Cooling heat exchanger

Abstract

The utility model provides a new structure's cooling heat exchanger who can expect the further improvement of cooling performance. Cooling heat exchanger (10) has the cooling flow path (18) who flows for cooling between two plates (14, 16) with the cooling surface (12) of overlapping with the cooling object in at least one side, wherein, the protruding (24) is arranged in the wall portion of cooling flow path (18), the protruding (24) extends in the cross direction relative to the flow path length direction of cooling flow path (18), a pair of inclined portion (26, 26) who expands to the both sides of flow path width direction towards the flow path length direction of cooling flow path (18) is arranged in the protruding (24), the low protruding portion (28) of low height and the high protruding portion (30) of high height are arranged in a pair of inclined portion (26, 26).

Description

Technical Field

[0001] This invention relates to a cooling heat exchanger for cooling objects such as batteries used in electric vehicles. Background Technology

[0002] Previously, cooling heat exchangers for cooling batteries, inverters, and the like were known. These cooling heat exchangers, such as those disclosed in Japanese Patent Application Publication No. 2011-165939 (Patent Document 1), have a structure in which a refrigerant passage for a cooling medium flows is formed in the internal region between opposing portions of a pair of overlapping outer shell plates. Furthermore, the surface of the outer shell plates is cooled through heat exchange with the cooling medium flowing through the refrigerant passage, thereby cooling the object overlapping the surface.

[0003] Existing technical documents

[0004] Patent documents

[0005] Patent Document 1: Japanese Patent Application Publication No. 2011-165939 Utility Model Content

[0006] Problems to be solved by utility models

[0007] However, the heat exchanger for cooling as described in Patent Document 1 has the following problems: the cooling medium flowing near the object being cooled in the refrigerant passage is easily heated due to heat exchange with the object being cooled; on the other hand, the cooling medium flowing away from the object being cooled is difficult to generate heat exchange with the object being cooled, and thus is unlikely to contribute to cooling performance. Therefore, in Patent Document 1, a protrusion (reduction section) is formed protruding into the refrigerant passage, and the cooling medium is stirred as it passes over the protrusion.

[0008] However, the inventors have learned through research that even with a protrusion like that in Patent Document 1, the cooling performance is still insufficient.

[0009] The problem this invention aims to solve is to provide a novel cooling heat exchanger with a structure that can be expected to further improve cooling performance.

[0010] means for solving problems

[0011] The following describes preferred embodiments for understanding this utility model. These embodiments are illustrative and can be appropriately combined with each other. Furthermore, the multiple constituent elements described in each embodiment can be independently identified and used as much as possible, and can also be appropriately combined with any constituent element described in other embodiments. Therefore, this utility model is not limited to the embodiments described below, and various other embodiments can be implemented.

[0012] The first embodiment is a heat exchanger for cooling, wherein a cooling flow path for the flow of a heat medium for cooling is formed between two plates, at least one of which has a cooling surface overlapping the object being cooled. A protrusion is provided on the wall of the cooling flow path, the protrusion extending in a direction intersecting the flow path length direction. The protrusion is provided with a pair of inclined portions extending to both sides in the flow path width direction in the flow path length direction. The pair of inclined portions are provided with a low protrusion with a low height and a high protrusion with a high height.

[0013] According to the cooling heat exchanger configured to follow this method, because it is shaped with a pair of inclined portions protruding from it, the flow of the hot medium across the inclined portions in a substantially orthogonal direction is directed in a direction inclined towards the width of the flow path relative to the length of the flow path. In this way, the flow of the hot medium is generated not only in the length of the flow path but also in the width of the flow path, which can more effectively obtain the stirring effect brought about by the turbulence of the hot medium, and can suppress the temperature rise at the position near the cooling surface of the hot medium even further downstream.

[0014] Furthermore, because the low and high protrusions, with varying heights, are positioned at different locations along the flow path width within the protrusion, the stirring effect and flow velocity of the heat medium caused by the protrusion can differ along the flow path width. This allows for adjustment of cooling performance along the flow path width, enabling, for example, the achievement of cooling performance more closely aligned with the temperature distribution of the object being cooled.

[0015] The second method is based on the cooling heat exchanger described in the first method, wherein the protrusion is V-shaped when viewed from the protruding direction.

[0016] According to the cooling heat exchanger configured to follow this method, since the protrusion is V-shaped, the heat medium after the protrusion is easily formed into turbulent flow such as eddies, thus achieving improved cooling performance by efficiently agitating the heat medium.

[0017] The third approach is based on the cooling heat exchanger described in the first or second approach, wherein the protrusion height of the protrusion gradually increases from the low protrusion to the high protrusion.

[0018] According to the cooling heat exchanger configured to follow this method, it is possible to achieve smooth flow of the heat medium while preventing the flow pattern of the heat medium from changing drastically in the flow path width direction, and to effectively regulate the cooling performance in the flow path width direction by gradually changing the stirring effect and flow rate caused by the protrusions in the flow path width direction.

[0019] The fourth method is based on the heat exchanger for cooling described in any one of the first to third methods, wherein multiple protrusions are arranged in the flow path length direction of the cooling flow path, and the multiple protrusions arranged in the flow path length direction include multiple types in which the low protrusions are positioned differently in the flow path width direction and the high protrusions are positioned differently in the flow path width direction.

[0020] According to a cooling heat exchanger configured to follow this method, for example, when the cooling performance in the required flow path width direction varies in the flow path length direction, the required cooling performance can be achieved to a greater extent by appropriately configuring multiple types of protrusions with different positions of low protrusions and high protrusions.

[0021] The fifth method is based on the heat exchanger for cooling described in any one of the first to fourth methods, wherein either the low protrusion or the high protrusion is located in the central portion of the flow path width direction of the protrusion, and either the low protrusion or the high protrusion is located at both ends of the flow path width direction of the protrusion.

[0022] According to a heat exchanger configured to follow this method, the flow of the hot medium flowing through the central portion of the flow path width direction across the protrusion and the flow of the hot medium flowing through the two ends of the flow path width direction across the protrusion can be made different in terms of stirring effect, flow rate, etc. Therefore, the effect of the protrusion on the cooling performance can be made different between the central portion and the two ends of the flow path width direction, and the cooling performance can be adjusted in the flow path width direction.

[0023] The sixth method is based on the heat exchanger for cooling described in the fifth method, wherein a plurality of protrusions are arranged in the length direction of the cooling flow path, and the plurality of protrusions are configured such that a first protrusion and a second protrusion are alternately arranged in the length direction of the flow path. The first protrusion has a low protrusion in the central part of the flow path width direction and a high protrusion in both ends. The second protrusion has a high protrusion in the central part of the flow path width direction and a low protrusion in both ends.

[0024] According to a cooling heat exchanger configured in accordance with this method, a first protrusion with a low protrusion in the central portion of the flow path width direction and a second protrusion with low protrusions at both ends of the flow path width direction are alternately arranged in the flow path length direction. Thus, for example, the flow of the hot medium connecting the low protrusions, which easily suppress flow resistance, becomes meandering in the flow path width direction, thereby achieving a stirring effect of the hot medium in the flow path width direction. Furthermore, for example, the hot medium flowing from one low protrusion to the next high protrusion can also be expected to be efficiently stirred by colliding with the high protrusion with relatively low flow resistance.

[0025] The seventh method is based on a cooling heat exchanger described in any one of the first to sixth methods, wherein the cooling surface is provided on one of the plates and the protrusion is formed on the other plate.

[0026] According to a cooling heat exchanger configured in accordance with this method, by providing a protrusion on a plate opposite to the plate having a cooling surface, the heat medium flowing away from the cooling surface, which is difficult to exchange heat with the object being cooled, can be effectively stirred by the protrusion. Furthermore, because the cooling surface is provided on a plate different from the plate where the protrusion is formed, it is possible to prevent the protrusion from affecting the shape of the cooling surface, for example.

[0027] The eighth embodiment is based on a cooling heat exchanger described in any one of the first to seventh embodiments, wherein a support portion is provided that protrudes from the plate on the other side and is fixedly mounted to the plate on one side, the protrusion being adjacent to the downstream side of the support portion and disposed on the side.

[0028] According to the cooling heat exchanger configured to follow this method, since the flow of the hot medium separated in the flow path width direction by the support is guided to the protrusion located on the downstream side of the support, the stirring effect brought by the protrusion can be obtained efficiently.

[0029] The ninth embodiment is based on a cooling heat exchanger described in any one of the first to eighth embodiments, wherein both plates have cooling surfaces, an inner fin is disposed between the two plates, cooling flow paths are formed on both sides of the inner fin, and the inner fin is provided with a surface protrusion protruding toward one of the cooling flow paths as a protrusion, and a back protrusion protruding toward the other cooling flow path as a protrusion.

[0030] According to a cooling heat exchanger configured to follow this method, for example, the object to be cooled can be cooled separately through cooling surfaces on both sides. Furthermore, since the protrusions are not plates with cooling surfaces but are formed on inner fins disposed between plates, it is possible to prevent the protrusions from affecting the shape of the cooling surfaces. Because the inner fins are provided with surface protrusions and back protrusions protruding to one side, the stirring effect brought by the protrusions can be effectively utilized on either side of the two cooling flow paths separated by the inner fins.

[0031] The tenth embodiment is based on a cooling heat exchanger described in any one of the first to ninth embodiments, wherein the cooling flow path has a parallel flow path section composed of a plurality of flow path sections extending in parallel, and a plurality of protrusions are arranged in a flow path length direction relative to the flow path section constituting the parallel flow path section.

[0032] According to a cooling heat exchanger configured to follow this method, for example, it is possible to obtain a larger cooling surface area while ensuring the flow path width of the cooling flow path in the parallel flow path sections, and to regulate the flow of the heat medium by adjusting the flow path width of each flow path section. Furthermore, by providing multiple protrusions arranged along the length direction relative to the flow path sections, improved cooling performance based on the stirring effect of the protrusions is achieved over a large range along the length direction of the flow path sections. Moreover, in this method, the protrusions do not necessarily need to be provided in all flow path sections; it is sufficient to provide multiple protrusions arranged along the length direction of the flow path in at least one flow path section.

[0033] The eleventh method is based on the heat exchanger for cooling described in any one of the first to tenth methods, wherein the flow path length of the cooling flow path is 200 mm or more.

[0034] In a cooling flow path of 200 mm or more, such as a cooling heat exchanger with a structure following this method, the downstream heat medium can easily become hotter due to prolonged heat exchange with the object being cooled. Therefore, by providing protrusions with low and high protrusions in a pair of inclined sections to efficiently stir the heat medium, even when the cooling flow path is long, the temperature rise of the downstream heat medium can be suppressed, and the cooling performance can be maintained further downstream.

[0035] The twelfth embodiment is based on a cooling heat exchanger described in any one of the first to eleventh embodiments, wherein the protrusion extends throughout the entire width of the cooling flow path and is continuous with the sidewall portion of the cooling flow path at both ends.

[0036] A heat exchanger for cooling, configured according to this method, can effectively improve cooling performance by preventing the flow of hot medium between the sidewall of the cooling flow path and the protrusion, thus preventing it from meandering at the protrusion. Furthermore, when the protrusion is far from the sidewall of the cooling flow path, the flow velocity of the hot medium between the sidewall of the cooling flow path and the two ends of the protrusion tends to increase, thereby posing a risk of scraping between the wall of the cooling flow path and the protrusion. However, in the heat exchanger for cooling according to this method, the protrusion extends throughout the entire width of the flow path and is continuous with the sidewall of the cooling flow path, thereby preventing the flow of hot medium between the sidewall of the cooling flow path and the protrusion, and preventing scraping between the wall of the cooling flow path and the protrusion.

[0037] The thirteenth embodiment is based on the heat exchanger for cooling described in any one of the first to twelfth embodiments, wherein the protrusion has a cross-sectional shape that tapers towards the protruding front end in the cross-section of the cooling flow path along the length of the flow path, and the arc-shaped protrusion top, the upstream inclined portion extending obliquely from the protrusion top towards the protrusion base which is the bottom surface side of the cooling flow path towards the upstream side of the cooling flow path, and the downstream inclined portion extending obliquely from the protrusion top towards the protrusion base towards the downstream side are provided without corners and are smoothly continuous.

[0038] According to the cooling heat exchanger configured to follow this method, the protruding surface has a smooth and continuous cross-section in the flow path length direction, thereby enabling smooth flow of the heat medium across the protrusion.

[0039] The fourteenth embodiment is based on the heat exchanger for cooling described in the thirteenth embodiment, wherein, in the cross-section along the length of the cooling flow path, the radius of curvature of the top of the protrusion is in the range of 0.05 to 1.5 times the length of the base of the protrusion, and in the cross-section along the length of the cooling flow path, the inclination angle of the upstream inclined portion relative to the bottom surface of the cooling flow path is in the range of 20° to 70°.

[0040] According to the cooling heat exchanger configured to follow this method, the radius of curvature of the protrusion top is 0.05 times or more relative to the length dimension of the protrusion base, so that the protrusion top does not become a substantial corner but a smooth arc-shaped cross-section. Furthermore, the radius of curvature of the protrusion top is 1.5 times or less relative to the length dimension of the protrusion base, thereby preventing excessive lengthening of the protrusion in the flow path length direction, and allowing the inclination angles of the upstream and downstream inclined portions, which are smoothly continuous with the protrusion top, relative to the bottom surface to be set sufficiently large.

[0041] The upstream inclined section has an inclination angle of 20° or more relative to the bottom surface of the cooling flow path, thereby effectively disrupting the flow of the hot medium from the upstream side toward the protrusion, achieving improved cooling performance through stirring. Furthermore, the upstream inclined section has an inclination angle of 70° or less relative to the bottom surface of the cooling flow path, thus preventing the flow of the hot medium from being excessively restricted by the protrusion.

[0042] The fifteenth embodiment is based on the heat exchanger for cooling described in the thirteenth embodiment, wherein, in the cross-section along the length of the cooling flow path, the inclination angle of the upstream inclined portion relative to the bottom surface of the cooling flow path is 25° or less.

[0043] According to the cooling heat exchanger configured to follow this method, the inclination angle of the upstream inclined section relative to the bottom surface of the cooling flow path is set to 25° or less, which can set the pressure loss to be small enough, for example, to allow the use of a lower-performance, lower-cost pump to flow the heat medium.

[0044] The sixteenth embodiment is a heat exchanger for cooling, which has a cooling flow path formed inside for the flow of a heat medium for cooling, and cools a cooling object overlapping with a cooling surface. The wall of the cooling flow path has a protrusion that extends in a direction intersecting the flow path length direction. The protrusion has a pair of inclined portions that extend to both sides in the flow path width direction in the flow path length direction. The pair of inclined portions has a low protrusion with a low height and a high protrusion with a high height.

[0045] A cooling heat exchanger configured to follow this method can achieve the same effect as the cooling heat exchanger described in the first method. Furthermore, for example, if the wall of the cooling flow path is not composed of two plates but of a single component such as a tube, the cooling performance can also be improved by providing protrusions with the above-described structure of low and high protrusions within the internal cooling flow path.

[0046] Utility Model Effect

[0047] According to this invention, the cooling performance of a heat exchanger for cooling can be further improved. Attached Figure Description

[0048] Figure 1 This is an exploded perspective view of a cooling heat exchanger as the first embodiment of the present invention.

[0049] Figure 2 yes Figure 1 The cross-sectional view of the cooling heat exchanger shown is equivalent to Figure 3 The diagram of section II-II.

[0050] Figure 3 yes Figure 2 Sectional view III-III.

[0051] Figure 4 It is Figure 3 The diagram shows an enlarged representation of section IV-IV.

[0052] Figure 5 It is Figure 3 The diagram shows an enlarged representation of the VV cross section.

[0053] Figure 6 This is an exploded perspective view of a cooling heat exchanger as a second embodiment of the present invention.

[0054] Figure 7 yes Figure 6 The cross-sectional view of the cooling heat exchanger shown is equivalent to Figure 8 Diagram of section VII-VII.

[0055] Figure 8 yes Figure 7 Sectional view of VIII-VIII.

[0056] Figure 9 yes Figure 6 The cross-sectional view shown is equivalent to... Figure 10 A diagram of the IX-IX section.

[0057] Figure 10 It is equivalent to Figure 9 An enlarged sectional view of section XX.

[0058] Figure 11 It is equivalent to Figure 9 An enlarged sectional view of section XI-XI.

[0059] Figure 12 This is a cross-sectional view of a cooling heat exchanger as another embodiment of the present invention.

[0060] Figure 13 This is a cross-sectional view showing a cooling heat exchanger as the third embodiment of this utility model, which is equivalent to... Figure 14 A diagram of section XIII-XIII.

[0061] Figure 14 It is equivalent to Figure 13 Enlarged sectional view of section XIV-XIV.

[0062] Figure 15 It is equivalent to Figure 13 An enlarged sectional view of the XV-XV section.

[0063] Figure 16This is a cross-sectional view showing a cooling heat exchanger as the fourth embodiment of this utility model.

[0064] Figure 17 This is an exploded perspective view of a cooling heat exchanger as the fifth embodiment of the present invention.

[0065] Figure 18 This is a top view of the inner fins constituting the cooling heat exchanger according to the sixth embodiment of this utility model.

[0066] Figure 19 yes Figure 18 The cross-sectional view shown is equivalent to a portion of the inner fin. Figure 20 A diagram of the XIX-XIX section.

[0067] Figure 20 It is equivalent to Figure 18 Enlarged sectional view of section XX-XX.

[0068] Figure 21 It is equivalent to Figure 18 Enlarged sectional view of section XXI-XXI.

[0069] Figure 22 This is a top view of the inner fins constituting the cooling heat exchanger according to the seventh embodiment of this utility model.

[0070] Figure 23 It is equivalent to Figure 22 Enlarged sectional view of section XXIII-XXIII.

[0071] Figure 24 It is equivalent to Figure 22 Enlarged sectional view of section XXIV-XXIV.

[0072] Figure 25 This is a cross-sectional view of the inner fins that constitute part of a cooling heat exchanger as another embodiment of the present invention.

[0073] Explanation of reference numerals in the attached figures

[0074] 10: Cooling heat exchanger (first embodiment); 12: Cooling surface; 14: Upper plate; 16: Lower plate; 18: Cooling flow path; 20: Flow path section; 22: Parallel flow path section; 24: Protrusion; 24a: First protrusion; 24b: Second protrusion; 26: Inclined section; 28: Low protrusion; 30: High protrusion; 32: Ridge; 40: Cooling heat exchanger (second embodiment); 42: Upper plate; 44: Lower plate; 46: Inner fins; 48: Cooling flow path; 48a: Surface fins Cooling flow path; 48b: Cooling flow path on the back side; 50: Surface protrusion (protrusion); 50a: First surface protrusion (first protrusion); 50b: Second surface protrusion (second protrusion); 52: Back protrusion (protrusion); 52a: First back protrusion (first protrusion); 52b: Second back protrusion (second protrusion); 54: Surface protrusion (protrusion in another embodiment); 56: Back protrusion (protrusion); 60: Heat exchanger for cooling (third embodiment); 62: Protrusion; 62a: First protrusion; 62b: Second protrusion 70: Cooling heat exchanger (fourth embodiment); 72: Protrusion; 72a: First protrusion; 72b: Second protrusion; 80: Cooling heat exchanger (fifth embodiment); 82: Support portion; 84: Protrusion; 90: Inner fin (sixth embodiment); 92: Inclined plate portion; 94: Top; 102: Protrusion; 102a: First protrusion; 102b: Second protrusion; 104: Top of protrusion; 106: Base of protrusion; 108: Upstream inclined portion; 110: Downstream inclined portion; 112: Low protrusion; 1 14: High protrusion; 116: Low central protrusion; 118: High central protrusion; 120: Inner fin (seventh embodiment); 122: Protrusion; 122a: First protrusion; 122b: Second protrusion; 124: Convexity; 140: Protrusion (another embodiment); 142: Top of protrusion; 144: Upstream inclined portion; 146: Downstream inclined portion; 148: Base of protrusion; R: Radius of curvature of the top of protrusion; L: Length dimension of the base of protrusion; α: Inclination angle of the upstream inclined portion; β: Inclination angle of the downstream inclined portion. Detailed Implementation

[0075] The embodiments of this utility model will now be described with reference to the accompanying drawings.

[0076] exist Figures 1-5 In the image, a cooling heat exchanger 10 is shown as the first embodiment of this utility model. The cooling heat exchanger 10 has a structure formed by overlapping a flat upper plate 14 with a cooling surface 12 and a concave lower plate 16. A cooling flow path 18 for the flow of a cooling medium is formed between the upper plate 14 and the lower plate 16. Furthermore, the cooling heat exchanger 10 cools a cooling object, such as a battery (not shown), that overlaps with the cooling surface 12 by heat exchange with the cooling medium via the upper plate 14.

[0077] The flow path length of the cooling flow path 18 is preferably 200 mm or more, more preferably 300 mm or more, and even more preferably 500 mm or more. The cooling flow path 18 has parallel flow path sections 22 composed of multiple parallelly extending flow path sections 20, and a protrusion 24 protrudes from the bottom wall of each flow path section 20. The protrusion 24 is integrally formed with the lower plate 16, protrudes toward the upper plate 14, and extends in the direction intersecting the flow path length direction relative to the flow path length direction of the flow path section 20. The protrusion 24 has a pair of inclined portions 26, 26 extending to both sides in the flow path width direction in the flow path length direction, and when viewed from above and below, forms a V-shape that tapers toward the upstream front end. The inclined portions 26 of the protrusion 24 extend linearly in the flow path intersection direction with a generally triangular cross-sectional shape. Multiple protrusions 24 are provided in the flow path section 20 in a manner arranged along the flow path length direction. In this embodiment, the protrusion 24 is continuously provided throughout the flow path width direction of the flow path portion 20, and both ends are integrally continuous with the side wall portion of the flow path portion 20. Therefore, in this embodiment, there is no gap between the protrusion 24 and the side wall portion of the flow path portion 20 without the protrusion 24.

[0078] The protrusion 24 has a pair of inclined portions 26, 26 with a low protrusion 28 and a high protrusion 30. The protrusion height of the protrusion 24 gradually (continuously) increases from the low protrusion 28 to the high protrusion 30. In addition, the protrusion height of the protrusion 24 refers to the vertical distance from the inner surface of the bottom wall of the flow path portion 20 to the ridge line 32.

[0079] The protrusion 24 includes: a first protrusion 24a, which has a low protrusion 28 at its central portion and high protrusions 30, 30 at both ends in the flow path width direction; and a second protrusion 24b, which has a high protrusion 30 at its central portion and low protrusions 28, 28 at both ends in the flow path width direction. Therefore, the plurality of protrusions 24 arranged along the length direction of the flow path portion 20 includes two types (the first protrusion 24a and the second protrusion 24b) where the low protrusions 28 are positioned differently in the flow path width direction and the high protrusions 30 are positioned differently in the flow path width direction. The plurality of protrusions 24 provided in the flow path portion 20 of this embodiment are configured such that the first protrusion 24a and the second protrusion 24b are alternately arranged in the flow path length direction.

[0080] The cooling heat exchanger 10, which follows the structure of this embodiment as described above, overlaps the cooling surface 12 with a battery pack (not shown) that is the object to be cooled. Furthermore, a low-temperature heat medium is supplied from the upstream side to the cooling flow path 18, and the heat medium flows from the upstream side to the downstream side in the cooling flow path 18, thereby generating heat exchange between the heat medium and the battery pack via the upper plate 14, and the battery pack is cooled by the cooling heat exchanger 10.

[0081] Through heat exchange with the battery pack, the heat medium flowing in the upper part of the cooling flow path 18 near the upper plate 14 is more likely to reach a higher temperature than the heat medium flowing in the lower part of the cooling flow path 18 away from the upper plate 14. Here, protrusions 24 are provided in the cooling flow path 18 to disrupt the flow of the heat medium as it flows over them, thus agitating the heat medium. As a result, the heat medium flowing in the upper part of the cooling flow path 18 mixes with the heat medium flowing in the lower part, thereby reducing the temperature difference in the vertical direction within the cooling flow path 18. Consequently, the temperature difference between the heat medium flowing in the upper part of the cooling flow path 18 and the battery pack can be significantly maintained further downstream of the cooling flow path 18, achieving excellent cooling performance over a larger area of ​​the cooling surface 12.

[0082] In this embodiment, the length of the cooling flow path 18 is preferably 200 mm or more, more preferably 300 mm or more, and even more preferably 500 mm or more. Even with such a long cooling flow path 18, the improved cooling performance due to the stirring effect of the protrusion 24 ensures that the cooling performance extends further downstream.

[0083] The protrusion 24 is a V-shape that narrows towards the upstream when viewed from above, and has a pair of inclined portions 26, 26. The flow of hot medium across the pair of inclined portions 26, 26 tends to form in directions orthogonal to each other relative to the pair of inclined portions 26, 26 (edges 32). Therefore, for example, the hot medium flowing across the pair of inclined portions 26, 26 approaches each other inwards towards the width of the flow path, and these flows of hot medium merge on the downstream side of the protrusion 24. Thus, the flow of hot medium is more strongly disturbed on the downstream side of the protrusion 24, thereby effectively exerting a stirring effect. Furthermore, for example, the formation of a vortex flow by the merging of the flows of hot medium across the pair of inclined portions 26, 26 can also be expected to provide effective stirring of the hot medium.

[0084] The protrusion 24 includes: a first protrusion 24a, which has a low protrusion 28 in the central portion and high protrusions 30, 30 at both ends in the flow path width direction; and a second protrusion 24b, which has a high protrusion 30 in the central portion and low protrusions 28, 28 at both ends in the flow path width direction. Thus, by employing protrusions 24 with varying heights in the flow path width direction, the stirring effect and flow rate of the heat medium caused by the protrusions 24 can be varied in the flow path width direction. Therefore, the cooling performance can be adjusted in the flow path width direction of the cooling flow path 18, for example, providing a cooling heat exchanger 10 with cooling performance corresponding to the temperature distribution of the battery pack.

[0085] In this embodiment, the protrusion height of the protrusion 24 varies continuously along the length of the pair of inclined portions 26, 26. Therefore, while preventing the flow pattern of the heat medium from changing drastically in the flow path width direction and achieving smooth flow of the heat medium, the stirring effect and flow rate brought about by the protrusion 24 gradually change in the flow path width direction, thereby effectively adjusting the cooling performance in the flow path width direction.

[0086] In this embodiment, the first protrusion 24a and the second protrusion 24b are alternately arranged along the length of the cooling flow path 18. Therefore, when the hot medium flows through the low protrusion 28 where the flow resistance is relatively small, for example, by alternately passing through the low protrusion 28 of the first protrusion 24a located at the center in the width direction of the flow path and the low protrusions 28 of the second protrusion 24b located at both ends in the width direction of the flow path, a meandering flow of the hot medium can be formed, and the stirring effect of the hot medium brought about by the meandering flow is expected.

[0087] Furthermore, the first protrusion 24a and the second protrusion 24b are alternately arranged along the length of the cooling flow path 18, so that, for example, the hot medium passing through the low protrusion 28 of the first protrusion 24a flows toward the high protrusion 30 of the second protrusion 24b, which is adjacent to the downstream side of the first protrusion 24a. Thus, the hot medium flowing smoothly through the low protrusion 28 of the first protrusion 24a collides with the high protrusion 30 of the second protrusion 24b, thereby strongly disturbing the flow of the hot medium and effectively providing a stirring effect. Similarly, the hot medium passing through the low protrusions 28, 28 of the second protrusion 24b collides with the high protrusions 30, 30 of the first protrusion 24a, which is adjacent to the downstream side of the second protrusion 24b, thus expecting a stirring effect on the hot medium.

[0088] exist Figures 6-11 In the figure, denoted as a cooling heat exchanger 40 is shown as a second embodiment of the present invention. The cooling heat exchanger 40 has the following structure: inner fins 46 are accommodated between the overlapping surfaces of an upper plate 42 whose upper surface is a cooling surface 12 and a lower plate 44 whose lower surface is also a cooling surface 12. In the following description, components and parts substantially the same as those in the first embodiment are denoted by the same reference numerals in the figures and their descriptions are omitted.

[0089] like Figure 7 , Figure 8 As shown, in the cooling heat exchanger 40, cooling flow paths 48 are formed on both sides of the inner fin 46. That is, a surface cooling flow path 48a is formed between the inner fin 46 and the opposing surface of the upper plate 42, and a back cooling flow path 48b is formed between the inner fin 46 and the opposing surface of the lower plate 44.

[0090] like Figures 9-11As shown, the inner fin 46 has surface protrusions 50 protruding towards the cooling flow path 48a on the front side and back protrusions 52 protruding towards the cooling flow path 48b on the back side. In summary, the protrusions in this embodiment are composed of a plurality of surface protrusions 50 and a plurality of back protrusions 52 protruding from both sides of the inner fin 46.

[0091] The surface protrusion 50 and the back protrusion 52 are respectively generally V-shaped, similar to the protrusion 24 in the first embodiment. For example... Figure 10 , Figure 11 As shown, the surface protrusion 50 is composed of a first surface protrusion 50a, which is a first protrusion with a low protrusion 28 in the central portion of the flow path width direction, and a second surface protrusion 50b, which is a second protrusion with a low protrusion 28 in each of the two end portions of the flow path width direction. Similarly, the back protrusion 52 is composed of a first back protrusion 52a, which is a first protrusion with a low protrusion 28 in the central portion of the flow path width direction, and a second back protrusion 52b, which is a second protrusion with a low protrusion 28 in each of the two end portions of the flow path width direction.

[0092] Furthermore, in this embodiment, the protrusion heights of the two ends of the protrusions 50 and 52 in the flow path width direction decrease sharply towards the outer side in the flow path width direction, failing to reach the wall of the flow path portion 20, and thus the height dimension becomes 0. In other words, the rate of change of the protrusion height at the two ends of the protrusions 50 and 52 is greater than that of the other parts. Moreover, the protrusions 50 and 52 are only provided in the middle portion of the flow path width direction of the flow path portion 20, not reaching the two ends. In addition, the protrusion heights of both ends of the protrusions 50 and 52, whether the first protrusion or the second protrusion, decrease towards the outer side in the flow path width direction.

[0093] It could also be, such as Figure 12 As shown in the diagram, the middle portion of the surface protrusion 54 and the back protrusion 56 has a roughly constant protrusion height dimension in the flow path width direction, with the protrusion height dimension varying only at the two ends. In summary, the two end portions of the surface protrusion 54 and the back protrusion 56, whose height decreases sharply towards the outer side in the flow path width direction, can also be regarded as part of a pair of inclined portions 26, 26.

[0094] In the cooling heat exchanger 40 of this embodiment, a battery pack (not shown) that is to be cooled overlaps with the upper cooling surface 12 and the lower cooling surface 12, respectively. Then, the battery pack is cooled by heat exchange with a heat medium.

[0095] The inner fins 46 that separate the cooling flow paths 48a and 48b have surface protrusions 50 protruding into the cooling flow path 48a and back protrusions 52 protruding into the cooling flow path 48b. Thus, the protrusions 50 and 52 provide a stirring effect on both the hot medium flowing in the cooling flow path 48a and the hot medium flowing in the cooling flow path 48b, thereby improving the cooling performance through the stirring of the hot medium.

[0096] exist Figures 13-15 In the image, a cooling heat exchanger 60 is shown as a third embodiment of the present invention. The cooling heat exchanger 60 includes a protrusion 62 extending from the lower plate 16. In this embodiment, the protrusion 62... Figure 13 When viewed from the indicated protruding direction, it forms an inverted V-shape with two protrusions 24 in the opposite direction to those in the first embodiment, arranged in the flow path width direction; as a whole, it forms a roughly inverted W-shape. Therefore, the protrusion 62 has four inclined portions 26, 26, 26, 26, with a low protrusion 28 and a high protrusion 30 provided at each end of each inclined portion 26. Furthermore, of the four inclined portions 26, 26, 26, 26 constituting the protrusion 62, two inclined portions extend in the same direction, and the other two inclined portions extend in a different direction. The protrusion 62 includes: a first protrusion 62a, which has low protrusions 28 at its central portion and both ends in the flow path width direction; and a second protrusion 62b, which has high protrusions 30 at its central portion and both ends in the flow path width direction.

[0097] The cooling heat exchanger 60 of this embodiment, as described above, also performs the same effect as in the first embodiment.

[0098] Furthermore, for example, if the flow path width of the flow path section 20 is large, and a protrusion composed of a V-shape or an inverted V-shape is provided, then if the width of the protrusion is to be set sufficiently large relative to the flow path width of the flow path section 20, it becomes necessary to increase the length of the protrusion in the flow path length direction or decrease the tilt angle of the inclined portion 26 relative to the flow path width direction. Both of these situations risk adversely affecting the improvement in cooling performance brought about by the protrusion. In this embodiment, a protrusion 62 with two inverted V-shapes arranged along the flow path width direction is used. Therefore, even if the flow path width of the flow path section 20 is large, it is possible to prevent the length of the protrusion 62 in the flow path length direction from becoming excessively large, and the tilt angle of the inclined portion 26 relative to the flow path width direction can be set with a large degree of freedom.

[0099] exist Figure 16In the image, a cooling heat exchanger 70 is shown as the fourth embodiment of this utility model. The protrusion 72 of the cooling heat exchanger 70 includes a pair of inclined portions 26, 26 disposed at positions offset from each other in the length direction of the flow path, and is composed of a pair of mutually separated inclined portions 26, 26. The protrusion 72 includes, within the pair of inclined portions 26, 26: a first protrusion 72a, which has a low protrusion 28 at its central portion in the width direction of the flow path; and a second protrusion 72b, which has a high protrusion 30 at its central portion in the width direction of the flow path.

[0100] Furthermore, in this embodiment, among the pair of inclined portions 26, 26 constituting the protrusion 72, the ends of the central sides of the flow path width that are close to each other are located at a position where there is no gap when viewed in the flow path length direction or at a position where they overlap. Additionally, in this embodiment, the ends of the pair of inclined portions 26, 26 that are close to each other in the flow path width center side are either both low protrusions or both high protrusions, with approximately the same protrusion height. Furthermore, in this embodiment, the separation distance between the ends of the pair of inclined portions 26, 26 that are close to each other in the flow path width center side in the flow path length direction is less than or equal to the dimension of each inclined portion 26 in the flow path length direction.

[0101] exist Figure 17 The image shows a cooling heat exchanger 80 according to the fifth embodiment of this utility model. The cooling heat exchanger 80 has a support portion 82 protruding from a lower plate 16 toward an upper plate 14, in which the lower plate 16 and the upper plate 14 are fixedly mounted. A protrusion 84 is formed adjacent to the downstream side of the support portion 82. The protrusion 84 is positioned laterally offset from the support portion 82 in the flow path width direction, for example, on both sides of the downstream side of the support portion 82. The protrusion 84 is V-shaped, expanding laterally toward the downstream side in the flow path width direction, and similarly to the protrusion 24 of the first embodiment, it has a low protrusion 28 and a high protrusion 30.

[0102] According to the cooling heat exchanger 80 which has a structure that follows the above-described embodiment, for example, by using the support portion 82 of the lower plate 16 as a fixed mounting portion with the upper plate 14, the fixed mounting strength between the upper plate 14 and the lower plate 16 is improved.

[0103] Furthermore, the support column 82 is provided in the flow path 20, so that the hot medium flowing in the flow path 20 is separated and flows to both sides in the flow path width direction relative to the support column 82. Therefore, by providing a protrusion 84 on the side downstream of the support column 82 on the flow path of the hot medium separated by the support column 82, the flow of the hot medium can be guided towards the protrusion 84, and the stirring effect brought by the protrusion 84 can be obtained efficiently.

[0104] exist Figure 18 In the diagram, the inner fins 90 constitute the cooling heat exchanger according to the sixth embodiment of this utility model. Furthermore, since the inner fins 90 of this embodiment can be replaced with the inner fins 46 in the second embodiment, there are instances where reference numerals from the second embodiment are used to describe components and parts substantially the same as those in the second embodiment. Additionally, Figure 18 The left side of the middle becomes the upstream of the cooling flow path. Figure 18 The right side of the flow path becomes the downstream of the cooling flow path.

[0105] The inner fin 90 is formed from metal, synthetic resin, or the like, and is a thin-walled plate. In this embodiment, the inner fin 90 is a stamped metal part. The inner fin 90 has a serrated, wavy cross-section. In this embodiment, multiple flat, inclined plate portions 92 that extend obliquely in the up-down and front-back directions have a serrated cross-section that is integrally continuous along the front-back direction at the folded-back tops 94. The inner fin 90 extends linearly in the left-right direction with a substantially constant cross-sectional shape. Furthermore, there is no particular limitation on the number of folds (number of tops 94) of the serrated, wavy inner fin 90; for example, it can be appropriately set based on the width of the mold cooling surface 12 and the cross-sectional area of ​​the flow path portions 20 divided by the inner fin 90.

[0106] The inner fin 90, like the inner fin 46 in the second embodiment, is disposed between the upper plate 14 and the lower plate 16. In the inner fin 90, for example, the top 94 is brazed to the upper plate 14 and the lower plate 16, thus positioning it on the upper plate 14 and the lower plate 16. The cooling flow path 18 between the upper plate 14 and the lower plate 16 is divided by the inner fin 90 into multiple flow path sections 20 arranged along the width direction of the flow path. Multiple flow path sections 20 are formed on both the upper and lower sides of the inner fin 90, and the cooling surfaces 12 of the upper plate 14 and the lower plate 16 are cooled by the hot medium flowing through the upper and lower flow path sections 20. In this embodiment, the flow path section 20 is formed by a wall portion, two continuous inclined plate sections 92, 92 via a top 94, and the upper plate 14 or the lower plate 16, forming a generally triangular cross-section.

[0107] A protrusion 102 is formed in the inner fin 90. The protrusion 102 extends in a generally V-shape on the surface of the inner fin 90, tapering (narrowing in width) towards the upstream side of the cooling flow path. The protrusion 102 is generally V-shaped when viewed vertically. The protrusion 102 is composed of a first protrusion 102a protruding towards the upper surface of the inner fin 90 and a second protrusion 102b protruding towards the lower surface of the inner fin 90.

[0108] exist Figure 19 In the diagram, a magnified cross-section along the length of a protrusion 102 is shown. The protrusion 102 is... Figure 19The cross-section shown is a tapered shape that narrows in width along the length of the flow path towards the protruding tip. More specifically, the protrusion 102 in... Figure 19 The cross-section shown has a continuous cross-sectional shape comprising a curved, arc-shaped protrusion top 104, an upstream inclined portion 108 extending obliquely upstream from the upstream end of the protrusion top 104 toward the protrusion base 106 (the end of the protrusion 102 that connects to the inclined plate portion 92), and a downstream inclined portion 110 extending obliquely downstream from the downstream end of the protrusion top 104 toward the protrusion base 106. Furthermore, Figure 19 The cross-section of the protrusion 102 shown is the cross-section along the length of the flow path, passing through the center of the flow path width direction. However, any cross-section in the protrusion 102 that is orthogonal to the edge 32 becomes... Figure 19 For any cross-section orthogonal to edge 32, the same cross-sectional shape is preferably applicable to... Figure 19 The same numerical range is explained.

[0109] exist Figure 19 In the cross-section along the flow path length shown, the radius of curvature R of the protruding top 104, including the ridge line 32, is preferably 0.05 to 1.5 times the length L of the protruding base 106 in the flow path length direction, more preferably 0.2 to 1.45 times. By making the radius of curvature R of the protruding top 104 more than 0.05 times the length L of the protruding base 106, the protruding top 104 will not become a substantial corner but a smooth arc-shaped cross-section. Furthermore, by making the radius of curvature R of the protruding top 104 less than 1.5 times the length L of the protruding base 106, it is possible to prevent the length of the protrusion 102 from becoming excessively long in the flow path length direction and to set the inclination angles α and β of the upstream inclined portion 108 and the downstream inclined portion 110, which are smoothly continuous with the protruding top 104, to be sufficiently large. Furthermore, in this embodiment, the radius of curvature R of the protrusion top 104 is in the range of 0.05 to 0.5 times the length dimension L of the protrusion base 106.

[0110] The upstream inclined portion 108 may be curved, but in this embodiment it is straight. The upper end of the upstream inclined portion 108 extends tangentially from the upstream end of the protrusion top 104 and is smoothly continuous relative to the protrusion top 104 without any corners. The lower end of the upstream inclined portion 108 may also be curved into an arc shape, in which case it is desirable to be smooth and continuous relative to the inclined plate portion 92 that forms the bottom surface of the cooling flow path 18 without any corners.

[0111] The inclination angle α of the upstream inclined portion 108 relative to the inclined plate portion 92 constituting the bottom surface of the cooling flow path 18 is in the range of 20° to 70°, more preferably in the range of 30° to 60°. Furthermore, when the upstream inclined portion 108 is curved, the inclination angle α of the upstream inclined portion 108 relative to the inclined plate portion 92 can be grasped, for example, as the average value of the inclination angle of the upstream inclined portion 108 relative to the inclined plate portion 92.

[0112] By setting the inclination angle α of the upstream inclined portion 108 to 20° or more, the flow of the hot medium from the upstream side toward the protrusion 102 is effectively disturbed by the upstream inclined portion 108, which forms a sufficiently large angle relative to the flow direction of the hot medium, thereby improving the cooling performance through stirring. Furthermore, by setting the inclination angle α of the upstream inclined portion 108 to 70° or less, it is possible to prevent the flow of the hot medium from being excessively restricted by the protrusion 102.

[0113] The downstream inclined portion 110 may also be curved, but in this embodiment it is straight. The upper end of the downstream inclined portion 110 extends tangentially from the downstream end of the protruding top 104, and is smoothly continuous with respect to the protruding top 104 without any corners. The lower end of the downstream inclined portion 110 may also be curved into an arc shape, in which case it is desirable to be smooth and continuous with respect to the inclined plate portion 92 that forms the bottom surface of the cooling flow path 18 without any corners.

[0114] The inclination angle β of the downstream inclined portion 110 relative to the inclined plate portion 92 constituting the bottom surface of the cooling flow path 18 is in the range of 20° to 70°, more preferably in the range of 30° to 60°. Furthermore, when the downstream inclined portion 110 is curved, the inclination angle β of the downstream inclined portion 110 relative to the inclined plate portion 92 can be, for example, grasped as the average value of the inclination angle of the downstream inclined portion 110 relative to the inclined plate portion 92.

[0115] By setting the inclination angle β of the downstream inclined portion 110 to 20° or more, the flow of the hot medium across the protrusion 102 is easily separated from the downstream inclined portion 110, thereby enabling the formation of turbulent flows such as eddies on the downstream side of the protrusion 102. Furthermore, by setting the inclination angle β of the downstream inclined portion 110 to 70° or less, effective stirring of the hot medium along the downstream inclined portion 110 is expected due to the merging of the flow separated from the downstream inclined portion 110.

[0116] However, as Figure 20 , Figure 21As shown, in the protrusion 102 of this embodiment, the protrusion height varies in the front-rear direction, which is the width of the flow path. Furthermore, the plurality of protrusions 102 are composed of a central low protrusion 116 with a low protrusion 112 at the front and rear center and a high protrusion 114 at both the front and rear ends, and a central high protrusion 118 with a high protrusion 114 at the front and rear center and a low protrusion 112 at both the front and rear ends. The first protrusion 102a and the second protrusion 102b are both configured to include a plurality of central low protrusions 116 and a plurality of central high protrusions 118.

[0117] like Figure 18 As shown, in each of the plurality of first protrusions 102a and second protrusions 102b arranged along the length of the flow path, the central low protrusion 116 and the central high protrusion 118 are arranged alternately in the left-right direction that is the length of the flow path. Therefore, in the central portion of the flow path section 20 in the flow path width direction, the low protrusion 112 of the central low protrusion 116 and the high protrusion 114 of the central high protrusion 118 are arranged alternately in the flow path length direction. In addition, in the two ends of the flow path section 20 in the flow path width direction, the high protrusions 114, 114 of the central low protrusion 116 and the low protrusions 112, 112 of the central high protrusion 118 are arranged alternately in the flow path length direction.

[0118] According to the inner fin 90 of this embodiment as described above, the stirring effect of the hot medium can be more strongly obtained in the high protrusion 114 with a large protrusion height dimension, and the pressure loss is reduced by suppressing the flow resistance of the hot medium through the low protrusion 112 with a small protrusion height dimension.

[0119] In this embodiment, the low protrusion 112 and the high protrusion 114 are arranged adjacent to each other in the flow path length direction. The hot medium that flows smoothly in the low protrusion 112 is efficiently stirred at the high protrusion 114, which is located downstream of the low protrusion 112, thereby effectively improving the cooling performance. In addition, the hot medium whose flow is strongly disturbed by the high protrusion 114 flows more smoothly at the low protrusion 112, which is located downstream of the high protrusion 114, so it is difficult for flow stagnation to occur.

[0120] Furthermore, the hot medium tends to flow more easily in the low protrusion 112, where the flow resistance is smaller than that of the high protrusion 114. However, the central low protrusion 116 and the central high protrusion 118 are alternately arranged in the length direction of the flow path, and the low protrusion 112 is alternately located in the central and end portions in the width direction of the flow path in the length direction of the flow path. Therefore, in the flow path section 20, the hot medium also flows along the width direction of the flow path in a manner that connects the low protrusions 112, which can also be expected to eliminate the imbalance of the temperature distribution of the hot medium in the width direction of the flow path.

[0121] exist Figures 22-24 In the diagram, the inner fin 120 is shown as constituting the cooling heat exchanger according to the seventh embodiment of this utility model. The inner fin 120 has the same serrated cross-sectional shape as the inner fin 90 of the sixth embodiment.

[0122] A protrusion 122 is provided on the inner fin 120. The protrusion 122 is composed of multiple first protrusions 122a protruding upwards and multiple second protrusions 122b protruding downwards. Similar to the protrusion 102 of the inner fin 90, the protrusion 122, as a whole, forms a V-shape when viewed vertically, especially on the upstream side (…). Figure 22 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 to both sides. Figure 22 It consists of two separate protrusions 124 and 124 that extend and tilt to the right side of the middle.

[0123] The protrusion 122 in this embodiment, like the protrusion 102 in the sixth embodiment, includes a central low protrusion 116 and a central high protrusion 118. Furthermore, in this embodiment, the plurality of central low protrusions 116 and the plurality of central high protrusions 118 are arranged alternately in the flow path length direction. Moreover, since the protrusion 122 in this embodiment is composed of two protrusions 124, 124 that are separated from each other in the central portion in the flow path width direction, 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.

[0124] The inner fin 120, which follows the structure of this embodiment as described above, can achieve the same effect as the inner fin 90 of the sixth embodiment. Furthermore, since the protrusion 122 is only provided on the inclined plate portion 92 and not formed on the top 94, the forming process of the protrusion 122 can be simplified.

[0125] The embodiments of this utility model have been described in detail above, but this utility model is not limited to this specific description. For example, the height of the protrusion preferably changes gradually from the low protrusion to the high protrusion, but it can also be a step-like or stepped change in height.

[0126] When multiple protrusions are provided, these protrusions can also be different from each other in terms of shape, size, spacing (configuration density), etc.

[0127] The protrusion can be, for example, an inverted V-shape extending to both sides in the flow path width direction towards the upstream side. Alternatively, the protrusion can also be a W-shape, such as two V-shapes extending to both sides in the flow path width direction towards the downstream side. Or, the protrusion only needs to have at least one V-shaped or inverted V-shaped portion locally in the flow path width direction; for example, three or more V-shaped portions can be arranged.

[0128] exist Figure 19 The text indicates a protrusion 102 with an inclination angle of 20° to 70° for the upstream inclined portion 108. However, for example, other types of protrusions could also be used. Figure 25 The protrusion 140 is shown. That is, Figure 25 In the protrusion 140, the radius of curvature of the protrusion top 142 is large, and both the upstream inclined portion 144 (as the upstream side) and the downstream inclined portion 146 (as the downstream side) are composed of curved surfaces. The protrusion top 142 and the inclined plate portion 92 are connected and arranged smoothly and continuously 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 a continuous curved shape. Furthermore, Figure 25 In the protrusion 140, the radius of curvature R of the protrusion top 142, which is arc-shaped in the cross-section along the flow path length direction, 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 25 In the cross-section along the length of the flow path shown, the inclination angle α of the upstream inclined portion 144 relative to the bottom surface of the flow path portion 20 in this embodiment is 25° or less, and the inclination angle β of the downstream inclined portion 146 in this embodiment is 25° or less. In summary, the protrusion 140 and... Figure 19 Compared to the protrusion 102 shown, the protrusion 140 has a flat shape in the cross-section along the length of the flow path, with a smaller proportion of its height to the length L of its base 148. This results in a smaller rate of change in the cross-sectional area of ​​the flow path caused by the protrusion 140. Because the protrusion 140 is designed as described above, pressure loss caused by the flow of the hot medium across the protrusion 140 is suppressed, allowing for the circulation of the hot medium using a lower-performance, lower-cost pump.

[0129] The protrusions do not necessarily need to be continuously arranged throughout the entire flow path width direction of the flow path section. It is desirable that the width of the protrusions in the flow path width direction is 50% or more, more preferably 70% or more, relative to the flow path width of the flow path section. This restricts the meandering flow at the protrusions, making it easier for flow to cross the protrusions, thus efficiently utilizing the disruptive effect of the protrusions on the flow of the heat medium. Furthermore, when serrated inner fins are used, and the flow path width of the flow path section varies in the flow path depth direction, it is desirable that the width of the protrusions be 50% or more, more preferably 70% or more, relative to the maximum width of the flow path section (the width between the tops in serrated inner fins). Additionally, when the flow path width of the flow path section varies in the flow path length direction, it is desirable that the width of the protrusions be set within the above-mentioned range relative to the flow path width at the location where the protrusions are provided.

[0130] The pair of inclined portions constituting the protrusion do not necessarily have to be identical in shape or size. For example, they may have different lengths, or different maximum and / or minimum protrusion heights. In addition, the inclination angles of the pair of inclined portions relative to the length direction of the flow path and towards the width direction of the flow path may also be different.

[0131] For example, the low protrusion and the high protrusion can be respectively located in the middle portion of the inclined portion and at both ends of the inclined portion. In short, besides the case where only one low protrusion and one high protrusion are provided in a single inclined portion, there can also be multiple low protrusions and multiple high protrusions in a single inclined portion. Furthermore, it is sufficient that at least one low protrusion and one high protrusion are provided in a single protrusion; for example, a low protrusion can be provided in one inclined portion and a high protrusion can be provided in the other inclined portion.

[0132] Furthermore, the tilt angle (the tilt angle relative to the length direction of the flow path towards the width direction) of a pair of tilted sections is not limited. Also, when the height dimension of the tilted section continuously varies between the low and high protrusions, the rate of change and the amount of height change are not limited. Furthermore, when the height dimension continuously varies between the low and high protrusions, the area of ​​height variation does not need to be the entire tilted section, and the proportion of the variation area relative to the entire tilted section is not limited. Furthermore, the protrusion does not need to be provided throughout the entire width direction of the flow path, and the proportion of the protrusion relative to the entire flow path is not limited in the width direction. Furthermore, the height dimension of the protrusion can be appropriately set, and the proportion of the high and low protrusions of the protrusion relative to the height direction of the flow path is not limited. Furthermore, the orthogonal section to the extension direction of the tilted section is not limited to a triangular cross-section shape. Furthermore, the orthogonal section to the extension direction of the tilted section is not limited to a shape that is approximately similar in shape to the extension direction of the tilted section; it can also be a different shape in the extension direction of the tilted section. Furthermore, the width dimension of the tilted section in the length direction of the flow path does not need to vary with the height and can be constant.

[0133] For example, when two types of protrusions, such as the first protrusion 24a and the second protrusion 24b in the first embodiment, are provided, these two types of protrusions can be arranged two or three times apart in the flow path length direction, or they can be areas where protrusions of the same type are arranged adjacent to each other in the flow path length direction.

[0134] The cooling flow path may not necessarily consist of multiple flow path sections arranged side by side; it may consist of only one flow path section. Furthermore, within a single flow path section, multiple protrusions may be arranged along the width of the flow path. Additionally, the depth, width, and length of the multiple flow path sections constituting the side-by-side flow path section may differ from one another.

[0135] Cooling flow paths are not limited to straight-line cooling flow paths. For example, they can bend back and extend in a U-shape or meandering shape, or they can bend and extend in an L-shape.

[0136] The plate (lower plate 16) on the other side for the protrusion can also be made of metal.

[0137] The heat exchanger for cooling is not necessarily limited to a structure formed by overlapping two plates (upper plate 14 and lower plate 16 in the embodiment described above). For example, it can also be tubular or the entire wall of the cooling flow path is composed of a single component.

Claims

1. A heat exchanger (10, 40, 60, 70, 80) for cooling, wherein a cooling flow path (18, 48) for the flow of a heat medium for cooling is formed between two plates (14, 42; 16, 44) having at least one cooling surface (12) overlapping with the object being cooled, wherein, The walls of the cooling flow paths (18, 48) are provided with protrusions (24, 62, 72, 84, 102). The protrusions (24, 62, 72, 84, 102) extend in the direction of intersection with the length of the cooling flow path (18, 48). The protrusions (24, 62, 72, 84, 102) are provided with a pair of inclined portions (26; 26) that extend to both sides in the flow path width direction in the flow path length direction toward the cooling flow path (18, 48). The pair of inclined portions (26; 26) are provided with low protrusions (28, 112) with low height and high protrusions (30, 114) with high height.

2. The cooling heat exchanger (10, 40, 60, 70, 80) according to claim 1, wherein, The protrusions (24, 62, 72, 84, 102) appear V-shaped when viewed from the protruding direction.

3. The cooling heat exchanger (10, 40, 60, 70, 80) according to claim 1 or 2, wherein, The protrusion height of the protrusions (24, 62, 72, 84, 102) gradually increases from the low protrusions (28, 112) to the high protrusions (30, 114).

4. The cooling heat exchanger (10, 40, 60, 70, 80) according to claim 1 or 2, wherein, The protrusions (24, 62, 72, 84, 102) are arranged in multiple ways along the length of the cooling flow path (18, 48). The plurality of protrusions (24, 62, 72, 84, 102) arranged in the length direction of the flow path include multiple types of low protrusions (28, 112) that are located differently in the width direction of the flow path and high protrusions (30, 114) that are located differently in the width direction of the flow path.

5. The cooling heat exchanger (10, 40, 60, 70, 80) according to claim 1 or 2, wherein, Either the low protrusion (28, 112) or the high protrusion (30, 114) is located in the central portion of the protrusion (24, 62, 72, 84, 102) in the flow path width direction, and either the low protrusion (28, 112) or the high protrusion (30, 114) is located at one of the two ends of the protrusion (24, 62, 72, 84, 102) in the flow path width direction.

6. The cooling heat exchanger (10, 40, 60, 70) according to claim 5, wherein, The protrusions (24, 62, 72, 102) are arranged in multiple ways along the length of the cooling flow path (18, 48). The plurality of protrusions (24, 62, 72, 102) are configured such that first protrusions (24a, 62a, 72a, 102a) and second protrusions (24b, 62b, 72b, 102b) are alternately arranged in the flow path length direction. The first protrusions (24a, 62a, 72a, 102a) have the low protrusions (28, 112) in the central portion in the flow path width direction and the high protrusions (30, 114) in both end portions. The second protrusions (24b, 62b, 72b, 102b) have the high protrusions (30, 114) in the central portion in the flow path width direction and the low protrusions (28, 112) in both end portions.

7. The cooling heat exchanger (10, 60, 70, 80) according to claim 1 or 2, wherein, The cooling surface (12) is provided on one of the plates (14), and the protrusions (24, 62, 72, 84) are formed on the other plate (16).

8. The cooling heat exchanger (80) according to claim 1 or 2, wherein, A support portion (82) is provided that protrudes from the other plate (16) and is fixedly installed on the other plate (14), the protrusion (84) being adjacent to the downstream side of the support portion (82) and disposed on the side.

9. The cooling heat exchanger (40) according to claim 1 or 2, wherein, Both plates (42; 44) have the cooling surface (12). An inner fin (46, 90) is disposed between the two plates (42; 44), and the cooling flow path (48) is formed on both sides of the inner fin (46, 90). The inner fins (46, 90) are provided with a surface protrusion (50) protruding into one cooling flow path (48) as the protrusion, and a back protrusion (52) protruding into the other cooling flow path (48) as the protrusion.

10. The cooling heat exchanger (10, 40, 60, 70, 80) according to claim 1 or 2, wherein, The cooling flow path (18, 48) has a parallel flow path section (22) consisting of a plurality of flow path sections (20) extending in parallel. A plurality of protrusions (24, 62, 72, 84, 102) are arranged in the flow path length direction relative to the flow path section (20) constituting the parallel flow path section (22).

11. The cooling heat exchanger (10, 40, 60, 70, 80) according to claim 1 or 2, wherein, The length of the cooling flow path (18, 48) is 200 mm or more.

12. The cooling heat exchanger (10, 60, 70, 80) according to claim 1 or 2, wherein, The protrusions (24, 62, 72, 84) extend throughout the width of the cooling flow path (18) and are continuous with the sidewall portion of the cooling flow path (18) at both ends.

13. The heat exchanger for cooling according to claim 1 or 2, wherein, The protrusion (102) has a cross-sectional shape that tapers towards the front end in the cross-section of the cooling flow path (48) along the length of the flow path. The arc-shaped protrusion top (142), the upstream inclined portion (144) that extends obliquely from the protrusion top (142) toward the protrusion base (148) which is the bottom side of the cooling flow path (48) and the downstream inclined portion (146) that extends obliquely from the protrusion top (142) toward the protrusion base (148) and the downstream inclined portion (146) that extends obliquely from the protrusion top (142) toward the protrusion base (148) and the protrusion is provided without corners and is smoothly continuous.

14. The heat exchanger for cooling according to claim 13, wherein, In the cross-section along the length of the cooling flow path (48), the radius of curvature of the protrusion top (142) is in the range of 0.05 to 1.5 times the length of the protrusion base (148). Furthermore, in the cross-section along the length of the cooling flow path (48), the inclination angle of the upstream inclined portion (144) relative to the bottom surface of the cooling flow path (48) is in the range of 20° to 70°.

15. The heat exchanger for cooling according to claim 13, wherein, In the cross section along the length of the cooling flow path (48), the inclination angle of the upstream inclined portion (144) relative to the bottom surface of the cooling flow path (48) is 25° or less.

16. A heat exchanger for cooling, wherein a cooling flow path (48) for the flow of a heat medium for cooling is formed internally, for cooling an object overlapping with a cooling surface, wherein, The wall of the cooling flow path (48) is provided with protrusions (122, 140). The protrusions (122, 140) extend in a direction intersecting the length direction of the cooling flow path (48). The protrusion (122, 140) is provided with a pair of inclined portions that extend to both sides in the flow path width direction in the flow path length direction toward the cooling flow path (48). The pair of inclined portions are provided with a low protrusion (112) with a low height and a high protrusion (114) with a high height.

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