Heat exchanger

Abstract

A heat exchanger (100) is provided with: a plurality of first plates (11); a second plate (12) disposed between an adjacent pair of first plates (11) with a space therebetween, alternately forming a first flow path (13) and a second flow path (14); and a heat exchange promoting member (15) provided in the first flow path (13), at least one of the first plates (11) and the second plate (12) having a plurality of protruding portions (50) formed in a V shape in plan view, recessed in the first flow path (13) and protruding in the second flow path (14), having a height lower than a flow path height of the second flow path (14), the protruding portions (50) being arranged with a leading end portion (51) and an opening portion (52) of the V shape aligned in a flow direction of a second fluid in the second flow path (14), and one of a pair of free end portions (53, 54) of the V shape positioned on a first flow inlet (11d) side through which the first fluid flows into the first flow path (13), and the other positioned on a first flow outlet (11e) side through which the first fluid flows out from the first flow path (13).

Description

Technical Field

[0001] This invention relates to heat exchangers. Background Technology

[0002] JP2016-090123A discloses a heat exchanger in which a first plate and a second plate are alternately stacked with a gap, alternately forming a cooling water flow path and an ATF (Automatic Transmission Fluid) flow path, and heat exchange occurs between the cooling water and the ATF through the first plate or the second plate. In this heat exchanger, the first plate is provided with multiple ribs protruding toward the second plate and along the flow direction of the cooling water, with the front end faces of the ribs abutting against the second plate, thereby blocking a portion of the cooling water flow path between the first and second plates. Furthermore, in this heat exchanger, internal fins are provided in the ATF flow path to increase the heat conduction area of ​​the first and second plates. Summary of the Invention

[0003] However, in the heat exchanger of JP2016-090123A, the cooling water flow path is separated by fins, allowing the cooling water to flow to all corners. However, this results in a stagnant water area downstream of the fins, increasing the flow resistance of the cooling water and reducing heat exchange performance. Furthermore, while internal fins are installed in the ATF flow path, they do not contact the first plate at the locations where the fins are installed, thus also contributing to reduced heat exchange performance.

[0004] The purpose of this invention is to improve the heat exchange performance of both the first fluid flow path and the second fluid flow path in a heat exchanger in which the first and second fluid flow paths are alternately formed by stacking the first and second plates with a gap.

[0005] According to one aspect of the present invention, a heat exchanger for heat exchange between a first fluid and a second fluid flowing in a direction intersecting with the first fluid comprises: a plurality of first plates arranged in parallel with a gap; a second plate arranged with a gap between an adjacent pair of first plates and alternately stacked with the first plates to alternately form a first flow path for the first fluid to flow and a second flow path for the second fluid to flow; and a heat exchange promoting member disposed in the first flow path and abutting against the first plate and the second plate, at least one of the first plate and the second plate having a plurality of protrusions formed in a V-shape in plan view such that it is recessed in the first flow path and protrudes in the second flow path, and its height is lower than the flow path height of the second flow path, the protrusions being configured such that the front end and opening of the V-shape are aligned toward the flow direction of the second fluid in the second flow path, and one of the pair of free ends of the V-shape is located at the first inlet side of the first fluid flowing toward the first flow path, and the other is located at the first outlet side of the first fluid from the first flow path.

[0006] In the above configuration, at least one of the first plate and the second plate has a plurality of protrusions. These protrusions are formed in a V-shape (viewed from above) such that they are recessed within the first flow path and protrude within the second flow path, and their height is lower than the flow path height of the second flow path. The protrusions are configured such that the front end and opening of the V-shape are aligned with the flow direction of the second fluid in the second flow path, and one of the pair of free ends of the V-shape is located at the first inlet side of the first fluid flowing into the first flow path, and the other is located at the first outlet side of the first fluid from the first flow path. Therefore, the first fluid is agitated by flowing inside the protrusions, thus improving the heat exchange performance of the first fluid. Furthermore, longitudinal vortices are generated in the flow of the second fluid under the action of the V-shaped protrusions, thus improving the heat exchange performance of the second fluid. Therefore, the heat exchange performance in both the flow paths of the first and second fluids can be improved simultaneously. Attached Figure Description

[0007] Figure 1 This is a perspective view of the heat exchanger of an embodiment of the present invention viewed from an oblique angle.

[0008] Figure 2 This is a three-dimensional view of the heat exchanger as seen from a slightly downward angle.

[0009] Figure 3 This is a longitudinal sectional view of the heat exchanger.

[0010] Figure 4 This is a top view of the first plate.

[0011] Figure 5 This is a top view of the second panel.

[0012] Figure 6 This is a top view showing the state of the first and second plates overlapping.

[0013] Figure 7A This is a longitudinal sectional view of the circular protrusion.

[0014] Figure 7B This is a longitudinal sectional view of the V-shaped protrusion.

[0015] Figure 8 This is a top view used to illustrate the relationship between the V-shaped protrusion and the heat exchange promoting component.

[0016] Figure 9 This is a longitudinal sectional view used to illustrate the relationship between the V-shaped protrusion and the first flow path.

[0017] Figure 10 This is a top view of the first plate of a first modified example of a heat exchanger according to an embodiment of the present invention.

[0018] Figure 11 This is a top view of the second panel.

[0019] Figure 12 This is a top view showing the state of the first and second plates overlapping.

[0020] Figure 13 This is a top view of the first plate of a second modified example of a heat exchanger according to an embodiment of the present invention.

[0021] Figure 14 This is a top view of the second panel.

[0022] Figure 15A This is a longitudinal sectional view of the circular protrusion.

[0023] Figure 15B This is a longitudinal sectional view of the V-shaped protrusion.

[0024] Figure 16 This is a top view of the first plate of a third variation of the heat exchanger according to an embodiment of the present invention.

[0025] Figure 17 This is a top view of the second panel.

[0026] Figure 18 This is a top view showing the arrangement of V-shaped protrusions in the first and second plates of a fourth modified example of a heat exchanger used to illustrate embodiments of the present invention.

[0027] Figure 19A This is a top view used to illustrate a variation of the V-shaped protrusion.

[0028] Figure 19B This is a top view used to illustrate other variations of the V-shaped protrusion.

[0029] Figure 19C This is a top view used to illustrate other variations of the V-shaped protrusion.

[0030] Figure 19D This is a top view used to illustrate other variations of the V-shaped protrusion. Detailed Implementation

[0031] Hereinafter, the heat exchanger 100 according to an embodiment of the present invention will be described with reference to the accompanying drawings.

[0032] First, refer to Figure 1 and Figure 2 The overall structure of the heat exchanger 100 will be described. Figure 1 This is a perspective view of the heat exchanger 100 according to an embodiment of the present invention, viewed from an oblique angle. Figure 2 This is a three-dimensional view of the heat exchanger 100 viewed from a slightly lower angle.

[0033] The heat exchanger 100 is installed in, for example, a vehicle, and uses the heat from the engine's (not shown) cooling water to warm up and cool the ATF (Automatic Transmission Fluid).

[0034] The heat exchanger 100 has a core 10, a cover part 20 and a bottom plate 30.

[0035] like Figure 1 As shown, the core 10 has a first plate 11, a second plate 12, and an inner fin 15 as a heat exchange promoting component (see reference). Figure 3 The core 10 exchanges heat between ATF, which is a first fluid, and cooling water, which flows in a direction intersecting the ATF, which is a second fluid. The structure of the core 10 will be referred to later. Figure 3 Let me explain in detail.

[0036] The cover member 20 is mounted on the upper surface of the core 10. The cover member 20 secures the core 10 from the upper surface. The cover member 20 is connected to a cooling water inlet 21 for allowing cooling water to flow into the core 10 and a cooling water outlet 22 for allowing cooling water to flow out of the core 10. In addition, the cover member 20 has an ATF return passage 23 that protrudes upward to guide ATF into the core 10.

[0037] A bottom plate 30 is mounted on the lower surface of the core 10. The bottom plate 30 serves as a base for assembling the core 10. Figure 2 As shown, flanges 33 with through holes at the four corners are formed on the bottom plate 30 for fixing. The bottom plate 30 has an ATF inlet 31 for ATF to flow into the core 10 and an ATF outlet 32 ​​for ATF to flow out of the core 10.

[0038] Next, refer to Figures 1 to 3 This explains the structure of the core 10. Figure 3 This is a longitudinal sectional view of the heat exchanger 100.

[0039] like Figure 3 As shown, multiple first plates 11 are arranged in parallel with gaps between them. Second plates 12 are arranged with gaps between adjacent pairs of first plates 11. Multiple first plates 11 and second plates 12 are alternately stacked with gaps between them to form the core 10.

[0040] The first plate 11 and the second plate 12 are flat metal plates that are easy to conduct heat, and their outer perimeters are formed into the same rectangle. To guide cooling water and ATF, the corners of the first plate 11 and the second plate 12 are slightly rounded (see reference). Figure 1 ).

[0041] Between adjacent first plates 11 and second plates 12, there are alternating ATF flow paths 13, which are multiple first flow paths for ATF flow, and cooling water flow paths 14, which are multiple second flow paths for cooling water flow.

[0042] The ATF flowing into the bottom plate 30 through the ATF inlet 31 and changing direction in the ATF reversal passage 23 is split and flows into various paths within the multiple ATF flow paths 13. The ATF that has passed through the multiple ATF flow paths 13 merges and flows out of the heat exchanger 100 from the ATF outlet 32. For example... Figure 3 As shown, each of the multiple ATF flow paths 13 is provided with an inner fin 15.

[0043] Cooling water flowing in from the cooling water inlet 21 connected to the cover component 20 is divided into various flow paths in the multiple cooling water flow paths 14. The cooling water that has passed through the multiple cooling water flow paths 14 merges and flows out of the cooling water outlet 22 to the outside of the heat exchanger 100.

[0044] Inner fins 15 are disposed within the ATF flow path 13, abutting against the first plate 11 and the second plate 12. The inner fins 15 are designed to increase the heat conduction area of ​​the first plate 11 and the second plate 12, thereby facilitating heat exchange of the ATF flowing through the ATF flow path 13. The ATF flowing through each ATF flow path 13 exchanges heat with the cooling water flowing through the adjacent cooling water flow path 14 via the first plate 11 and the second plate 12.

[0045] Multiple first plates 11 and second plates 12 have cooling water inlet side flow holes 11a, cooling water outlet side flow holes 11b, and ATF supply holes 11c formed at the same positions. By stacking the first plates 11 and the second plates 12, the cooling water inlet side flow holes 11a, cooling water outlet side flow holes 11b, and ATF supply holes 11c are arranged in a manner that penetrates through the first plates 11 and the second plates 12 along the stacking direction.

[0046] Similarly, although not shown, multiple first plates 11 and second plates 12 have ATF inlet-side flow holes 11d and ATF outlet-side flow holes 11e formed at the same positions. By stacking the first plates 11 and the second plates 12, the ATF inlet-side flow holes 11d and the ATF outlet-side flow holes 11e are arranged in such a way that they penetrate the first plates 11 and the second plates 12 along the stacking direction.

[0047] The cooling water inlet-side flow hole 11a is a hole for introducing cooling water into the cooling water flow path 14 of the core 10. The cooling water inlet-side flow hole 11a is connected to the cooling water inlet 21 connected to the cover member 20 so that the cooling water flowing from the cooling water inlet 21 flows into the cooling water flow path 14. The cooling water flowing into the cooling water flow path 14 flows in a manner that diffuses throughout the entire cooling water flow path 14.

[0048] The cooling water outlet side flow hole 11b is a hole for discharging cooling water from the cooling water flow path 14. The cooling water outlet side flow hole 11b is connected to the cooling water outlet 22 connected to the cover component 20 so that the cooling water flowing from the cooling water flow path 14 flows out from the cooling water outlet 22.

[0049] ATF supply hole 11c is a hole for supplying ATF into the ATF flow path 13 of the core 10 to circulate the ATF. By providing ATF supply hole 11c, the gap between ATF inlet 31 and ATF outlet 32 ​​can be reduced. In other words, even if the gap between ATF inlet 31 and ATF outlet 32 ​​is small, the heat exchanger 100 can be enlarged.

[0050] Furthermore, the ATF flow path 13 and the cooling water flow path 14 form independent flow path systems, and the cooling water and ATF will not mix. In addition, the cooling water will not leak into the ATF flow path 13 from the cooling water inlet side flow hole 11a and the cooling water outlet side flow hole 11b, and the ATF will not leak into the cooling water flow path 14 from the ATF inlet side flow hole 11d and the ATF outlet side flow hole 11e.

[0051] Next, refer to Figures 4 to 9 This indicates the first board 11 and the second board 12. Figure 4 This is a top view of the first plate 11. Figure 5 This is a top view of the second plate 12. Figure 6 This is a top view showing the state of the first plate 11 and the second plate 12 overlapping. Figure 7A This is a longitudinal sectional view of the circular protrusion 40. Figure 7B This is a longitudinal sectional view of the V-shaped protrusion 50. Figure 8 This is a top view used to illustrate the relationship between the V-shaped protrusion 50 and the inner fin 15. Figure 9This is a longitudinal sectional view used to illustrate the relationship between the V-shaped protrusion 50 and the ATF flow path 13.

[0052] like Figure 4 As shown, the first plate 11 has a cooling water inlet-side flow hole 11a as a second flow inlet, a cooling water outlet-side flow hole 11b as a second flow outlet, an ATF supply hole 11c, an ATF inlet-side flow hole 11d as a first flow inlet, an ATF outlet-side flow hole 11e as a first flow outlet, a circular protrusion 40, and a V-shaped protrusion 50 as a protrusion.

[0053] A cooling water inlet side flow hole 11a is formed near the corner of one corner of the first plate 11.

[0054] A cooling water outlet-side flow hole 11b is formed near a diagonal corner of the first plate 11, positioned opposite the center of the first plate 11. The cooling water outlet-side flow hole 11b has the same shape as the cooling water inlet-side flow hole 11a. The cooling water outlet-side flow hole 11b is configured to be point-symmetrical with respect to the center of the first plate 11 to the cooling water inlet-side flow hole 11a.

[0055] The ATF supply hole 11c is formed at the center of the first plate 11. That is, the central axis of the ATF supply hole 11c is the center of the first plate 11.

[0056] The ATF inlet-side flow hole 11d is formed near a corner that is diagonally different from the corner where the cooling water inlet-side flow hole 11a and the cooling water outlet-side flow hole 11b are located.

[0057] The ATF outlet-side flow hole 11e is formed near a diagonal corner of the first plate 11, positioned opposite the center of the first plate 11. The ATF outlet-side flow hole 11e has the same shape as the ATF inlet-side flow hole 11d. The ATF outlet-side flow hole 11e is configured to be point-symmetrical with respect to the center of the first plate 11 and the ATF inlet-side flow hole 11d.

[0058] Thus, cooling water inlet flow hole 11a, cooling water outlet flow hole 11b, ATF inlet flow hole 11d, and ATF outlet flow hole 11e are provided at the four corners of the first plate 11. As a result, cooling water flowing from cooling water inlet flow hole 11a to cooling water outlet flow hole 11b and ATF flowing from ATF inlet flow hole 11d to ATF outlet flow hole 11e flow in directions that intersect each other within the heat exchanger 100.

[0059] With the first plate 11 and the second plate 12 stacked, the circular protrusion 40 is located at the same position as the circular protrusion 40 on the second plate 12. For example... Figure 7A As shown, the circular protrusion 40 mates with the circular protrusion 40 of the second plate 12 to have the same height as the flow path height of the cooling water flow path 14. Thus, when the first plate 11 and the second plate 12 are stacked, the circular protrusion 40 abuts against the circular protrusion 40 of the second plate 12, forming a columnar shape. When the first plate 11 and the second plate 12 are stacked and assembled, the circular protrusion 40 serves to maintain the flow path height of the cooling water flow path 14.

[0060] like Figure 4 As shown, a plurality of circular protrusions 40 are provided throughout the entire area of ​​the first plate 11. The circular protrusions 40 are particularly disposed around the cooling water inlet-side flow hole 11a, the cooling water outlet-side flow hole 11b, the ATF supply hole 11c, the ATF inlet-side flow hole 11d, and the ATF outlet-side flow hole 11e. Furthermore, the circular protrusions 40 are arranged in such a way that a pair of circular protrusions 40 sandwiches a V-shaped protrusion 50. Thus, when the first plate 11 and the second plate 12 are stacked and assembled, the flow path height of the cooling water flow path 14 at locations requiring dimensional control can be maintained at a specified height. Furthermore, by providing the circular protrusions 40, the inner fins 15 can be tightly attached to the first plate 11 and the second plate 12 during brazing.

[0061] like Figure 7B As shown, the V-shaped protrusion 50 is formed in a V-shape when viewed from above, such that it is recessed within the ATF flow path 13 and protrudes within the cooling water flow path 14. The V-shaped protrusion 50 is formed to be lower than the flow path height of the cooling water flow path 14. That is, the V-shaped protrusion 50 does not abut against the second plate 12, and therefore will not block the cooling water flow path 14. As a result, the increase in flow resistance in the cooling water flow path 14 can be suppressed.

[0062] like Figure 4 As shown, the V-shaped protrusion 50 is configured such that the V-shaped front end 51 and the opening 52 are arranged in the direction of the flow of cooling water in the cooling water flow path 14, and one of the pair of free ends 53 and 54 of the V-shape is located on the ATF inlet side flow hole 11d side, and the other is located on the ATF outlet side flow hole 11e side.

[0063] The cooling water flowing in the cooling water flow path 14 generates a longitudinal vortex when it passes over the V-shaped protrusion 50. Therefore, the cooling water flowing in the cooling water flow path 14 is stirred, thereby improving the heat exchange performance of the cooling water.

[0064] Multiple V-shaped protrusions 50 are arranged in an orthogonal direction to the flow direction of cooling water, and adjacent pairs of V-shaped protrusions 50 are arranged with a V-shaped front end 51 and an opening 52 arranged alternately in the orthogonal direction.

[0065] Therefore, the V-shaped front end 51 and opening 52 are arranged alternately, that is, adjacent V-shaped protrusions 50 are arranged in a staggered manner, thus reducing the interval between adjacent V-shaped protrusions 50.

[0066] Furthermore, the agitation effect of the cooling water is the same whether the front end 51 is located upstream of the cooling water flow direction in the cooling water flow path 14 and the opening 52 is located downstream, or whether the opening 52 is located upstream of the cooling water flow direction and the front end 51 is located downstream. This is because, in both cases, the straight portion from the front end 51 toward the free end 53 and the straight portion from the front end 51 toward the free end 54 are formed at an inclination relative to the cooling water flow direction.

[0067] A straight line connecting the cooling water inlet side flow hole 11a and the cooling water outlet side flow hole 11b ( Figure 6 The V-shaped protrusion 50 on one side of the straight line O) is perpendicular to the center of the first plate 11 and the straight line ( Figure 6 The V-shaped protrusion on the side of the straight line O in the middle is symmetrical at point 50.

[0068] Therefore, the V-shaped protrusions 50 on the sides of the straight line connecting the cooling water inlet side flow hole 11a and the cooling water outlet side flow hole 11b are arranged symmetrically at one point, so that even if rotated 180 degrees, the same configuration remains. Therefore, the assembly of the first plate 11 and the second plate 12 becomes easy.

[0069] like Figure 5 As shown, similarly, the second plate 12 has a cooling water inlet-side flow hole 11a as a second flow inlet, a cooling water outlet-side flow hole 11b as a second flow outlet, an ATF supply hole 11c, an ATF inlet-side flow hole 11d as a first flow inlet, an ATF outlet-side flow hole 11e as a first flow outlet, a circular protrusion 40, and a V-shaped protrusion 50 as a protrusion.

[0070] The cooling water inlet side flow hole 11a, cooling water outlet side flow hole 11b, ATF supply hole 11c, ATF inlet side flow hole 11d, ATF outlet side flow hole 11e, and circular protrusion 40 are the same as the first plate 11, so their description is omitted here.

[0071] Near the cooling water inlet-side flow hole 11a, V-shaped protrusions 50 are radially arranged from the cooling water inlet-side flow hole 11a to diffuse the flow of incoming cooling water throughout the entire area of ​​the cooling water flow path 14. Similarly, near the cooling water outlet-side flow hole 11b, V-shaped protrusions 50 are radially arranged from the cooling water outlet-side flow hole 11b to collect the flow of outgoing cooling water throughout the entire area of ​​the cooling water flow path 14.

[0072] At a position away from the cooling water inlet side flow hole 11a and the cooling water outlet side flow hole 11b, the V-shaped protrusion 50 is configured such that the V-shaped front end 51 and the opening 52 are arranged in the direction of the flow of cooling water in the cooling water flow path 14, and one of the pair of free ends 53 and 54 of the V-shape is located on the ATF inlet side flow hole 11d side and the other is located on the ATF outlet side flow hole 11e side.

[0073] Similarly, in the second plate 12, the straight line connecting the cooling water inlet side flow hole 11a and the cooling water outlet side flow hole 11b ( Figure 6 The V-shaped protrusion 50 on one side of the straight line O) is perpendicular to the center of the second plate 12 and the straight line ( Figure 6 The V-shaped protrusion on the side of the straight line O in the middle is symmetrical at point 50.

[0074] like Figure 6 As shown, in the heat exchanger 100, the V-shaped protrusions 50 of the first plate 11 and the V-shaped protrusions 50 of the second plate 12 are alternately arranged in the flow direction of the cooling water flow path 14.

[0075] like Figure 8 As shown, the inner fin 15 has a heat exchange wall 15a erected between the first plate 11 and the second plate 12, the heat exchange wall 15a being configured to intersect the flow direction of ATF from the ATF inlet side flow hole 11d toward the ATF outlet side flow hole 11e.

[0076] In addition, such as Figure 9 As shown, the V-shaped protrusion 50 is formed as a recess within the ATF flow path 13, so that ATF flows inside the V-shaped protrusion 50 at the location where it is provided. Thus, the ATF is stirred by flowing inside the V-shaped protrusion 50, thereby improving its heat exchange performance. Furthermore, the flow of ATF inside the V-shaped protrusion 50 reduces the flow resistance within the ATF flow path 13.

[0077] As described above, the first plate 11 and the second plate 12 have multiple V-shaped protrusions 50, wherein the V-shaped protrusions 50 are formed in a V-shape when viewed from above, such that they are recessed in the ATF flow path 13 and protrude in the cooling water flow path 14, and their height is lower than the flow path height of the cooling water flow path 14. The V-shaped protrusions 50 are configured such that the front end 51 and the opening 52 of the V-shape are aligned toward the flow direction of the cooling water in the cooling water flow path 14, and one of the pair of free ends 53, 54 of the V-shape is located on the ATF inlet side flow hole 11d side, and the other is located on the ATF outlet side flow hole 11e side. Therefore, the ATF flows inside the V-shaped protrusions 50 and is stirred, thereby improving the heat exchange performance of the ATF. In addition, longitudinal vortices are generated in the flow of cooling water under the action of the V-shaped protrusions 50, thereby improving the heat exchange performance of the cooling water. Therefore, the heat exchange performance of the ATF flow path 13 and the cooling water flow path 14 can be improved simultaneously.

[0078] Furthermore, in this embodiment, the V-shaped protrusion 50 is provided on the first plate 11 and the second plate 12. However, the V-shaped protrusion 50 may also be provided on at least one of the first plate 11 and the second plate 12.

[0079] Next, refer to Figures 10 to 12 A first variation of the heat exchanger 100 according to an embodiment of the present invention will be described. Figure 10 This is a top view of the first plate 11 of a first modified example of the heat exchanger 100. Figure 11 This is a top view of the second plate 12. Figure 12 This is a top view showing the state of the first plate 11 and the second plate 12 overlapping. Furthermore, in the various modifications shown below, the differences from the above embodiments are emphasized, and structures with the same function are labeled with the same reference numerals and their descriptions are omitted.

[0080] The first variation differs from the above embodiment in that it does not have an ATF supply hole 11c. In this case, the ATF inlet 31 is connected to the ATF inlet-side flow hole 11d. The ATF flowing in from the ATF inlet 31 of the bottom plate 30 is diverted and flows into each of the multiple ATF flow paths 13. The ATF that has passed through the multiple ATF flow paths 13 merges and flows out of the heat exchanger 100 from the ATF outlet 32.

[0081] In the first modified example, no ATF supply hole 11c is provided at the center of the first plate 11 and the second plate 12, so a V-shaped protrusion 50 can be provided at this position. As a result, while reducing the dead water zone, the V-shaped protrusion 50 generates a longitudinal vortex in the cooling water and agitates the ATF, thereby improving the heat exchange performance of both the ATF flow path 13 and the cooling water flow path 14.

[0082] Next, refer to Figures 13 to 15B A second variation of the heat exchanger 100 according to an embodiment of the present invention will be described. Figure 13 This is a top view of the first plate 11 of a second variant of the heat exchanger 100. Figure 14 This is a top view of the second plate 12. Figure 15A This is a longitudinal sectional view of the circular protrusion 40. Figure 15B This is a longitudinal sectional view of the V-shaped protrusion 50.

[0083] In the second variation, adjacent V-shaped protrusions 50 are connected to make the adjacent free ends 53 and 54 of the V-shape continuous with each other.

[0084] Therefore, the V-shaped protrusions 50 are formed so that the free ends 53 and 54 are continuous with each other, thus increasing the contact area between the ATF, which has a higher viscosity than cooling water, and the first plate 11 and the second plate 12. This promotes heat exchange of the ATF flowing through the ATF flow path 13.

[0085] Furthermore, in the second variation, the V-shaped protrusions 50 of the first plate 11 and the V-shaped protrusions 50 of the second plate 12 are arranged such that their front ends 51 and openings 52 are offset from each other at the same position. That is, when viewed from above, the V-shaped protrusions 50 of the first plate 11 and the V-shaped protrusions 50 of the second plate 12 are formed to intersect at two points.

[0086] like Figure 15A As shown, in the stacked state of the first plate 11 and the second plate 12, the circular protrusions 40 of the first plate 11 and the circular protrusions 40 of the second plate 12 abut against each other to form a columnar shape. Conversely, as... Figure 15B As shown, at the two points where the V-shaped protrusions 50 of the first plate 11 and the V-shaped protrusions 50 of the second plate 12 intersect, the opposing V-shaped protrusions 50 do not abut against each other. That is, a cooling water flow path 14 is also formed between the opposing V-shaped protrusions 50. As a result, the heat exchange performance can be improved while suppressing the increase of flow resistance in the cooling water flow path 14.

[0087] Next, refer to Figure 16 and Figure 17 A third variation of the heat exchanger 100 according to an embodiment of the present invention will be described. Figure 16 This is a top view of the first plate 11 of a third variant of the heat exchanger 100. Figure 17 This is a top view of the second plate 12.

[0088] Similarly, in the third variation, adjacent V-shaped protrusions 50 are connected to make the adjacent free ends 53 and 54 of the V-shape continuous with each other.

[0089] Therefore, the V-shaped protrusions 50 are formed so that the free ends 53 and 54 are continuous with each other, thus increasing the contact area between the ATF, which has a higher viscosity than cooling water, and the first plate 11 and the second plate 12. This promotes heat exchange of the ATF flowing through the ATF flow path 13.

[0090] In the third variation, the V-shaped protrusions 50 are arranged radially not only near the cooling water inlet-side flow hole 11a, but also throughout the entire region from the cooling water inlet-side flow hole 11a and the cooling water outlet-side flow hole 11b. This allows the flow of incoming cooling water to diffuse throughout the entire region of the cooling water flow path 14, and allows the flow of outgoing cooling water to converge throughout the entire region of the cooling water flow path 14.

[0091] Similarly, in the third variation, the V-shaped protrusions 50 of the first plate 11 and the V-shaped protrusions 50 of the second plate 12 are arranged such that their front ends 51 and openings 52 are offset from each other at the same position. That is, when viewed from above, the V-shaped protrusions 50 of the first plate 11 and the V-shaped protrusions 50 of the second plate 12 are formed to intersect at two points.

[0092] Circular protrusions 40 are provided at the two points where they intersect. As a result, the circular protrusions 40 are provided at the position where the flow area of ​​the cooling water flow path 14 is smaller, so the dead water zone can be reduced compared to the case where the circular protrusions 40 are provided independently of the V-shaped protrusions 50.

[0093] Furthermore, in the third modification, an arc-shaped protrusion 60 is provided between the outer peripheral end of the first plate 11 and the cooling water inlet-side flow hole 11a, the cooling water outlet-side flow hole 11b, the ATF inlet-side flow hole 11d, and the ATF outlet-side flow hole 11e. The second plate 12 is the same. Therefore, the cooling water flowing between the outer peripheral end of the first plate 11 and the cooling water inlet-side flow hole 11a, the cooling water outlet-side flow hole 11b, the ATF inlet-side flow hole 11d, and the ATF outlet-side flow hole 11e can be rectified.

[0094] Next, refer to Figure 18 A fourth modification of the heat exchanger 100 according to an embodiment of the present invention will be described. Figure 18 This is a top view illustrating the configuration of the V-shaped protrusions 50 in the first plate 11 and the second plate 12 of a fourth modified example of the heat exchanger 100.

[0095] In the fourth variation, the V-shaped protrusions 50 are alternately arranged on the first plate 11 and the second plate 12 in the direction of the straight line connecting the ATF inlet-side flow hole 11d and the ATF outlet-side flow hole 11e.

[0096] Similarly, in the fourth variation, the V-shaped protrusion 50 generates a longitudinal vortex in the cooling water, thereby stirring the ATF and improving the heat exchange performance of both the ATF flow path 13 and the cooling water flow path 14.

[0097] The above implementation methods can achieve the following effects.

[0098] The heat exchanger 100, which exchanges heat between ATF and cooling water flowing in a direction intersecting the ATF, includes: a plurality of first plates 11 arranged in parallel with a gap; a second plate 12 arranged with a gap between an adjacent pair of first plates 11 and alternately stacked with the first plates 11 to alternately form an ATF flow path 13 for ATF flow and a cooling water flow path 14 for cooling water flow; and an inner fin 15 disposed in the ATF flow path 13 and abutting against the first plates 11 and the second plates 12. At least one of the first plate 11 and the second plate 12 has a plurality of V-shaped protrusions 50. The V-shaped protrusions 50 are formed in a V-shape when viewed from above, in a manner that is recessed in the ATF flow path 13 and protrudes in the cooling water flow path 14, and the height is lower than the flow path height of the cooling water flow path 14. The V-shaped protrusions 50 are configured such that the front end portion 51 and the opening portion 52 of the V-shape are arranged toward the flow direction of the cooling water in the cooling water flow path 14, and one of the pair of free ends 53 and 54 of the V-shape is located on the side of the ATF inlet side flow hole 11d, and the other is located on the side of the ATF outlet side flow hole 11e.

[0099] In this structure, at least one of the first plate 11 and the second plate 12 has a plurality of V-shaped protrusions 50. The V-shaped protrusions 50 are formed in a V-shape when viewed from above, recessed within the ATF flow path 13 and protruding within the cooling water flow path 14, and their height is lower than the flow path height of the cooling water flow path 14. The V-shaped protrusions 50 are configured such that the front end 51 and the opening 52 of the V-shape are aligned towards the flow direction of the cooling water in the cooling water flow path 14, and one of the pair of free ends 53 and 54 of the V-shape is located on the ATF inlet side flow hole 11d side, and the other is located on the ATF outlet side flow hole 11e side. Therefore, the ATF is agitated by flowing inside the V-shaped protrusions 50, thus improving the heat exchange performance of the ATF. Furthermore, longitudinal vortices are generated in the flow of cooling water under the action of the V-shaped protrusions 50, thus improving the heat exchange performance of the cooling water. Therefore, the heat exchange performance of ATF flow path 13 and cooling water flow path 14 can be improved simultaneously.

[0100] The embodiments of the present invention have been described above, but the above embodiments only show a part of the application examples of the present invention, and the technical scope of the present invention is not limited to the specific structure of the above embodiments.

[0101] For example, the V-shaped protrusion 50 can also be as follows: Figures 19A to 19D The shape shown. Figures 19A to 19D This is a top view used to illustrate variations of the various V-shaped protrusions 50.

[0102] exist Figure 19A In the modified example of the V-shaped protrusion 50 shown, the front end portion 51 is formed into an arc shape. Figure 19B In the modified example of the V-shaped protrusion 50 shown, not only the front end 51, but also the entire area between the free ends 53 and 54 is formed into an arc shape, thus becoming approximately U-shaped. Figure 19C In the modified example of the V-shaped protrusion 50 shown, from Figure 19B The modified example shown further provides straight sections towards the free ends 53 and 54, thus forming a roughly U-shaped form. Figure 19D In the modified example of the V-shaped protrusion 50 shown, the front end 51 is divided into two, thus becoming approximately W-shaped. Figures 19A to 19D These variations also include the V-shaped protrusion 50 formed in a V-shape.

[0103] Furthermore, in the above embodiments, the first fluid is ATF and the second fluid is cooling water. However, the first fluid and the second fluid are not limited to these.

[0104] This application claims priority based on Japanese Patent Application No. 2021-062949 filed with the Japan Patent Office on April 1, 2021, the entire contents of which are incorporated herein by reference.

Claims

1. A heat exchanger that performs heat exchange between a first fluid and a second fluid flowing in a direction intersecting the first fluid, characterized in that, The heat exchanger includes: Multiple first plates are arranged in parallel with intervals between them; The second plate, disposed between an adjacent pair of first plates with a gap, alternately stacked with the first plates to alternately form a first flow path for the flow of a first fluid and a second flow path for the flow of a second fluid; and A heat exchange facilitator is disposed in the first flow path and abuts against the first plate and the second plate. At least one of the first plate and the second plate has a plurality of protrusions, which are formed in a V-shape when viewed from above, such that they are recessed in the first flow path and protrude in the second flow path, and their height is lower than the flow path height of the second flow path. The protrusions are configured such that the V-shaped front end and opening are arranged facing the flow direction of the second fluid in the second flow path, and one of the pair of free ends of the V-shape is located on the first inlet side of the first fluid flowing into the first flow path, and the other is located on the first outlet side of the first fluid from the first flow path, and multiple protrusions are arranged along an orthogonal direction orthogonal to the flow direction of the second fluid. The protrusion on one side of the straight line connecting the second inlet for the second flow path and the second outlet for the second fluid from the second flow path is symmetrical about the center of the first plate and the second plate with respect to the other side of the straight line. The adjacent pair of protrusions are arranged in a V-shape, with the front end and the opening alternating in the orthogonal direction.

2. The heat exchanger according to claim 1, wherein, The heat exchange promoting component has a heat exchange wall that is erected between the first plate and the second plate. The heat exchange wall is configured to intersect the flow direction of the first fluid from the first inlet toward the first outlet.

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