upper end portion of the end wall link portion 36. The end wall link portion 36 is inclined in a direction in which the end wall main portion 37 is spaced apart in the front-rear direction. The end wall main portion 37 is formed to be substantially non-inclined in the upward-downward direction. The end wall main portion 37 further projects downward than the lower end of the end wall link portion 36. Alternatively, the end wall portion 35 can be configured such that the end wall link portion 36 projects downward, and the end wall main portion 37 projects upward from a lower end portion of the end wall link portion 36.

[0103] An intermediate partition portion 38 is provided between the end wall portions 35 and the end wall portions 35 in the inner fin 34. The intermediate partition portion 38 is integrally continuous at the end portions on the inner side in the front-rear direction of the end wall link portion 36. Further, the end wall portions 35 project to both sides in the upward-downward direction with respect to the intermediate partition portion 38. In addition, the intermediate partition portion 38 is located in the middle in the upward-downward direction of the end wall main portion 37, and extends in a substantially orthogonal direction with respect to the upward-downward direction. The intermediate partition portion 38 of the present embodiment is divided into three protrusion formation portions 40, 40, 40 by two partition wall portions 42, 42 described later.

[0104] ​In the middle of the front-rear direction of the middle partition portion 38 in the inner fin 34, two partition wall portions 42 protruding to both sides in the up-down direction from the middle partition portion 38 are provided. The partition wall portion 42 integrally has a partition wall main body portion 44 protruding to both sides in the up-down direction from the middle partition portion 38, and a pair of partition wall connecting portions 46, 46 connecting the upper and lower ends of the partition wall main body portion 44 and the middle partition portion 38. The partition wall main body portion 44 is continuously formed over the entire length in the left-right direction of the inner fin 34, and is formed to be substantially non-inclined with respect to the up-down direction. The partition wall connecting portions 46 are continuously formed over the entire length in the left-right direction of the inner fin 34, and extend from the upper and lower ends of the partition wall main body portion 44 toward the inner side in the up-down direction. The partition wall connecting portions 46 are inclined in a direction in which the partition wall main body portion 44 is spaced apart in the front-rear direction. The partition wall connecting portions 46, 46 extending from the upper and lower ends of the partition wall main body portion 44 are connected to each of the two protrusion formation portions 40, 40 adjacent in the front-rear direction, and these two protrusion formation portions 40, 40 are continuously formed integrally by the partition wall portion 42.

[0105] In the protrusion formation portions 40, 40 of the middle partition portion 38 divided by the partition wall portions 42, 42, a plurality of protrusions 48 are formed. As shown in Figure 4 The protrusions 48 are formed in a substantially V-shape on the surface of the inner fin 34, and are formed to be a substantially V-shape when viewed in the up-down direction, and the width in the front-rear direction narrows toward the left side of the upstream side of the cooling flow path 28 by the arrangement of the inner fin 34 to the cooling flow path 28 described later. In the protrusions 48, the left side portion on the upstream side of the cooling flow path 28 is formed as an upstream inclined surface 50 inclined in a direction in which the protrusion height dimension increases toward the downstream side, and the right side portion on the downstream side is formed as a downstream inclined surface 52 inclined in a direction in which the protrusion height dimension decreases toward the downstream side. Thus, in the connecting portion of the upstream inclined surface 50 and the downstream inclined surface 52, that is, the central portion in the left-right direction of the protrusion 48, the ridge line 54 having the largest protrusion height dimension is continuously formed in a substantially V-shape when viewed in the up-down direction.

[0106] The protrusions 48 are provided in a plurality of numbers arranged at substantially equal intervals in the left-right direction. The same number of first protrusions 48a (described later) are formed at substantially the same positions in the left-right direction in the protrusion formation portions 40, 40, 40. The same number of second protrusions 48b (described later) are formed at substantially the same positions in the left-right direction. The protrusions 48 are provided over substantially the entire length of the intermediate partition portion 38 in the left-right direction. The protrusions 48 are provided in regions scattered over substantially the entire portions of the protrusion formation portions 40 in the front-rear direction. In the present embodiment, the protrusions 48 are slightly separated from the end wall portions 35, 35 and the partition wall portions 42, 42 in the front-rear direction, and there are portions in which the protrusions 48 are absent at the front-rear end portions of the protrusion formation portions 40. Thus, at the time of forming by press working based on the end wall portions 35, 35 and the partition wall portions 42, 42, it is possible to prevent the protrusions 48 from becoming an obstacle to the forming of the end wall portions 35, 35 and the partition wall portions 42, 42. Further, it is also possible that the protrusions 48 are continuously provided over the entire portions of the protrusion formation portions 40 in the width direction (front-rear direction), and the both end portions are directly connected to the partition wall portions 42 and / or the end wall portions 35.

[0107] As shown in Figure 2 , Figure 5 , the protrusions 48 include first protrusions 48a protruding from the lower surface of the intermediate partition portion 38, and second protrusions 48b protruding from the upper surface of the intermediate partition portion 38. As shown in Figure 2 , the first protrusions 48a and the second protrusions 48b are alternately arranged in the left-right direction. The first protrusions 48a and the second protrusions 48b protrude in opposite directions in substantially the same shape and size in the present embodiment, and the shape and size can also be different from each other. Regarding the arrangement of the first protrusions 48a and the second protrusions 48b in the left-right direction in the three protrusion formation portions 40, 40, 40, the same arrangement is provided in the present embodiment, but the arrangement can also be different from each other.

[0108] As shown in Figures 1-3 , the inner fins 34 are arranged between the upper and lower portions of the first member 14 and the second member 16, and as shown in Figure 2 , Figure 3As shown, the inner fins 34 are housed in the cooling flow path 28 that constitutes the inner region of the outer wall member 12. The length dimension of the inner fins 34 in the left-right direction is formed to be smaller than the length dimension of the cooling flow path 28 in the left-right direction, and the left and right end surfaces of the inner fins 34 are separated inward from the outer wall member 12 in the left-right direction. In summary, the inner fins 34 are partially arranged in the flow path length direction of the cooling flow path 28, in the approximate center of the cooling flow path 28. Therefore, in the present embodiment, more specifically, the inner region of the outer wall member 12 that is divided into two by the inner fins 34 becomes the central portion in the left-right direction, excluding the end portions in the left-right direction of the cooling flow path 28. In the present embodiment, the inner fins 34 are positioned inward in the left-right direction from the supply holes 20 and the discharge holes 22 that are formed in the end portions in the flow path length direction of the cooling flow path 28, and are arranged without covering these supply holes 20 and discharge holes 22.

[0109] The inner fins 34 can be positioned with respect to the outer wall member 12 by fitting the end wall portions 35, the end wall portions 35 and the second member 16 in the front-rear direction, or by sandwiching at least one of the end wall portions 35, the end wall portions 35 and the partition wall portions 42, the partition wall portions 42 between the bottom wall of the first member 14 and the second member 16. Further, a positioning structure other than the end wall portions 35, the end wall portions 35 and the partition wall portions 42, the partition wall portions 42 can be provided between the inner fins 34 and the outer wall member 12. Specifically, for example, if a protrusion or the like that engages with the left and right end surfaces of the inner fins 34 in the left-right direction is provided in at least one of the bottom wall and the side wall of the second member 16, the inner fins 34 can be positioned with respect to the outer wall member 12 in each of the front-rear, left-right, and up-down directions without the fitting of the end wall portions 35, the end wall portions 35 into the recessed portions 18, or the sandwiching of the end wall portions 35, the end wall portions 35 and / or the partition wall portions 42, the partition wall portions 42 between the first member 14 and the second member 16. Further, the inner fins 34 can be non-fixed to the outer wall member 12, and at least one of the end wall portions 35, the end wall portions 35 and the partition wall portions 42, the partition wall portions 42 can be fixed to the outer wall member 12 by means of adhesion, brazing, or the like.

[0110] By arranging the inner fins 34 inside the cooling flow path 28, the cooling flow path 28 is divided into a plurality of portions in the middle portion in the flow path length direction by the inner fins 34. That is, the middle partition portion 38 of the inner fins 34 is positioned in the middle in the up-down direction of the end wall portions 35, the end wall portions 35 and the partition wall portions 42, the partition wall portions 42, and thus is separated from both of the cooling wall portions 30. Thus, the cooling flow path 28 is divided into two portions on both sides in the up-down direction by the inner fins 34, and the region of the cooling flow path 28 on the lower side than the inner fins 34 is formed as a region that cools the cooling wall portion 30 of the first member 14, and the region on the upper side than the inner fins 34 is formed as a region that cools the cooling wall portion 30 of the second member 16.

[0111] In a heat exchanger 10 with a double-sided cooling structure, where the cooling flow path 28 is divided into two parts on the upper and lower sides by the middle partition 38 of the inner fins 34, and cooling surfaces 32 are provided on the upper and lower sides respectively, it is easy to control the flow rate and velocity of the heat medium by adjusting the flow path cross-sectional area of ​​the upper and lower sides of the cooling flow path 28 that cools the cooling surfaces 32 and the cooling surfaces 32 (cooling wall portion 30, cooling wall portion 30).

[0112] Furthermore, by positioning the inner fins 34 in the middle portion of the cooling flow path 28 along its length, the two ends of the cooling flow path 28, which has supply holes 20 and discharge holes 22, are not vertically separated by the inner fins 34. Therefore, the heat medium supplied from the supply holes 20 to the cooling flow path 28 does not obstruct the inner fins 34 from flowing into any area of ​​the cooling flow path 28, and the heat medium passing through any area of ​​the cooling flow path 28 does not obstruct the inner fins 34 from being discharged to the outside through the discharge holes 22.

[0113] The areas on the upper and lower sides of the inner fins 34 in the cooling flow path 28 are divided into three sections in the front-to-back direction by two partition sections 42, 42. Thus, the cooling flow path 28 is divided into six flow path sections 56, 56..., 56 in which the heat medium flows in the same direction. These six flow path sections 56, 56..., 56 arranged side by side constitute the parallel flow path section 58 of this embodiment.

[0114] In this way, the upper and lower sides of the cooling flow path 28 are divided into three by the partition wall 42 in the flow path width direction. This allows for appropriate control of the flow rate and velocity of the heat medium flowing in each flow path 56, and enables greater freedom in setting the dimensions of the cooling surface 32 and the flow path width direction of the cooling surface 32 that are cooled by these flow path 56.

[0115] like Figure 2 , Figure 3 As shown, either the first protrusion 48a or the second protrusion 48b protrudes from the middle partition 38 of the inner fin 34 into each flow path portion 56. The first protrusion 48a is spaced upward relative to the lower cooling wall portion 30. Furthermore, a first narrow flow path 60a is formed between the first protrusion 48a and the lower cooling wall portion 30, where the flow path cross-sectional area in the lower flow path portion 56 is smaller than that of other portions. Conversely, the second protrusion 48b is spaced downward relative to the upper cooling wall portion 30. Furthermore, a second narrow flow path 60b is formed between the second protrusion 48b and the upper cooling wall portion 30, where the flow path cross-sectional area in the upper flow path portion 56 is smaller than that of other portions. In this embodiment, the first narrow flow path 60a and the second narrow flow path 60b are formed with approximately the same flow path cross-sectional area and flow path cross-sectional shape, but they may also be different.

[0116] As shown in Figure 6 the cooling heat exchanger 10 formed in the above-described structure is equipped with a battery pack 62 as a cooling target. The battery pack 62 is, for example, a battery for an electric vehicle, a hybrid vehicle, or the like. The battery pack 62 has, for example, a substantially rectangular parallelepiped shape as a whole, and the front-to-rear width dimension is formed larger than the left-to-right length dimension. In addition, terminal portions 64 protruding forward are provided at both the upper and lower end portions of the battery pack 62. The terminal portions 64 are formed as output terminals for outputting a large current through a bus bar not shown. Therefore, the battery pack 62 of the present embodiment has the upper and lower end portions with the terminal portions 64 more likely to become high temperature than the upper and lower central portions in the use state.

[0117] The cooling heat exchanger 10 is a double-sided cooling structure in which cooling surfaces 32 are provided on both the upper and lower surfaces, and thus the battery pack 62 overlaps the cooling surfaces 32, 32 on both the upper and lower sides of the cooling heat exchanger 10. In the present embodiment, a plurality of battery packs 62 are arranged in the flow path length direction of the cooling flow path 28, that is, the left-to-right direction on both the upper and lower sides of the cooling heat exchanger 10, and the plurality of battery packs 62 overlap the cooling surfaces 32, 32.

[0118] In the cooling heat exchanger 10, the cooling surfaces 32, 32 provided on the surfaces of the cooling wall portions 30, 30 become low temperature through heat exchange between the heat medium flowing in the cooling flow path 28 and the cooling wall portions 30, 30 of the first member 14 and the second member 16. Further, the battery pack 62 that generates heat during operation is mounted on the cooling surfaces 32, 32, and the battery pack 62 is cooled through heat exchange between the first member 14 and the second member 16 having the cooling surfaces 32, 32 and the battery pack 62 overlapping each cooling surface 32. In other words, the battery pack 62 is cooled through heat exchange between the battery pack 62 and the heat medium flowing in the cooling flow path 28 via the first member 14 and the second member 16.

[0119] The inner fins 34 are arranged in the cooling flow path 28, and the inner fins 34 are in contact with the outer wall member 12 (the first member 14 and the second member 16). Therefore, the substantial contact area of the outer wall member 12 with the heat medium is increased by the inner fins 34, and the cooling surfaces 32, 32 are efficiently cooled by the heat medium.

[0120] The heat medium temperature rises due to receiving heat from the battery group 62. In particular, the heat medium flowing near the cooling wall portion 30, the position of the cooling wall portion 30 is heated by the heat of the battery group 62 and the temperature becomes high. On the other hand, the heat medium flowing away from the cooling wall portion 30, the position of the cooling wall portion 30, in other words, near the inner fin 34 is not easily subjected to the heat of the battery group 62, and the temperature rise is relatively suppressed and it is easy to maintain a low temperature. Thus, in the heat medium in the cooling flow path 28, by heat exchange with the battery group 62, it is easy to generate a temperature distribution in which the temperature becomes high toward both the upper and lower sides. As a result, the temperature difference between the high-temperature heat medium flowing near the cooling wall portion 30, the position of the cooling wall portion 30 and the battery group 62 becomes small, and the efficiency of heat exchange between the battery group 62 and the heat medium decreases.

[0121] Therefore, in the cooling heat exchanger 10, the inner fin 34 is provided with the first protrusion 48a and the second protrusion 48b which protrude into the cooling flow path 28, and the heat medium is stirred when passing over the first protrusion 48a and the second protrusion 48b, whereby the temperature difference in the up-and-down direction of the heat medium is reduced. Thus, the heat medium flowing only near the battery group 62 is prevented from becoming high-temperature, the temperature difference between the battery group 62 and the heat medium flowing near it is ensured to be large, and the heat exchange efficiency between the battery group 62 and the heat medium can be improved.

[0122] In the present embodiment, the first protrusion 48a and the second protrusion 48b are formed throughout substantially the entire left-and-right direction of the inner fin 34. Thus, in the parallel flow path portion 58 formed by the inner fin 34, the stirring effect of the heat medium based on the first protrusion 48a and the second protrusion 48b is exerted, and the battery group 62 is efficiently cooled by the heat medium flowing in the parallel flow path portion 58. Further, in the cooling heat exchanger 10 of the present embodiment, the inner fin 34 is provided up to the left-and-right direction outer side of the region overlapping the battery group 62, and the effect of the inner fin 34 of improving the heat exchange efficiency can effectively act on the entire battery group 62.

[0123] The protrusion 48 of the present embodiment is formed in a V-shape shape in which the width narrows toward the upstream side of the flow path portion 56 on the surface of the inner fin 34. In summary, the protrusion 48 is formed in a V-shape shape when viewed from above. When the heat medium passes over the protrusion 48, it flows in a direction orthogonal to the protrusion 48 in which the flow resistance is small, and thus flows in a direction inclined toward the inner side of the flow path width direction with respect to the flow path length direction (left-and-right direction) of the flow path portion 56. Also, the flow of the heat medium toward the inner side of the flow path width direction converges on the downstream side of the protrusion 48, and thus a vortex flow, a turbulent flow is generated on the downstream side of the protrusion 48, and the heat medium is stirred by the vortex flow, the turbulent flow. Thus, the temperature difference in the up-and-down direction of the heat medium is reduced, and the decrease in cooling performance of the heat medium due to heating by the battery group 62 is suppressed.

[0124] However, there is a case where the battery pack 62 is deformed in a manner that the surface bulges due to heat generation during use, in which case the cooling wall portion 30 provided with the cooling surface 32 is elastically deformed so as to follow the deformation of the battery pack 62. That is, the cooling wall portion 30 formed in a flat plate shape is allowed to elastically flexibly deform, and at least one of the partition wall portion 42 of the inner fin 34 overlapping the cooling wall portion 30 from the cooling flow path 28 side, the partition wall main body portion 44, and the partition wall connecting portion 46 is allowed to elastically flexibly deform. Thus, in a case where the surface of the battery pack 62 is deformed so as to bulge toward the cooling surface 32 and the cooling surface 32 is pressed into the cooling flow path 28 side, the elastic flexible deformation of the cooling wall portion 30 provided with the cooling surface 32 is not hindered by the partition wall portion 42 of the inner fin 34. In this way, by elastically deforming the cooling surface 32 so as to follow the deformation of the surface of the battery pack 62, the generation of a gap between the overlapping surface of the cooling surface 32 and the battery pack 62, the plastic deformation of the first member 14 and the second member 16 having the cooling wall portion 30, the plastic deformation of the inner fin 34, and the like are prevented. As described above, in the inner fin 34 of the present embodiment, the partition wall portion 42 is formed as an elastically deformable portion that allows approach (approach deformation) based on the elastic deformation of the cooling wall portion 30.

[0125] By allowing the partition wall portion 42 to elastically flexibly deform, for example, even if the upper and lower height dimensions of the partition wall portion 42 are slightly larger than the depth of the recessed portion 18 due to an error, the partition wall portion 42 can be accommodated in the cooling flow path 28 by elastically flexibly deforming the partition wall portion 42. In the present embodiment, the end wall portion 35 of the inner fin 34 also allows elastic flexible deformation similarly to the partition wall portion 42, and thus accommodation failure into the cooling flow path 28 is also avoided for the end wall portion 35. Therefore, a structure in which the inner fin 34 is sandwiched between the cooling wall portions 30 and supported can also be adopted while allowing the dimensional difference caused by the tolerances of the second member 16 and the inner fin 34.

[0126] Figure 7 A cooling heat exchanger 70 as a second embodiment of the present application is shown. The cooling heat exchanger 70 has a structure in which an inner fin 72 is arranged between the first member 14 and the second member 16. In the following description, the same reference numerals are attached to the members and portions that are substantially the same as those of the above-described embodiment, and thus the description is omitted.

[0127] The inner fin 72 is formed of metal, synthetic resin, or the like, and is formed in a thin-walled plate shape. The inner fin 72 has a sawtooth-shaped, wavy cross section that is folded back in the up-down direction. In the present embodiment, a sawtooth-shaped cross section is provided in a manner in which a plurality of the inclined plate portions 74 that expand obliquely to the up-down direction and the front-rear direction are continuously arranged in the up-down direction at the top portions 76 of the folds. The inner fin 72 extends linearly in the left-right direction in the sawtooth-shaped cross-sectional shape. Furthermore, the number of folds (the number of top portions 76) of the inner fin 72 formed in a sawtooth shape or a wavy shape is not particularly limited, and is appropriately set in consideration of, for example, the flow path cross-sectional area of the flow path portion divided by the width dimension of the cooling surface and the inner fin 72.

[0128] The inner fin 72 is formed with a protrusion 78. The protrusion 78 is formed in a substantially V-shaped shape on the surface of the inner fin 72, and the tip end is tapered (the width is narrowed) toward the upstream side of the cooling flow path. In general, the protrusion 78 is formed in a substantially V-shaped shape when viewed in the up-down direction. The protrusion 78 is composed of a first protrusion 78a that protrudes toward the upper surface side of the inner fin 72, and a second protrusion 78b that protrudes toward the lower surface side of the inner fin 72. The first protrusion 78a and the second protrusion 78b are arranged in groups at positions at which they are spaced apart from each other in the flow path length direction of the cooling flow path, that is, the left-right direction, and in the present embodiment, are arranged in two rows in the flow path width direction of the cooling flow path, that is, the front-rear direction, with five groups provided in each row. Therefore, in the inner fin 72 of the present embodiment, ten of each of the first protrusion 78a and the second protrusion 78b are formed.

[0129] The V-shaped protrusion 78 is formed so that the end portion of the upstream side on which the width is narrowed is located at the inclined plate portion 74, that is, the top portion 76 of the sawtooth of the inner fin 72. In the V-shaped protrusion 78, the end portion of the downstream side does not reach the end portion of the inclined plate portion 74, and the protrusions 78 adjacent in the front-rear direction are separated from each other in the front-rear direction. Furthermore, the protrusion 78 can be provided up to the top portion 76, or can be provided at a portion that is offset from the top portion 76. The protrusion 78 can be provided at least in the inclined plate portion 74 between the adjacent top portions 76, and is preferably also formed in the inclined plate portion 74 between the end portion in the front-rear direction of the inner fin 72 and the top portion 76 adjacent thereto.

[0130] In the present embodiment, the inner fin 72 is formed as a stamped metal piece, and the protrusion 78 is formed by stamping, so there is a V-shaped recess in the surface of the protrusion 78 that is opposite the protruding side. Furthermore, if the protrusion 78 is formed at the same time as the formation of the sawtooth cross section by stamping of a flat metal raw material plate, the number of processing steps can be reduced.

[0131] According to the cooling heat exchanger 70 equipped with the aforementioned inner fins 72, a cooling flow path (not shown) formed between the first member 14 and the second member 16 is divided in the height direction (vertical direction) by the inner fins 72. Furthermore, the inner fins 72 have a serrated cross-sectional shape, so the serrated top 76 overlaps with either the first member 14 or the second member 16, thereby dividing the cooling flow path into multiple sections in the width direction (front-back direction). As a result, the cooling surfaces 32 respectively provided on the upper and lower outer surfaces of the first member 14 and the second member 16 are effectively cooled by the flow path portions of the divided cooling flow paths.

[0132] The inner fin 72 of this embodiment can not only divide the cooling flow path vertically with a simpler shape than the inner fin 34 of the first embodiment, but also divide it in the width direction of the flow path, thereby improving the cooling performance. In addition, the inner fin 72 can be configured in a non-fixed manner between the first member 14 and the second member 16, or the top 76 and the front and rear ends can be fixedly connected to the first member 14 and the second member 16.

[0133] Furthermore, by providing the first protrusion 78a and the second protrusion 78b protruding into the flow path area of ​​the cooling flow path on the inner fin 72, the hot medium flowing in these flow path areas is stirred by the first protrusion 78a and the second protrusion 78b, preventing the hot medium flowing only near each cooling surface 32 from becoming high temperature, thereby improving the cooling performance.

[0134] For example, when the cooling wall 30 deforms towards each other due to pressure from the battery pack, the inner fins 72 can allow the cooling wall 30 to deform through the elastic flexural deformation of each inclined plate 74. Thus, by having the inclined plate 74 function as an elastic deformation section, it improves the responsiveness of the battery pack relative to the cooling surfaces 32 of the cooling wall 30 and prevents unintentional plastic deformation from external inputs.

[0135] In addition, Figure 7 The example shown is an inner fin 72 with a serrated cross section. For example, an inner fin with a wavy cross section that is integrally formed as a curved cross section without a flat inclined plate portion 74 can also be used.

[0136] Figure 8 A cooling heat exchanger 80, as a third embodiment of the present invention, is shown. The cooling heat exchanger 80 has a structure in which inner fins 82 are disposed between the first member 14 and the second member 16.

[0137] The inner fin 82 is formed as a plate-shaped member having a sawtooth-shaped, wavy cross section, like the inner fin 72 of the second embodiment. The sizes of the protrusions 84 (first protrusions 84a and second protrusions 84b) of the inner fin 82 are different from those of the inner fin 72 of the second embodiment. The protrusions 84 of the present embodiment are formed in the same V shape as the protrusions 78 of the second embodiment, and are continuously provided throughout the entire front-rear direction of the inclined plate portion 74, with the end portions on the downstream side reaching the front-rear end portions of the inclined plate portion 74.

[0138] As shown in the present embodiment, the protrusions 84 can be formed on substantially the entire inner fin 82 in the flow path width direction of the cooling flow path. Further, the protrusions 84 can be provided up to the top portion 76 of the inner fin 82, and preferably, the ease of processing is achieved by providing the protrusions 84 at portions offset from the top portion 76.

[0139] Figure 9 An inner fin 90 constituting a cooling heat exchanger according to a fourth embodiment of the present application is shown. Further, the inner fin 90 of the present embodiment can be adopted in place of the inner fin 34 of the first embodiment, and therefore, in the following description, the same reference numerals are assigned to the members and portions that are substantially the same as those of the first embodiment for easy understanding.

[0140] A plurality of protrusions 48 (first protrusions 48a and second protrusions 48b) are formed in the intermediate partition portion 38 (protrusion formation portion 40, protrusion formation portion 40, protrusion formation portion 40) of the inner fin 90. In the present embodiment, the protrusions 48 are not provided in the left portion of the inner fin 90 on the upstream side of the cooling flow path 28, but are provided only in the right portion of the inner fin 90 on the downstream side of the cooling flow path 28. Thus, the effect of disturbing the flow of the heat medium based on the protrusions 48 is exerted more strongly on the downstream side than on the upstream side of the cooling flow path 28, and regions in which the effect of disturbing the flow of the heat medium is different from each other are set at different positions in the flow path length direction of the cooling flow path 28.

[0141] Further, in the present embodiment, the number of protrusions 48 and the arrangement thereof are different among the three protrusion formation portions 40, 40, and 40. Specifically, the more the protrusions 48 are formed in the protrusion formation portion 40 on the front side in the flow path width direction of the cooling flow path 28, and the narrower the intervals of the protrusions 48 in the flow path length direction. Thus, on the downstream side of the parallel flow path portion 58, the more the flow path portion 56 is located on the front side, the more strongly the effect of disturbing the flow of the heat medium based on the protrusions 48 is exerted, and regions in which the effect of disturbing the flow of the heat medium is different from each other are set at different positions in the flow path width direction of the cooling flow path 28.

[0142] Thus, if the inner fins 90 according to the present embodiment are used, the effect of disturbing the flow of the heat medium to generate a vortex or turbulence (turbulence promotion effect) is set to be locally different in the parallel flow path portion 58, and thus in a portion in which the turbulence promotion effect is exerted strongly, a high cooling performance is exerted, and the battery pack 62 can be efficiently cooled.

[0143] In particular, in the present embodiment, the turbulence promotion effect is exerted more strongly on the downstream side of the cooling flow path 28 (parallel flow path portion 58), and thus the heat medium, which is heated by the portion of the cooling wall portion 30 on the downstream side, is stirred by heat exchange with the battery pack 62, and thus effective cooling performance can be ensured on the downstream side as well. In addition, in the present embodiment, the turbulence promotion effect is exerted more strongly on the front side, and thus the front side portion of the battery pack 62, in which the terminal portion 64 is provided and the amount of heat generation easily becomes large, can be efficiently cooled.

[0144] Further, the arrangement of the protrusions 48 shown in the present embodiment is merely an example, and appropriate changes can be made, for example, in consideration of the manner of heat generation (temperature distribution) of the battery pack 62, the required cooling performance, and the like. In addition, the turbulence promotion effect based on the protrusions 48 is not only different due to the number and arrangement of the protrusions 48, but also different due to the size, shape, surface frictional resistance, and the like including the height of the protrusions 48, and thus regions in which the turbulence promotion effect is different can also be set by differences in the size and the like of the protrusions 48.

[0145] In addition, for example, in a case in which it is only necessary to set regions in which the turbulence promotion effect is different for the battery pack 62 overlapping with either one of the cooling surfaces 32, the setting of regions in which the turbulence promotion effect is different based on differences in the arrangement, number, shape, size, surface frictional resistance, and the like of the protrusions 48 can be applied to only either one of the first protrusions 48a and the second protrusions 48b as shown in the present embodiment.

[0146] Figures 10-13 An inner fin 100 constituting a cooling heat exchanger according to a fifth embodiment of the present application is shown. Further, the inner fin 100 of the present embodiment can be used in place of the inner fin 72 in the second embodiment. In addition, Figure 10 the left side in FIG. 10 is the upstream of the cooling flow path, Figure 10 the right side in FIG. 10 is the downstream of the cooling flow path.

[0147] The inner fin 100 is formed in a thin-walled plate shape from metal, synthetic resin, or the like, and extends in the left-right direction with a sawtooth-shaped or wavy cross-sectional shape, similarly to the inner fin 72 of the second embodiment. The inner fin 100 of the present embodiment is formed as a stamped metal piece.

[0148] The inner fin 100 is formed with a protrusion 102. The protrusion 102 extends in a substantially V-shape on the surface of the inner fin 100, and is formed so as to become narrower in width toward the leading end toward the upstream side of the cooling flow path. The protrusion 102 is formed in a substantially V-shape when viewed in the vertical direction. The protrusion 102 is composed of a first protrusion 102a that protrudes toward the upper surface side of the inner fin 100, and a second protrusion 102b that protrudes toward the lower surface side of the inner fin 100.

[0149] Figure 11 An enlarged view shows a cross section in the flow path length direction of one protrusion 102. In the cross section shown in Figure 11 the protrusion 102 is formed in a cross-sectional shape that becomes narrower in width in the flow path length direction toward the protruding leading end. In more detail, in the cross section shown in Figure 11 the protrusion 102 is formed in a cross-sectional shape that continuously has the following members: a protrusion top portion 104 that curves in a circular arc shape; an upstream inclined portion 108 that extends obliquely toward the upstream side from the end portion on the upstream side of the protrusion top portion 104 toward the protrusion base portion 106 (the connecting end portion in the protrusion 102 with the inclined plate portion 74); and a downstream inclined portion 110 that extends obliquely toward the downstream side from the end portion on the downstream side of the protrusion top portion 104 toward the protrusion base portion 106. Further, Figure 11 the cross section of the protrusion 102 shown in is a cross section in the flow path length direction through the center in the flow path width direction, and any cross-sectional shape of the protrusion 102 that is orthogonal to the ridge line 54 is formed in the same cross-sectional shape as Figure 11 the same cross-sectional shape as Figure 11 the same numerical range and the like as described in the description of

[0150] In the cross section in the flow path length direction shown in Figure 11 the radius of curvature R of the protrusion top portion 104 including the ridge line 54 is set to be within a range of 0.05 to 1.5 times the length dimension L in the flow path length direction of the protrusion base portion 106, and more preferably within a range of 0.2 to 1.45 times. By setting the radius of curvature R of the protrusion top portion 104 to be 0.05 times or more of the length dimension L of the protrusion base portion 106, the protrusion top portion 104 is formed in a smooth circular arc cross section substantially without becoming a corner portion. In addition, by setting the radius of curvature R of the protrusion top portion 104 to be 1.5 times or less of the length dimension L of the protrusion base portion 106, it is possible to prevent the length dimension in the flow path length direction of the protrusion 102 from becoming excessively long, and it is possible to set the inclination angles a, b of the upstream inclined portion 108 and the downstream inclined portion 110 that are smoothly continuous with the protrusion top portion 104 to be sufficiently large. Further, in the present embodiment, the radius of curvature R of the protrusion top portion 104 is set to be within a range of 0.05 to 0.5 times the length dimension L of the protrusion base portion 106.

[0151] The upstream inclined portion 108 can be curved, and in the present embodiment is formed in a straight line shape. The upper end portion of the upstream inclined portion 108 extends from the end portion on the upstream side of the protrusion top portion 104 in a tangential direction, and is continuous with the protrusion top portion 104 without a corner portion and smoothly. The lower end portion of the upstream inclined portion 108 can be curved in a circular arc shape, and in this case, it is preferable that the lower end portion of the upstream inclined portion 108 be continuous with the inclined plate portion 74 that constitutes the bottom surface of the cooling flow path 28 without a corner portion and smoothly.

[0152] The inclination angle a of the upstream inclined portion 108 with respect to the inclined plate portion 74 that constitutes the bottom surface of the cooling flow path 28 is set to a range of 20 to 70°, and more preferably to a range of 30 to 60°. Further, in the case where the upstream inclined portion 108 is curved, the inclination angle a of the upstream inclined portion 108 with respect to the inclined plate portion 74 can be, for example, grasped as an average value of the inclination angle of the upstream inclined portion 108 with respect to the inclined plate portion 74.

[0153] By setting the inclination angle a of the upstream inclined portion 108 to 20° or more, the flow of the heat medium from the upstream side toward the protrusion 102 is efficiently disturbed by the upstream inclined portion 108 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 action is achieved. In addition, by setting the inclination angle a of the upstream inclined portion 108 to 70° or less, it is possible to prevent the flow of the heat medium from being excessively restricted by the protrusion 102.

[0154] The downstream inclined portion 110 can be curved, and in the present embodiment is formed in a straight line shape. The upper end portion of the downstream inclined portion 110 extends from the end portion on the downstream side of the protrusion top portion 104 in a tangential direction, and is continuous with the protrusion top portion 104 without a corner portion and smoothly. The lower end portion of the downstream inclined portion 110 can be curved in a circular arc shape, and in this case, it is preferable that the lower end portion of the downstream inclined portion 110 be continuous with the inclined plate portion 74 that constitutes the bottom surface of the cooling flow path 28 without a corner portion and smoothly.

[0155] The inclination angle β of the downstream inclined portion 110 with respect to the inclined plate portion 74 that constitutes the bottom surface of the cooling flow path 28 is set to a range of 20 to 70°, and more preferably to a range of 30 to 60°. Further, in the case where the downstream inclined portion 110 is curved, the inclination angle β of the downstream inclined portion 110 with respect to the inclined plate portion 74 can be, for example, grasped as an average value of the inclination angle of the downstream inclined portion 110 with respect to the inclined plate portion 74.

[0156] By setting the inclination angle β of the downstream inclined portion 110 to 20° or more, the flow of the heat medium that passes over the protrusion 102 is easily peeled off from the downstream inclined portion 110, and thus an effect of easily generating a disturbed flow after the flow is disturbed by a vortex or the like on the downstream side of the protrusion 102 can be expected. In addition, by setting the inclination angle β of the downstream inclined portion 110 to 70° or less, the flow of the heat medium along the downstream inclined portion 110 is also ensured, and an effect of efficient stirring based on the heat medium that converges from the flow peeled off from the downstream inclined portion 110 can be expected.

[0157] However, as Figure 12 , Figure 13 indicated, the protrusion height dimension of the protrusion 102 of the present embodiment varies in the flow path width direction, that is, the front-rear direction. Also, the plurality of protrusions 102 are composed of: a central low protrusion 116 whose central portion in the front-rear direction is formed as a low protruding portion 112 having a low protrusion height and whose both end portions in the front-rear direction are formed as a high protruding portion 114 having a high protrusion height; and a central high protrusion 118 whose central portion in the front-rear direction is formed as a high protruding portion 114 having a high protrusion height and whose both end portions in the front-rear direction are formed as a low protruding portion 112 having a low protrusion height. Both the first protrusion 102a and the second protrusion 102b include a plurality of the central low protrusions 116 and a plurality of the central high protrusions 118. Figure 11 , Figure 12 In

[0158] As Figure 10 indicated, among the plurality of the first protrusions 102a and the second protrusions 102b arranged in the flow path length direction, both the central low protrusion 116 and the central high protrusion 118 are alternately arranged in the flow path length direction, that is, the left-right direction. Therefore, in the central portion in the flow path width direction of the flow path portion 56, the low protruding portion 112 of the central low protrusion 116 and the high protruding portion 114 of the central high protrusion 118 are arranged alternately in the flow path length direction. In addition, in both end portions in the flow path width direction of the flow path portion 56, the high protruding portion 114 of the central low protrusion 116, the high protruding portion 114, and the low protruding portion 112 of the central high protrusion 118, and the low protruding portion 112 are arranged alternately in the flow path length direction.

[0159] According to the inner fin 100 of the present embodiment described above, in the high protruding portion 114 having a large protrusion height dimension, the stirring effect of the heat medium can be obtained more strongly, and by the low protruding portion 112 having a small protrusion height dimension, the flow resistance of the heat medium is suppressed, and reduction of pressure loss is achieved.

[0160] In this embodiment, the low protrusion 112 and the high protrusion 114 are arranged adjacent to each other along the length of the flow path. The hot medium flowing smoothly in the low protrusion 112 is efficiently stirred by the high protrusion 114 located downstream of the low protrusion 112, thereby achieving a significant improvement in cooling performance. In addition, the hot medium, which is more strongly disturbed by the high protrusion 114, flows more smoothly in the low protrusion 112 located downstream of the high protrusion 114, thus reducing the likelihood of flow stagnation.

[0161] Furthermore, the hot medium flows easily in the low protrusion 112, where the flow resistance is lower than that of the high protrusion 114. By alternating the central low protrusion 116 and the central high protrusion 118 along the length of the flow path, the low protrusion 112 is alternately located at the central portion and both ends in the width direction of the flow path along the length of the flow path. Therefore, in the flow path 56, a flow of hot medium meandering along the width direction of the flow path in a manner connecting the low protrusions 112 is also generated, which can be expected to eliminate the effect of eliminating the deviation in the temperature distribution of the hot medium in the width direction of the flow path.

[0162] Figures 14-16 The inner fins 120 constituting a cooling heat exchanger according to the sixth embodiment of the present invention are shown. The inner fins 120 have the same serrated cross-sectional shape as the inner fins 100 of the fifth embodiment.

[0163] The inner fin 120 is provided with protrusions 122. Each protrusion 122 is composed of multiple first protrusions 122a protruding from the upper surface and multiple second protrusions 122b protruding from the lower surface. Similar to the protrusions 102 of the inner fin 100, the protrusions 122 are generally formed in a V-shape when viewed vertically, but on the upstream side (… Figure 14 The end of the protrusion 122 (on the left side) is discontinuous. That is, in this embodiment, the protrusion 122 extends downstream from the center in the flow path width direction towards both sides. Figure 14 It consists of two mutually separated protrusions 124, 124 that extend obliquely to the right side of the middle.

[0164] The protrusion 122 in this embodiment, like the protrusion 102 in the fifth embodiment, includes a central low protrusion 116 and a central high protrusion 118. Furthermore, in this embodiment, a plurality of central low protrusions 116 and a plurality of central high protrusions 118 are arranged alternately in the flow path length direction. Moreover, the protrusion 122 in this embodiment is composed of two protrusions 124, 124 that are separated from each other at their central portions in the flow path width direction. Therefore, the low protrusion 112 of the central low protrusion 116 and the high protrusion 114 of the central high protrusion 118, located on the central side in the flow path width direction, are respectively provided on the two protrusions 124, 124.

[0165] The same effect as that of the inner fin 100 in the fifth embodiment can be obtained by forming the inner fin 120 according to the structure described in this embodiment. In addition, the protrusion 122 is only provided on the inclined plate portion 74 and not formed on the top 76, thereby making the forming based on the protrusion 122 easier.

[0166] Figure 17 A portion of the inner fins 130 constituting a cooling heat exchanger according to the seventh embodiment of this utility model is shown. In the inner fins 130, the protrusion height and spacing of a plurality of protrusions 102 arranged along the length of the flow path vary.

[0167] More specifically, multiple protrusions 102 move downstream ( Figure 17 The protrusion height of the protrusion 102 increases as it moves downstream, and the spacing between adjacent protrusions 102 in the flow path length direction narrows. Furthermore, the rate of change of the protrusion height of the protrusion 102 and the rate of change of the spacing between protrusions 102 can vary; in this embodiment, these rates of change are set to constant. The protrusion height of the protrusion 102 varies in the flow path width direction, and in a comparison of low protrusions 112 and / or high protrusions 114, the protrusion height becomes higher towards the downstream side.

[0168] Thus, if the protrusion height of the protrusion 102 is set to increase towards the downstream side, the stirring effect based on the protrusion 102 can be more effectively utilized on the downstream side where the temperature difference between the upper and lower heat mediums tends to increase due to heat exchange, thereby maintaining cooling performance further downstream. Furthermore, by setting the protrusions 102 and their spacing to narrow towards the downstream side, the stirring effect based on the protrusion 102 can also be obtained more effectively on the downstream side, maintaining cooling performance further downstream.

[0169] The embodiments of this utility model have been described in detail above, but this utility model is not limited to its specific description. For example, the specific shape of the inner fin is not limited to the shape shown in the first to fourth embodiments. As long as the cooling flow path 28 is divided into two parts in the opposing direction of the pair of cooling wall portions 30, 30 to achieve a double-sided cooling structure, there is no particular limitation. In addition, it is preferable that the inner fin is also divided into cooling flow paths 28 in the flow path width direction, but the division in the flow path width direction is not necessary. It is possible to divide only the two flow path regions: the cooling wall portion 30 side of the first member 14 and the cooling wall portion 30 side of the second member 16.

[0170] The outer wall component is not limited to a structure where the first component 14 and the second component 16 overlap. For example, a structure can be adopted in which a pair of covers, each having a supply hole and a discharge hole, are installed at both ends of an outer wall body that is formed into a cylindrical shape and integrally has a pair of cooling walls. In this structure, for example, before installing the covers onto the outer wall body, the inner fins are inserted into the inner circumference of the outer wall body in the axial direction, thereby allowing the inner fins to be accommodated and disposed in the internal region of the outer wall component. Furthermore, the cylindrical outer wall body can be easily manufactured, for example, by extrusion molding or drawing molding of a metal material.

[0171] The inner fins may not have elastic deformation sections, and the whole can be formed as a rigid body. In this case, the inner fins can also be expected to function as reinforcing members, thereby improving the deformation rigidity and load resistance of the cooling heat exchanger.

[0172] The protrusion is not limited to a V-shape; for example, it can also be hemispherical, columnar, or stepped. Furthermore, the protrusion can also be formed by ribs extending in a direction substantially orthogonal to the flow direction of the heat medium. Additionally, the V-shaped protrusion is not limited to a strict V-shape; as long as it is formed integrally as a V-shape on the surface of the inner fin, bending, partial cuts, and differences in the angle of inclination relative to the flow path direction on both sides of the width direction are all permissible. Moreover, the protrusion can also be formed, for example, into a V-shape that narrows towards the downstream side, the opposite of the embodiments described above.

[0173] Figure 11 The diagram shows a protrusion 102 with an inclination angle in the range of 20 to 70° for the upstream inclined portion 108. For example, it is also possible to use a protrusion 102 with an inclination angle in the range of 20 to 70°. Figure 18 The protrusion shown is 140. That is, Figure 18 The protrusion 140 has a large radius of curvature at its top 142, and both the upstream inclined portion 144 (as the upstream side) and the downstream inclined portion 146 (as the downstream side) are formed with curved surfaces. The connection is configured such that the protrusion top 142 and the inclined plate portion 74 are smoothly continuous without corners in the cross-section along the flow path length direction. Therefore, the overall cross-sectional shape of the protrusion 140 in the flow path length direction is formed as a continuous curved shape. Figure 18 The radius of curvature R of the arc-shaped protrusion top 142 formed in the cross-section along the flow path length of the protrusion 140 is preferably 0.7 times or more, and more preferably 1 times or more, relative to the length dimension L of the protrusion base 148. Furthermore, in Figure 18 In the cross-section along the length of the flow path shown, in this embodiment, the inclination angle α of the upstream inclined portion 144 relative to the bottom surface of the flow path portion 56 is set to 25° or less, and the inclination angle β of the downstream inclined portion 146 relative to the bottom surface of the flow path portion 56 is set to 25° or less. In summary, compared to... Figure 11The protrusion 102 shown, the protrusion 140 of the present embodiment is formed in a flat shape in which the ratio of the protruding height dimension in the cross section in the flow path length direction to the length dimension L of the protrusion base 148 is small, and is formed so that the rate of change in the flow path cross-sectional area of the protrusion 140 is small. According to the protrusion 140 described above, pressure loss due to the flow of the heat medium over the protrusion 140 is suppressed, and thus the heat medium can be circulated using an inexpensive pump with relatively low performance.

[0174] The protrusions do not need to be continuously provided throughout the flow path width direction of the flow path portion, and preferably the width dimension of the protrusions in the flow path width direction is set to 50% or more, and more preferably 70% or more, of the flow path width dimension of the flow path portion. Thereby, the flow around the protrusions is restricted, and the flow over the protrusions is easily generated, and thus the effect of disturbing the flow of the heat medium based on the protrusions is efficiently exerted. Further, in the case where the inner fins are zigzag, or in the case where the flow path width dimension of the flow path portion varies in the flow path depth direction, preferably the width dimension of the protrusions is set to 50% or more, and more preferably 70% or more, of the maximum width dimension of the flow path portion (the width dimension between the top portions in the case of the zigzag inner fins). In addition, in the case where the flow path width dimension of the flow path portion varies in the flow path length direction, preferably the width dimension of the protrusions is set within the above range with respect to the flow path width dimension at the position where the protrusions are provided.

[0175] The first member 14 and the second member 16 can be made of synthetic resin. In this case, in order to ensure high thermal conductivity, the first member 14 and the second member 16 are formed of, for example, a thermally conductive synthetic resin in which a thermally conductive filler such as alumina (alumina soil), silica, silicon carbide, or the like is mixed in a synthetic resin material such as polyphenylene sulfide (PPS), polyamide, polypropylene, polybutylene terephthalate (PBT), or the like.

[0176] In the case where the battery group 62 is arranged in the stacking direction of the cooling heat exchangers 10, the battery group 62 can be cooled from both the upper and lower sides. Similarly, the battery group 62 can be cooled from both the upper and lower sides in the case where the cooling heat exchangers 10 are arranged in the stacking direction of the battery group 62. Figure 6 In the case where the battery group 62 is arranged in the stacking direction of the cooling heat exchangers 10, the battery group 62 can be cooled from both the upper and lower sides. Similarly, the battery group 62 can be cooled from both the upper and lower sides in the case where the cooling heat exchangers 10 are arranged in the stacking direction of the battery group 62. Figure 6 In the case where the battery group 62 is arranged in the stacking direction of the cooling heat exchangers 10, the battery group 62 can be cooled from both the upper and lower sides. Similarly, the battery group 62 can be cooled from both the upper and lower sides in the case where the cooling heat exchangers 10 are arranged in the stacking direction of the battery group 62.

[0177] Further, in a case where the plurality of cooling heat exchangers 10 are arranged in a stacked manner, for example, the supply holes and the discharge holes can be formed at both end portions of the second member 16, and the supply holes 20 and the discharge holes 22 of the first member 14 in one of the cooling heat exchangers 10 arranged adjacent in the vertical direction and the supply holes and the discharge holes of the second member 16 in the other of the cooling heat exchangers 10 can be connected to each other to communicate. Thus, the cooling flow path 28 of each of the plurality of cooling heat exchangers 10 arranged in the stacked manner can be connected to one external flow path, and the heat medium can be uniformly supplied and discharged with respect to these cooling flow paths 28.

[0178] The cooling target is not limited to the battery for the electrically powered vehicle, and can be, for example, a stationary type battery for industrial use or the like. In the first embodiment described above, the plurality of battery groups 62 are arranged on the cooling surface 32 of one cooling heat exchanger 10, but one battery group 62 can be arranged on the cooling surface 32 of one cooling heat exchanger 10. Further, one battery group 62 can be arranged across the plurality of cooling heat exchangers 10.

Claims

1. A cooling heat exchanger (10, 70, 80) that is internally formed with a cooling flow path (28) for a cooling heat medium to flow, and cools a cooling object (62) that overlaps a cooling surface (32) provided on a surface, wherein the cooling heat exchanger (10, 70, 80) is provided with a hollow outer wall member (12) that internally has the cooling flow path (28), and a pair of cooling wall portions (30) that have the cooling surface (32) on a surface are provided in mutually opposing portions in the outer wall member (12), an inner fin (34, 72, 82, 90, 100, 120, 130) that divides an internal region of the outer wall member (12) into two portions in an opposing direction of the pair of cooling wall portions (30) is provided in an internal region of the outer wall member (12), a first protrusion (48a, 78a, 84a, 102a, 122a) and a second protrusion (48b, 78b, 84b, 102b, 122b) that protrude in each one face are integrally formed in the inner fin (34, 72, 82, 90, 100, 120, 130).

2. The cooling heat exchanger (10, 70, 80) according to claim 1, wherein the cooling flow path (28) has a parallel flow path portion (58) that is composed of a plurality of flow path portions (56) that are adjacently and parallelly extended in a flow path width direction, divided by the inner fin (34, 72, 82, 90, 100, 120, 130), flow directions of the heat medium in the plurality of flow path portions (56) that constitute the parallel flow path portion (58) are the same.

3. The cooling heat exchanger (10, 70, 80) according to claim 1 or 2, wherein the outer wall member (12) is formed in a structure in which a first member (14) that constitutes one of the cooling wall portions (30) and a second member (16) that constitutes the other of the cooling wall portions (30) overlap each other in an opposing direction of the pair of cooling wall portions (30), the inner fin (34, 72, 82, 90, 100, 120, 130) is provided between opposing faces of the first member (14) and the second member (16).

4. The cooling heat exchanger (70, 80) according to claim 1 or 2, wherein the inner fin (72, 82, 100, 120) has a sawtooth-shaped, wave-shaped folded cross section in an opposing direction of the pair of cooling wall portions (30), the first protrusion (78a, 84a, 102a, 122a) and the second protrusion (78b, 84b, 102b, 122b) are formed between adjacent folded tops (76) in the inner fin (72, 82, 100, 120).

5. The cooling heat exchanger (10) according to claim 1 or 2, wherein ​ The inner fin (34, 90) has an intermediate partition portion (38) disposed separately from both of the pair of cooling wall portions (30) in the outer wall member (12), and divides the opposing surfaces of the pair of cooling wall portions (30) in the opposing direction of the pair of cooling wall portions (30) into two portions, The first protrusion (48a) and the second protrusion (48b) are formed in the intermediate partition portion (38), The inner fin (34, 90) has a partition wall portion (42) protruding to both sides from the intermediate partition portion (38) toward the pair of cooling wall portions (30), and the inner region of the outer wall member (12) is divided into a plurality of flow path portions (56) in the flow path width direction of the cooling flow path (28) by the partition wall portion (42).

6. The cooling heat exchanger (10, 70, 80) according to claim 1 or 2, wherein The first protrusion (48a, 78a, 84a, 102a, 122a) and the second protrusion (48b, 78b, 84b, 102b, 122b) are formed in a V-shape on the surface of the inner fin (34, 72, 82, 100, 120), and are formed to be narrower in width toward the upstream side of the cooling flow path (28).

7. The cooling heat exchanger (10, 70, 80) according to claim 1 or 2, wherein The inner fin (34, 72, 82, 90, 100, 120, 130) is disposed partially in the flow path length direction of the cooling flow path (28).

8. The cooling heat exchanger (10, 70, 80) according to claim 1 or 2, wherein In the cooling flow path (28), regions in which the flow of the heat medium is disturbed by at least one of the plurality of first protrusions (48a, 78a, 84a, 102a, 122a) and the plurality of second protrusions (48b, 78b, 84b, 102b, 122b) are different in the effect of disturbing the flow of the heat medium.

9. The cooling heat exchanger according to claim 8, wherein The regions in which the flow of the heat medium is disturbed are different in the effect of disturbing the flow of the heat medium and are disposed at different positions in the flow direction of the heat medium in the cooling flow path (28).

10. The cooling heat exchanger according to claim 9, wherein The regions in which the flow of the heat medium is disturbed are different in the effect of disturbing the flow of the heat medium and are disposed at different positions in the flow direction of the heat medium in the cooling flow path (28), and the effect of disturbing the flow of the heat medium is stronger in the region on the more downstream side.

11. The cooling heat exchanger (10) according to claim 8, wherein The cooling flow path (28) has a parallel flow path portion (58) composed of a plurality of flow path portions (56) that are adjacent and extend in parallel by being divided by the inner fin (34), The flow direction of the heat medium in the plurality of flow path portions (56) that constitute the parallel flow path portion (58) is the same, At least one set of adjacent flow path portions (56) in the parallel flow path portion (58) is provided with the regions in which the flow of the heat medium is disturbed, which are different in the effect of disturbing the flow of the heat medium.

12. The cooling heat exchanger (10, 70, 80) according to claim 8, wherein, The regions in which the flow of the heat medium is disturbed, which are different in the effect of disturbing the flow of the heat medium, are provided by at least one of a difference in the distance between a plurality of the first protrusions (48a, 78a, 84a, 102a, 122a) and a difference in the distance between a plurality of the second protrusions (48b, 78b, 84b, 102b, 122b) in the flow direction of the heat medium.

13. The cooling heat exchanger (10, 70, 80) according to claim 8, wherein, The regions in which the effects of disturbing the flow of the heat medium differ from each other are set by at least one of a difference in height among a plurality of the first protrusions (48a, 78a, 84a, 102a, 122a) and a difference in height among a plurality of the second protrusions (48b, 78b, 84b, 102b, 122b).

14. The cooling heat exchanger (10, 70, 80) according to claim 1 or 2, wherein The cooling object (62) is a battery.

15. The cooling heat exchanger (10, 70) according to claim 1 or 2, wherein The inner fins (34, 72) are provided with elastic deformation portions that allow the approach deformation of the pair of cooling wall portions (30) by elastic deformation.

16. The cooling heat exchanger (10, 80) according to claim 1 or 2, wherein The first protrusions (48a, 84a) and the second protrusions (48b, 84b) respectively extend throughout the entire flow path width of the cooling flow path (28), and are continuous with the side wall portions of the cooling flow path (28) at both end portions.

17. The cooling heat exchanger according to claim 1 or 2, wherein The protrusion height of at least one of the first protrusions (102a, 122a) and the second protrusions (102b, 122b) varies in the flow path width direction of the cooling flow path (28), and either a low protrusion portion (112) having a low protrusion height or a high protrusion portion (114) having a high protrusion height is located at a central portion in the flow path width direction, and the other of the low protrusion portion (112) and the high protrusion portion (114) is respectively located at both end portions in the flow path width direction of the first protrusions (102a, 122a) and the second protrusions (102b, 122b).

18. The cooling heat exchanger according to claim 17, wherein At least one of the first protrusions (102a, 122a) and the second protrusions (102b, 122b) arranged in the flow path length direction of the cooling flow path (28) is configured as a central low protrusion (116) in which the low protrusion portion (112) is provided at a central portion in the flow path width direction of the cooling flow path (28) and the high protrusion portion (114) is provided at both end portions, and a central high protrusion (118) in which the high protrusion portion (114) is provided at a central portion in the flow path width direction of the cooling flow path (28) and the low protrusion portion (112) is provided at both end portions are alternately arranged in the flow path length direction of the cooling flow path (28).

19. The cooling heat exchanger according to claim 1 or 2, wherein At least one of the first protrusions (102a, 122a) and the second protrusions (102b, 122b) is formed in a cross-sectional shape in which a cross section in the flow path length direction of the cooling flow path (28) is tapered toward a protrusion tip end, and a protrusion tip portion (104, 142) in an arc shape, an upstream inclined portion (108, 144) that extends obliquely toward an upstream side of the cooling flow path (28) from the protrusion tip portion (104, 142) toward a bottom surface side of the cooling flow path (28) that is a protrusion base portion (106, 148), and a downstream inclined portion (110, 146) that extends obliquely toward a downstream side from the protrusion tip portion (104, 142) toward the protrusion base portion (106, 148) are continuously provided without corners and smoothly.

20. The cooling heat exchanger according to claim 19, wherein In a cross section in the flow path length direction of the cooling flow path (28), a radius of curvature (R) of the protrusion top (104) is in a range of 0.05 to 1.5 times a length dimension (L) of the protrusion base (106), and in a cross section in the flow path length direction of the cooling flow path (28), an inclination angle of the upstream inclined portion (108) with respect to the bottom surface of the cooling flow path (28) is in a range of 20° to 70°.

21. The cooling heat exchanger according to claim 19, wherein In a cross section in the flow path length direction of the cooling flow path (28), an inclination angle of the upstream inclined portion (144) with respect to the bottom surface of the cooling flow path (28) is 25° or less.

22. The cooling heat exchanger according to claim 1 or 2, wherein In at least one of the first protrusions (102a) and the second protrusions (102b) arranged in the flow path length direction in the cooling flow path (28), a protruding height is higher toward the downstream.

23. The cooling heat exchanger according to claim 1 or 2, wherein In at least one of the first protrusions (48a) and the second protrusions (48b) arranged in the flow path length direction in the cooling flow path (28), a spacing in the flow path length direction of the cooling flow path (28) is narrower toward the downstream.

24. The cooling heat exchanger according to claim 1 or 2, wherein In at least one of the first protrusions (48a) and the second protrusions (48b) arranged in the flow path length direction in the cooling flow path (28), a protruding height is higher toward the downstream, and a spacing in the flow path length direction of the cooling flow path (28) is narrower toward the downstream.

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