JP6496067B1 - Heat exchanger - Google Patents

Abstract

An object is to provide a heat exchanger capable of improving heat exchange efficiency by suppressing local increase in temperature of a fluid. A heat exchanger (100) includes a second flow path (22) formed between adjacent tubes (50) and through which cooling water (second fluid) flows. The tube 50 projects into the second channel 22 and the oblique guide 71 which extends toward the upstream side 63 as the distance from the second fluid inlet 25 increases. Vertical guides 73 to 76 extending in the The pair of oblique guides 71 which project from the adjacent tubes 50 so as to face each other form a gap on the upstream side of the vertical guides 73 to 76 in the second flow path 22. [Selected figure] Figure 3

Description

  The present invention relates to a heat exchanger in which heat exchange is performed between fluids.

  Patent Document 1 discloses a multi-tubular heat exchanger that cools the exhaust gas of an internal combustion engine with cooling water.

  The multi-tube type heat exchanger includes a plurality of flat heat transfer tubes through which exhaust gas flows, and a casing through which cooling water flows between the flat heat transfer tubes. The cooling water flow introduced into the casing flows between the flat heat transfer tubes to exchange heat with the exhaust gas and cool the exhaust gas.

  A guide member for guiding the cooling water flow is disposed along the exhaust gas inlet side end between the flat heat transfer tubes. The cooling water flow is guided toward the exhaust gas inlet end by flowing along the guide member. As a result, a local rise in the temperature of the cooling water in the vicinity of the exhaust gas inlet side end is suppressed, and boiling of the cooling water is prevented.

JP, 2014-194296, A

  However, in the multi-tubular heat exchanger of Patent Document 1, since the cooling water flow introduced into the casing flows along the guide member, stagnation of the cooling water flow occurs behind the guide member, so the heat with exhaust gas is generated. There is a problem that the exchange can not be performed efficiently.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a heat exchanger capable of improving the heat exchange efficiency by suppressing a local increase in temperature of the fluid.

  According to an aspect of the present invention, there is provided a heat exchanger in which heat exchange is performed between a first fluid and a second fluid, which comprises a plurality of stacked tubes and a flow path formed inside the tubes. And a plurality of second flow paths formed between adjacent ones of the tubes for flowing the first fluid, and a plurality of second flow paths through which the second fluid flows, and the second flow path. And a second fluid inlet, which is disposed to be aligned in the flow passage width direction orthogonal to the flow passage direction, and which causes the second fluid to flow into the second flow passage, and the tube has the flow passage width direction And an oblique side extending toward the upstream side as it extends away from the second fluid inlet and protrudes into the second flow path. A guide and a vertical guide projecting in the second flow passage and extending in the flow passage direction; The oblique guide pair projecting opposite each other from the blanking forms a gap upstream of the longitudinal guide in the second flow path, the heat exchanger is provided, characterized in that.

  According to the above aspect, the second fluid flowing into the second flow passage from the second fluid inlet is guided along the oblique guide to the vicinity of the upstream side where stagnation is likely to occur, so that the temperature of the second fluid is localized Rising can be suppressed. Then, a portion of the second fluid flowing along the oblique guide is guided to the space between the vertical guides through the gap, thereby equalizing the velocity distribution of the second fluid. Thereby, the heat exchange efficiency of the heat exchanger can be enhanced.

FIG. 1 is a perspective view showing a heat exchanger according to an embodiment of the present invention. FIG. 2 is an exploded perspective view of the heat exchanger. FIG. 3 is a plan view of the tube. FIG. 4 is an exploded perspective view enlarging a part of the heat exchanger. FIG. 5 is a cross-sectional view taken along the line V-V of FIG. FIG. 6 is a plan view of a tube showing the flow direction of the cooling water. FIG. 7 is a diagram showing the relationship between the temperature difference T of the cooling water and the dimensional ratio D / H of the gap. FIG. 8 is a diagram showing the relationship between the pressure difference P of the cooling water and the dimensional ratio D / H of the gap. FIG. 9 is a diagram showing the relationship between the performance ratio T / P and the dimension ratio D / H of the gap. FIG. 10 is a plan view of a tube according to a modification.

  Hereinafter, a heat exchanger 100 according to an embodiment of the present invention will be described with reference to the attached drawings. In addition, in the attached drawings, a part of the heat exchanger 100 is omitted for simplification of the description.

  The heat exchanger 100 is a water-cooled EGR cooler used in an EGR (Exhaust Gas Recirculation) system (not shown) of a vehicle. The heat exchanger 100 cools a part (first fluid) of the exhaust gas discharged from the engine by the cooling water (second fluid). After flowing through the heat exchanger 100, the cooling water circulating through the cooling circuit circulates through the radiator and radiates heat to the outside air.

  As shown in FIGS. 1 and 2, in the heat exchanger 100, the cooling water is circulated between a plurality of tubes 50 forming the first flow passage 21 through which the exhaust gas flows and the tubes 50 to be stacked. And a casing 10 forming a second flow passage 22.

  Hereinafter, the configuration of the heat exchanger 100 will be described by setting three axes of X, Y, and Z orthogonal to each other in each drawing. In the tubes 50, the X axis direction in which the first flow path 21 extends is called "flow path direction", the Y axis direction is called "flow path width direction", and the Z axis direction in which the tubes 50 are arranged is "stacking direction". I call it ".

  As shown in FIG. 2, the tube 50 is formed into a tubular shape that is flat in the Z-axis direction by assembling the semicylindrical upper plate 60 and the lower plate 80. A fin 11 is disposed between the upper plate 60 and the lower plate 80 as a heat transfer member.

  The upper plate 60 and the lower plate 80 are formed into a flat semi-cylindrical shape by pressing a metal plate.

  The upper plate 60 has a plate-like heat transfer plate portion 61 extending in the X-axis direction and the Y-axis direction, and a pair extending in the Z-axis direction and the X-axis direction by bending from both sides of the heat transfer plate portion 61 Of the heat transfer plate portion 61 and the upstream side portion 63 extending in the X-axis direction and the Y-axis direction, and bent from the downstream end of the heat transfer plate portion 61; And a downstream side 64 extending in the direction and the Y-axis direction.

  Lower plate 80 is a plate-shaped heat transfer plate portion 81 extending in the X-axis direction and the Y-axis direction, and a pair extending in the Z-axis direction and the X-axis direction by bending from both sides of heat transfer plate portion 81 And the upstream side 83 extending from the upstream end of the heat transfer plate 81, and the downstream side 84 extending from the downstream end of the heat transfer plate 81. As shown in FIG.

  The upstream side portions 63 and 83 and the downstream side portions 64 and 84 of the tubes 50 to be stacked are joined without a gap. The heat transfer plate portions 61 and 81 of the tubes 50 to be stacked are arranged with an interval H (see FIG. 5), and the second flow path 22 is formed between the two.

  The casing 10 is formed into a tubular shape having a substantially rectangular cross section by assembling the semicylindrical upper shell 20 and the lower shell 30. Frame-shaped headers 15 and 16 are assembled to both open ends of the casing 10, respectively. The headers (not shown) of the EGR passage are connected to the headers 15 and 16 so that the exhaust gas is led to the first flow passage 21 in each of the tubes 50.

  Inside the header 15 is provided a first fluid inlet 35 (see FIG. 3) that distributes the exhaust introduced from the pipe of the EGR passage to the first flow passage 21. Inside the header 16 is provided a first fluid outlet 36 (see FIG. 3) for guiding the exhaust flowing out of the first flow passage 21 to the pipe of the EGR passage.

  Pipes 17 and 18 are connected to the casing 10. A pipe (not shown) for supplying cooling water is connected to one of the pipes 17. A pipe (not shown) for discharging the cooling water is connected to the other pipe 18.

  Inside the casing 10, a second fluid inlet 25 (see FIG. 3) for distributing the cooling water led from the pipe 17 to the second flow passage 22 between the respective tubes 50, and the cooling water flowing out from the second flow passage 22 And a second fluid outlet 27 (see FIG. 3) for guiding the fluid into the pipe 18.

  The upper shell 20 and the lower shell 30 are each formed in a semicylindrical shape by pressing a metal plate. The upper shell 20 has a bulge 33 forming a second fluid inlet 25 and a bulge 34 forming a second fluid outlet 27. The lower shell 30 has a bulging portion 31 forming a second fluid inlet 25 and a bulging portion 32 forming a second fluid outlet 27.

  At the time of manufacturing the heat exchanger 100, an assembly is formed in which the above-described members are assembled. The metal assembly is transferred to the heating furnace and heat treated to join the respective joints by brazing.

  At the time of operation of the heat exchanger 100, the cooling water circulating in the cooling circuit flows from the inside of the pipe 17 into the second fluid inlet 25 as shown by the black arrows in FIG. Distributed to As described later, the cooling water flowing through the second flow passage 22 collects at the second fluid outlet 27 and flows out through the inside of the pipe 18. On the other hand, a part of the exhaust gas discharged from the combustion chamber of the engine is distributed to the first flow passage 21 in each tube 50 through the first fluid inlet 35 in the header 15, as shown by the white arrow in FIG. Ru. The exhaust gas flowing through the first flow passage 21 is cooled by radiating heat to the cooling water flowing through the second flow passage 22 through the tubes 50. Exhaust gas flowing out of the first flow passage 21 collects through the first fluid outlet 36 in the header 16 and is supplied to the combustion chamber of the engine.

  Next, the configuration of the tube 50 will be described with reference to FIGS. 3 to 5.

  FIG. 3 is a plan view showing the upper plate 60 of the tube 50. As shown in FIG. The heat transfer plate portion 61 of the upper plate 60 extends between the upstream side portion 63 and the downstream side portion 64 and has a substantially rectangular outer shape centered on a center line Ox extending in the X-axis direction.

  The second fluid inlet 25 is formed facing the side end 62 near the upstream side 63. The second fluid inlet 25 is formed around a second fluid inlet center line Oyi extending in the Y-axis direction. The upstream side portion 63 is disposed to extend substantially parallel to the second fluid inlet center line Oyi.

  The second fluid outlet 27 is formed facing the side end 62 near the downstream side 64. The second fluid outlet 27 is formed around a center line Oyo extending in the Y-axis direction. The downstream side 64 is arranged to extend substantially parallel to the center line Oyo.

  The second fluid inlet 25 is formed facing one side end 62. The second fluid outlet 27 is formed facing the other side end 62. The second fluid inlet 25 and the second fluid outlet 27 may both be formed facing the one side end 62.

  In the heat transfer plate portion 61, one oblique guide 71, one upstream side oblique guide 72, and four vertical guides 73 to 76 are formed by press working. The oblique guide 71, the upstream oblique guide 72, and the longitudinal guides 73 to 76 project into the second flow passage 22 and guide the flow of cooling water as described later. The number of vertical guides 73 to 76 is not limited to this, and may be arbitrarily set according to the dimensions of the heat transfer plate 61 and the like.

  The oblique guide 71 is inclined with respect to the upstream side 63, and is disposed so as to approach the upstream side 63 as it is separated from the second fluid inlet 25. The center line O71 of the oblique guide 71 is arranged to intersect the second fluid inlet 25. The inclination angle θ1 with respect to the upstream side portion 63 (second fluid inlet center line Oyi) of the oblique guide 71 is arbitrarily set according to the arrangement of the heat transfer plate portion 61 and the second fluid inlet 25 or the like.

  The oblique guide 71 has an upstream end 71 a facing the second fluid inlet 25. The upstream end 71 a is disposed between the second fluid inlet center line Oyi and the upstream end 73 a of the vertical guide 73 in the X-axis direction.

  The upstream side oblique guide 72 is disposed between the upstream side 63 and the oblique guide 71. The upstream end 72a of the upstream side oblique guide 72 is disposed between the upstream side 63 and the second fluid inlet center line Oyi in the X-axis direction. The upstream diagonal guide 72 has a length shorter than that of the diagonal guide 71.

  The center line O 72 of the upstream oblique guide 72 is disposed to intersect the second fluid inlet 25. The inclination angle θ2 of the upstream side oblique guide 72 is set to a value substantially equal to the inclination angle θ1 of the oblique guide 71. That is, the upstream side oblique guide 72 is disposed substantially parallel to the oblique guide 71. The distance S between the upstream side oblique guide 72 and the oblique guide 71 is arbitrarily set according to the arrangement of the heat transfer plate portion 61 and the second fluid inlet 25 or the like.

  The vertical guides 73 to 76 are disposed between the oblique guide 71 and the downstream side 64 in the X-axis direction. The vertical guides 73 to 76 are disposed substantially in parallel with the side end 62 and substantially orthogonal to the upstream side 63 and the downstream side 64. The vertical guides 73 to 76 are arranged to have a substantially constant interval in the Y-axis direction.

  The upstream ends 73 a to 76 a of the vertical guides 73 to 76 are arranged stepwise in such a manner as to approach the upstream side portion 63 as they move away from the second fluid inlet 25. The upstream ends 73 a to 76 a of the vertical guides 73 to 76 are arranged on a line A substantially parallel to the oblique guide 71 and have a substantially constant distance C with respect to the oblique guide 71.

  The downstream ends 73 b to 76 b of the vertical guides 73 to 76 are arranged to have a substantially constant distance with respect to the downstream side 64.

  FIG. 4 is a perspective view showing the lower plate 80 and the upper plate 60. As shown in FIG. In the heat transfer plate portion 81 of the lower plate 80, one oblique guide 91, one upstream side oblique guide 92, and four longitudinal guides 93 to 96 are formed by press working. The oblique guide 91, the upstream side oblique guide 92, and the longitudinal guides 93 to 96 are at the same position so as to respectively oppose and project the oblique guide 71, the upstream side oblique guide 72, and the longitudinal guides 73 to 76 of the upper plate 60. Be placed.

  FIG. 5 is a cross-sectional view taken along the line V-V of FIG. The heat transfer plate portion 61 of the upper plate 60 and the heat transfer plate portion 81 of the lower plate 80 are arranged to extend substantially in parallel with the flow path height H in the Z-axis direction.

  The oblique guides 71 and 91 are formed by press-forming the upper plate 60 and the lower plate 80 respectively, and are raised in a ridge shape from the flow channel surfaces 69 and 89 of the second flow channel 22, and the flow channel surface of the first flow channel 21 Grooves 68 and 88 are dimples. A gap 23 having a size D in the Z-axis direction is formed between the oblique guide 71 of the upper plate 60 and the oblique guide 91 of the lower plate 80. As described later, the dimensional ratio D / H of the size D to the flow path height H is set to a range of 0.05 or more and 0.43 or less by simulation analysis. The actual flow path height H is set to 1.0 mm. The size D of the gap 23 is set in the range of not less than 0.05 and not more than 0.43 mm.

  Similarly, the upstream side oblique guides 72 and 92 and the longitudinal guides 73 to 76 and 93 to 96 are dimples formed by press forming the upper plate 60 and the lower plate 80, respectively. Also between the upstream diagonal guide 72 and the vertical guides 73 to 76 of the upper plate 60 and the upstream diagonal guide 92 and the vertical guides 93 to 96 of the lower plate 80, gaps having a size D equal to the gap 23 are It is formed.

  Next, the flow of the cooling water at the time of operation of the heat exchanger 100 will be described. FIG. 6 shows the flow direction of the cooling water by an arrow.

  As shown in FIG. 6, a portion of the cooling water flowing from the second fluid inlet 25 into the second flow passage 22 is guided by the oblique guide 71 in the Y-axis direction, and the remainder is the vertical closest to the second fluid inlet 25. It is guided by the guide 73 in the X-axis direction.

  The cooling water flow flowing into the second flow passage 22 from the second fluid inlet 25 flows in the X-axis direction along the vertical guide 73, whereby the downstream end flow passage portion 22c located in the vicinity of the downstream side portion 64 (see FIG. 6). In the region (right side region in FIG. 6) in the region (right side region in FIG. 6).

  The cooling water flowing from the second fluid inlet 25 into the second flow path 22 flows along the oblique guide 71, the upstream oblique guide 72, the oblique guide 91, and the upstream oblique guide 92, It is led to the upstream end channel portion 22a (the left region in FIG. 6) located in the vicinity. Thus, in the upstream end flow path portion 22a, stagnation of the cooling water flow is suppressed also in the region far from the second fluid inlet 25 (the region on the lower left side in FIG. 6). As a result, in the upstream end flow path portion 22a, a local rise in temperature of the cooling water due to heat received from the exhaust is suppressed, and boiling of the cooling water is prevented.

  A portion of the cooling water flow flowing along the oblique guide 71 and the oblique guide 91 flows in the X-axis direction through the gap 23 (see FIG. 5), so that the vertical guides 73 to 76, the vertical guides 93 to 96, and the casing 10 It is led to the intermediate flow path portion 22b to be partitioned. On the downstream side of the oblique guide 71 and the oblique guide 91, the circulation of the cooling water through the gap 23 suppresses the occurrence of stagnation.

  Since the upstream ends 73a to 76a of the vertical guides 73 to 76 are arranged with a fixed distance C (see FIG. 3) to the oblique guide 71, the velocity distribution of the cooling water flow in the intermediate flow passage 22b is uniform. Be

  The cooling water flow passing through the intermediate flow passage 22b flows along the inner walls of the vertical guides 73 to 76, the vertical guides 93 to 96, and the casing 10, whereby the downstream end flow passage located in the vicinity of the downstream side 64 It is led to 22c. As a result, even in a region far from the second fluid outlet 27 of the downstream end flow passage portion 22c, stagnation of the cooling water flow is suppressed, and boiling of the cooling water is prevented. The cooling water flow that has flowed through the downstream end flow passage 22 c flows out to the second fluid outlet 27 along the downstream side 64.

  In this manner, in the second flow path 22, the velocity distribution of the cooling water flow is made by the oblique guide 71, the upstream oblique guide 72, the oblique guide 91, the upstream oblique guide 92, the vertical guides 73 to 76, and the vertical guides 93 to 96. Be equalized. Thereby, the heat exchanger 100 has a high heat exchange efficiency.

  In the second flow path 22, by reducing the size D of the gap 23 to a certain extent with respect to the flow path height H, the heat transfer coefficient is increased while the flow path resistance is increased. In the heat exchanger 100, the dimensional ratio D / H of the size D to the flow path height H is determined as follows.

  In FIG. 7, the value by which the temperature difference T of the cooling water generated when the cooling water and the exhaust gas are caused to flow through the heat exchanger 100 under predetermined conditions changes according to the dimensional ratio D / H of the gap 23 is determined by simulation analysis Show the results. The temperature difference T of the cooling water is a difference between the temperature of the cooling water flowing through the second fluid inlet 25 and the temperature of the cooling water flowing through the second fluid outlet 27. As shown in FIG. 7, the temperature difference T of the cooling water gradually increases as the dimensional ratio D / H becomes larger than 0, and takes a peak value in the range of the dimensional ratio D / H of 0.2 to 0.3. As the ratio D / H becomes larger than 0.3, it becomes gradually lower.

  In FIG. 8, the pressure difference P of the cooling water generated when the cooling water and the exhaust gas are allowed to flow through the heat exchanger 100 under predetermined conditions is determined by simulation analysis as a value that changes according to the dimensional ratio D / H of the gap 23. Show the results. The pressure difference P of the coolant is a difference between the pressure of the coolant flowing through the second fluid inlet 25 and the pressure of the coolant flowing through the second fluid outlet 27. As shown in FIG. 8, the pressure difference P of the cooling water gradually decreases as the dimensional ratio D / H increases from 0 to 0.5.

  FIG. 9 shows the relationship between the performance ratio T / P obtained by dividing the temperature difference T of the cooling water by the pressure difference P of the cooling water and the dimensional ratio D / H of the gap 23. As shown in FIG. 9, the performance ratio T / P gradually increases as the dimensional ratio D / H becomes larger than 0, and takes a peak value in the range of the dimensional ratio D / H of 0.2 to 0.3, and the dimensional ratio As D / H becomes larger than 0.3, it becomes lower gradually. The performance ratio T / P becomes equal to or higher than the standard value required in the market when the dimensional ratio D / H is in the range of 0.05 or more and 0.43 or less.

  Next, the effects of the present embodiment will be described.

  [1] According to the present embodiment, the plurality of tubes 50 to be stacked, the first flow path 21 formed inside the tube 50 and through which the exhaust (first fluid) flows, and the plurality of first flow paths 21 The first fluid inlet 35 for distributing the exhaust gas, the first fluid outlet 36 for collecting the exhaust gases flowing out of the plurality of first flow paths 21, and the cooling water (second fluid) formed between the adjacent tubes 50 , A second fluid inlet 25 for distributing the cooling water to the plurality of second channels 22, and a second fluid outlet 27 for collecting the cooling water flowing out from the plurality of second channels 22. And. The first fluid inlet 35 and the first fluid outlet 36 are arranged in line with the first channel 21 in the channel direction (X-axis direction), and the second fluid inlet 25 and the second fluid outlet 27 are The two flow paths 22 are arranged in the flow path width direction (Y-axis direction) orthogonal to the flow path direction (X-axis direction). The tube 50 extends in the flow passage width direction (Y-axis direction), and includes upstream side portions 63 and 83, which are ends from which the exhaust flows into the first flow passage 21 from the first fluid inlet 35, and a second flow passage. 22 and diagonal guides 71 and 91 extending toward the upstream side portions 63 and 83 as they are separated from the second fluid inlet 25, and project to the second flow path 22 and extend in the flow path direction (X-axis direction) Existing vertical guides 73 to 76, 93 to 96; The pair of oblique guides 71 and 91 which project from the adjacent tubes 50 so as to face each other form a gap 23 on the upstream side of the vertical guides 73 to 76 and 93 to 96 in the second flow path 22.

  Based on the above configuration, the cooling water flowing into the second flow passage 22 from the second fluid inlet 25 is guided along the oblique guides 71 and 91 to the vicinity of the upstream side portion 63 where stagnation is likely to occur. It is suppressed that the temperature rises locally and boiling of the cooling water is prevented. Then, a part of the cooling water flowing along the oblique guides 71 and 91 is guided between the vertical guides 73 to 76 and 93 to 96 through the gap 23, so that the velocity distribution of the cooling water flow is equalized. Thus, the heat exchange efficiency of the heat exchanger can be enhanced.

  [2] Further, the vertical guides 73 to 76 are arranged in a step-like manner such that the upstream ends 73a to 76a approach the upstream side portion 63 as the distance from the second fluid inlet 25 increases.

  Based on the above configuration, the upstream ends 73a to 76a of the vertical guides 73 to 76 are disposed along the oblique guides 71, so that the cooling water in the second flow path 22 passes from the gap 23 to between the vertical guides 73 to 76. And the flow channel length is equalized. Thereby, equalization of velocity distribution of a cooling water flow which flows between vertical guides 73-76 is attained.

  [3] Further, the second fluid inlet 25 is formed around a second fluid inlet center line Oyi extending in the channel width direction (Y-axis direction). The upstream end 71 a of the oblique guide 71 is between the second fluid inlet center line Oyi and the upstream end 73 a of the vertical guide 73 provided at a position closest to the second fluid inlet 25 in the flow channel direction (X axis direction). It is arranged to be placed in

  Based on the above configuration, most of the cooling water flowing into the second flow path 22 from the second fluid inlet 25 is guided by the oblique guide 71 in the flow path width direction (Y-axis direction), and a portion thereof is the second It is guided in the flow channel direction (X-axis direction) by the vertical guide 73 closest to the fluid inlet 25. Thereby, the velocity distribution of the cooling water flow in the second flow passage 22 is equalized.

  [4] Moreover, the tube 50 is provided with the upstream side oblique guide 72 which extends toward the upstream side 63 as it protrudes from the second flow path 22 and is separated from the second fluid inlet 25, and the upstream side oblique guide 72 The configuration is such that the upstream side portion 63 and the oblique guide 71 are disposed.

  Based on the above configuration, the cooling water flowing into the second flow passage 22 from the second fluid inlet 25 is guided along the upstream side oblique guide 72 to the vicinity of the upstream side portion 63 where stagnation easily occurs. It is suppressed that the temperature rises locally.

  [5] Also, the oblique guides 71 and 91 are raised from the flow passage surfaces 69 and 89 facing the second flow passage 22 of the tube 50 and dimples recessed on the flow passage surfaces 68 and 88 facing the first flow passage 21. The configuration is

  Based on the above configuration, the oblique guides 71 and 91 can be formed by press-molding the upper plate 60 and the lower plate 80 of the tube 50, respectively. Thereby, the productivity of the tube 50 is secured.

  [6] The dimensional ratio D / H of the size D of the gap 23 to the flow path height H of the second flow path 22 in the stacking direction of the tubes 50 (Z-axis direction) is 0.05 or more and 0.43 or less The configuration is set to the range of

  Based on the above configuration, in the heat exchanger 100, it is possible to achieve a balance between suppressing the flow path resistance of the second flow path 22 and increasing the heat transfer coefficient.

  Next, a modification of the heat exchanger 100 shown in FIG. 10 will be described.

  [7] In this modification, as shown in FIG. 10, the inclination angle θ2 of the upstream side oblique guide 72 with respect to the flow path width direction (Y axis direction) is larger than the inclination angle θ1 of the oblique guide 71.

  Based on the above configuration, the cooling water flowing into the second flow path 22 from the second fluid inlet 25 flows along the upstream side oblique guide 72 that is inclined more than the oblique guide 71, so that the upstream side portion 63 where retention tends to occur The flow velocity introduced to the vicinity of is increased, and the local rise of the temperature of the cooling water is suppressed.

  As mentioned above, although the embodiment of the present invention was described, the above-mentioned embodiment showed only a part of application example of the present invention, and in the meaning of limiting the technical scope of the present invention to the concrete composition of the above-mentioned embodiment. Absent.

  For example, in the above embodiment, the oblique guide 71 and the upstream oblique guide 72 are configured to extend linearly, but may extend in a curved linear shape.

  In the above embodiment, the upstream side oblique guide 72 is provided along with the oblique guide 71. However, the upstream side oblique guide 72 may not be provided, and only the oblique guide 71 may be provided.

  Although this invention is suitable as a heat exchanger mounted in a vehicle, it is applicable also to the heat exchanger used other than a vehicle.

21 first channel 22 second channel 23 gap 25 second fluid inlet 35 first fluid inlet 50 tube 63 upstream side 68, 69, 88, 89 channel surface 71, 91 diagonal guide 71a upstream end 72, 92 upstream Diagonal guides 73-76, 93-96 Vertical guides 73a-76a upstream end 100 heat exchanger

Claims (7)

A heat exchanger in which heat exchange is performed between a first fluid and a second fluid, the heat exchanger comprising:
With multiple tubes stacked,
A plurality of first flow paths formed inside the tube and extending in the flow path direction and in which the first fluid flows;
A plurality of second flow paths formed between adjacent ones of the tubes and in which the second fluid flows;
And a second fluid inlet, which is disposed to be aligned in a flow passage width direction orthogonal to the flow passage direction with respect to the second flow passage, and causes the second fluid to flow into the second flow passage.
The tube is
An upstream side portion which is an end portion which extends in the channel width direction and into which the first fluid flows into the first channel;
An oblique guide that projects into the second flow path and extends so as to approach the upstream side as the distance from the second fluid inlet increases;
And a vertical guide projecting in the second flow path and extending in the flow path direction,
A pair of the diagonal guides projecting opposite to each other from the adjacent tubes form a gap on the upstream side of the vertical guide in the second flow path,
A heat exchanger characterized by The heat exchanger according to claim 1, wherein
The upstream ends of the plurality of vertical guides are arranged to approach the upstream side as they are farther from the second fluid inlet.
A heat exchanger characterized by The heat exchanger according to claim 1 or 2, wherein
The second fluid inlet is formed around a second fluid inlet center line extending in the flow passage width direction,
The upstream end opposite to the second fluid inlet of the oblique guide is the second fluid inlet center line in the flow direction, and the upstream end of the vertical guide provided at a position closest to the second fluid inlet; Placed between
A heat exchanger characterized by The heat exchanger according to any one of claims 1 to 3, wherein
The tube further includes an upstream diagonal guide that protrudes into the second flow path and extends closer to the upstream side as the distance from the second fluid inlet increases.
The upstream side oblique guide is disposed between the upstream side and the oblique guide.
A heat exchanger characterized by The heat exchanger according to claim 4, wherein
The inclination angle of the upstream oblique guide with respect to the flow passage width direction is larger than the inclination angle of the oblique guide.
A heat exchanger characterized by The heat exchanger according to any one of claims 1 to 5, wherein
The oblique guide is a dimple which protrudes from a flow passage surface facing the second flow passage of the tube and is recessed in the flow passage surface facing the first flow passage.
A heat exchanger characterized by The heat exchanger according to any one of claims 1 to 6, wherein
The dimensional ratio of the gap to the flow channel height of the second flow channel in the stacking direction of the tubes is set to a range of 0.05 or more and 0.43 or less.
A heat exchanger characterized by

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