JP7006626B2 - Heat exchanger - Google Patents

Description

The present disclosure relates to heat exchangers.

Conventionally, there is a heat exchanger described in Patent Document 1 below. The heat exchanger described in Patent Document 1 includes a plurality of tubes arranged in a laminated manner, an inlet tank connected to one end of each tube, and an outlet tank connected to the other end of each tube. ing. At the end of the inlet tank in the stacking direction of the tubes, an inflow pipe is provided to allow fluid to flow into the inlet tank. Out of both ends of the outlet tank in the tube stacking direction, the end on the same side as the inflow port is provided with a discharge pipe for discharging the fluid in the outlet tank.

By the way, in the heat exchanger having such a structure, the fluid tends to flow easily into the tube arranged near the inflow pipe, but it tends to be difficult to flow the fluid into the tube arranged away from the inflow pipe. .. This is a factor that makes the flow rate distribution of a plurality of tubes uneven.

In order to solve this problem, in the heat exchanger described in Patent Document 1 below, a plate-shaped member is provided inside the inlet tank. The plate-shaped member is formed by partially closing the opening at one end of a predetermined tube arranged on the same side as the inflow pipe and the discharge pipe in the tube stacking direction among the plurality of tubes. The opening area at one end is reduced. As a result, it becomes difficult for the fluid to flow into a predetermined number of tubes arranged near the inflow pipe, so that the flow rates of the plurality of tubes can be made uniform.

Japanese Patent No. 4830918

When the opening at one end of the tube is partially closed with a plate-like member as in the heat exchanger described in Patent Document 1, when the fluid flows into the tube from one end of the tube, the fluid flows into the tube. Since the fluid collides with the plate-shaped member, the flow of the fluid in the tube tends to be turbulent. Disturbances in the flow of fluid in the tube can cause noise.

The present disclosure has been made in view of these circumstances, and an object of the present invention is to provide a heat exchanger capable of reducing noise while suppressing bias in flow rate distribution in a plurality of tubes.

The heat exchanger that solves the above problems includes a heat exchange core portion (20), a first tank portion (31), a second tank portion (32), and a side plate (41) . A plurality of tubes (21) through which a fluid flows are laminated and arranged in the heat exchange core portion. The first tank portion is connected to one end of a plurality of tubes and distributes the fluid to the plurality of tubes. The second tank portion is connected to the other end of the plurality of tubes and collects the fluid that has passed through the plurality of tubes. Side plates are arranged at both ends of the heat exchange core portion in the tube stacking direction to reinforce the heat exchange core portion. When the direction in which a plurality of tubes are stacked and arranged is the tube stacking direction, an inflow pipe (40) that allows fluid to flow into the inside of the first tank portion at one end of the first tank portion located in the tube stacking direction. ) Is connected. A discharge pipe (43) for discharging the fluid inside the second tank portion is connected to one end of the second tank portion located on the same side as the inflow pipe in the tube stacking direction. Both ends of the side plate are connected to the first tank portion and the second tank portion, respectively. The first tank portion from the inflow pipe so that the fluid flows from the inflow pipe to the first tank portion at a predetermined angle with respect to the tube stacking direction at one end of the side plate connected to the first tank portion. A drift structure (412) that changes the flow direction of the fluid flowing into the water is provided.

According to this configuration, when the fluid flows into the first tank portion from the inflow pipe, the fluid flows at a predetermined angle with respect to the tube stacking direction, so that the fluid flows in a predetermined direction at one end of the first tank portion. The velocity of the fluid flowing along the area increases. As a result, the velocity distribution of the fluid flowing through one end of the first tank portion becomes biased. Due to this bias in the velocity distribution of the fluid, the pressure loss when the fluid flows into the tube becomes large in the region where the velocity of the fluid is high. Therefore, it becomes difficult for the fluid to flow into the tube arranged near one end of the first tank portion. By intentionally biasing the flow rate distribution of each tube in this way, the bias of the flow rate distribution of the tubes due to the position of the inflow pipe can be offset, so that the bias of the flow rate distribution in a plurality of tubes is suppressed. be able to. Further, according to the above configuration, it is not necessary to block one end of the tube, so that the flow of the fluid in the tube is unlikely to be disturbed. Therefore, noise can be reduced.

The reference numerals in parentheses described in the above means and claims are examples showing the correspondence with the specific means described in the embodiments described later.

According to the present disclosure, it is possible to provide a heat exchanger capable of reducing noise while suppressing bias in flow rate distribution in a plurality of tubes.

FIG. 1 is a front view showing the front structure of the heat exchanger of the first embodiment. FIG. 2 is a cross-sectional view showing a cross-sectional structure taken along the line II-II of FIG. FIG. 3 is a cross-sectional view showing a cross-sectional structure of a tube of a modified example of the first embodiment. FIG. 4 is a cross-sectional view showing a cross-sectional structure of the heat exchanger of the second embodiment. FIG. 5 is a cross-sectional view showing a cross-sectional structure of the heat exchanger of the third embodiment. FIG. 6 is a cross-sectional view showing a cross-sectional structure of the heat exchanger of the fourth embodiment. FIG. 7 is a perspective view showing a perspective structure of an end portion of the side plate of the fourth embodiment. FIG. 8 is a cross-sectional view showing a cross-sectional structure of the heat exchanger of the fifth embodiment. FIG. 9 is a cross-sectional view showing a cross-sectional structure of the heat exchanger of the sixth embodiment. FIG. 10 is a cross-sectional view showing a cross-sectional structure of the heat exchanger of the seventh embodiment. FIG. 11 is a cross-sectional view showing a cross-sectional structure of the heat exchanger of the eighth embodiment. FIG. 12 is a cross-sectional view showing a cross-sectional structure of the heat exchanger of the ninth embodiment. FIG. 13 is a cross-sectional view showing a cross-sectional structure of the inflow pipe of the ninth embodiment. FIG. 14 is a perspective view showing a perspective structure of the drift member of the ninth embodiment.

Hereinafter, an embodiment of the heat exchanger will be described with reference to the drawings. In order to facilitate understanding of the description, the same components are designated by the same reference numerals as possible in the drawings, and duplicate description is omitted.
<First Embodiment>
First, the heat exchanger 10 of the first embodiment shown in FIG. 1 will be described. The heat exchanger 10 is used, for example, as a heater core of an air conditioner mounted on a vehicle. The air conditioner is a device that air-conditions the interior of a vehicle by blowing heated or cooled air-conditioned air into the vehicle interior. The heat exchanger 10 is arranged in an air conditioning duct through which air conditioning air flows. Engine cooling water circulates inside the heat exchanger 10. The cooling water flowing inside the heat exchanger 10 is in a liquid single-phase state. The heat exchanger 10 heats the conditioned air by the heat of the cooling water by exchanging heat between the cooling water flowing inside the heat exchanger 10 and the conditioned air flowing in the conditioned duct. The conditioned air heated by the heat exchanger 10 is blown into the vehicle interior through the air conditioning duct to heat the vehicle interior. In the present embodiment, the cooling water flowing inside the heat exchanger 10 corresponds to the fluid.

As shown in FIG. 1, the heat exchanger 10 includes a heat exchange core portion 20, tank portions 31, 32, and side plates 41, 42. The heat exchanger 10 is made of a metal material such as an aluminum alloy.
The heat exchange core portion 20 is a portion that exchanges heat between the cooling water and the air. The heat exchange core portion 20 has a plurality of tubes 21 arranged in a laminated manner at predetermined intervals in the X-axis direction in the drawing, and a plurality of fins 22 arranged in a gap between adjacent tubes 21. Have. Note that FIG. 1 shows only a part of the plurality of fins 22. Hereinafter, the X-axis direction is also referred to as “tube stacking direction X”. Further, one of the tube stacking directions X is referred to as "X1 direction", and the other direction is referred to as "X2 direction".

As shown in FIG. 2, the tube 21 is composed of an elongated pipe having an internal flow path W10 through which cooling water flows. The cross-sectional shape of the tube 21 orthogonal to the Z-axis direction is flat. As shown in FIG. 1, the tube 21 is formed so as to extend in the Z-axis direction. Hereinafter, the Z-axis direction is also referred to as “tube longitudinal direction Z”. Further, one direction of the tube longitudinal direction Z is referred to as "Z1 direction", and the other direction is referred to as Z2 direction. Further, the direction orthogonal to both the X-axis direction and the Z-axis direction is also referred to as "tube width direction Y". In the heat exchanger 10, air flows in the tube width direction Y through the gap formed between the adjacent tubes 21 and 21.

The fin 22 is a so-called corrugated fin formed by bending a thin and long metal plate in a wavy shape. The bent portion of the fin 22 is fixed to the outer peripheral surfaces of the adjacent tubes 21 and 21 by brazing. The fins 22 are provided to increase the heat exchange efficiency between the cooling water and the air by increasing the heat transfer area of the tube 21.

The tank portions 31 and 32 are made of a tubular member formed so as to extend in the tube stacking direction X. As shown in FIG. 2, an internal flow path W20 through which cooling water flows is formed inside the first tank portion 31. One end 210 of a plurality of tubes 21 in the Z2 direction is connected to the first tank portion 31. One end 210 of the plurality of tubes 21 is arranged so as to penetrate the peripheral wall 312 of the first tank 31 and extend to the internal flow path W20 of the first tank 31. Similarly, an internal flow path through which the cooling water flows is formed inside the second tank portion. As shown in FIG. 1, the second tank portion 32 is connected to the other end portions 211 of the plurality of tubes 21 in the Z1 direction.

The end portion 311 of the first tank portion 31 in the X1 direction is closed. An inflow port 33 is provided at the end 310 of the first tank portion 31 in the X2 direction. The inflow port 33 is formed in a cylindrical shape. As shown in FIG. 2, the end portion 330 of the inflow port 33 in the X1 direction is joined to and fixed to the end portion 310 of the first tank portion 31 by brazing or the like. The axis m1 shown in FIG. 2 indicates the central axis of the first tank portion 31. As shown in FIG. 2, the inflow port 33 is arranged on the same axis m1 as the first tank portion 31.

An inflow pipe 40 is connected to the end 331 of the inflow port 33 in the X2 direction. Specifically, a flange portion 400 is formed at the tip end portion of the inflow pipe 40. The inflow pipe 40 is fixed to the end portion 331 of the inflow port 33 by crimping the flange portion 400 to the end portion 331 of the inflow port 33. A sealing member 50 for sealing between the outer peripheral surface of the inflow pipe 40 and the inner peripheral surface of the inflow port 33 is arranged.

An inclined surface 403 is formed on the inner wall surface 402 of the opening 401 that opens into the first tank portion 31 in the inflow pipe 40. The inclined surface 403 is formed so as to be inclined with respect to the tube stacking direction X.
As shown in FIG. 1, a discharge port 34 is provided at the end 320 of the second tank portion 32 in the X2 direction. Since the connection structure between the second tank portion 32 and the discharge port 34 is substantially the same as the connection structure between the first tank portion 31 and the inflow port 33 shown in FIG. 2, detailed description thereof will be omitted. A discharge pipe 43 is connected to the discharge port 34. The discharge pipe 43 is provided at one end of the second tank portion 32 located on the same side as the inflow pipe 40 in the tube stacking direction X. The end portion 321 of the second tank portion 32 in the X1 direction is closed.

As shown in FIG. 1, the side plates 41 and 42 are arranged at both ends of the heat exchange core portion 20 in the X-axis direction, respectively. The respective ends 410 and 420 of the side plates 41 and 42 in the Z2 direction are connected to the first tank portion 31. As shown in FIG. 2, the end portion 410 of the side plate 41 is arranged so as to penetrate the peripheral wall 312 of the first tank portion 31 and extend to the internal flow path W20 of the first tank portion 31. Similarly, the end portion 420 of the side plate 42 is also connected to the first tank portion 31. Further, as shown in FIG. 1, the other end portions 411 and 421 of the side plates 41 and 42 in the Z1 direction are connected to the second tank portion 32. The side plates 41 and 42 are provided to reinforce the heat exchange core portion 20.

Next, an operation example of the heat exchanger 10 of the present embodiment will be described.
In the heat exchanger 10, single-phase cooling water flows into the inside of the first tank portion 31 through the inflow pipe 40. The cooling water that has flowed into the first tank portion 31 is distributed to each tube 21 by flowing into the internal flow path W10 of each tube 21 from one end portion 210 of each tube 21. The cooling water distributed to each tube 21 flows through the internal flow path W10 of each tube 21 toward the second tank portion 32. In the heat exchanger 10, heat is exchanged between the cooling water flowing through the internal flow path W10 of each tube 21 and the air flowing between the adjacent tubes 21 and 21, so that the heat of the cooling water becomes air. It is transmitted and the air is heated. The cooling water that has passed through each tube 21 is collected in the second tank portion 32 and then discharged from the discharge pipe 43.

In this heat exchanger 10, since the inclined surface 403 is formed on the inner wall surface 402 of the inflow pipe 40, as shown in FIG. 2, the cooling water flowing from the inflow pipe 40 into the first tank portion 31 is indicated by an arrow. It flows in the direction indicated by D1, that is, in the direction forming a predetermined angle θ with respect to the axis m1. As the cooling water flows from the opening 401 of the inflow pipe 40 in the direction indicated by the arrow D1, the velocity of the cooling water flowing through the region A1 along the arrow D1 at the end 310 of the first tank portion 31 increases. As a result, the velocity distribution of the cooling water flowing through the end 310 of the first tank portion 31 becomes biased in the tube width direction Y. Due to this bias in the speed distribution of the cooling water, the pressure loss when the cooling water flows into the tube 21 becomes large in the region A1 where the speed of the cooling water is high. As a result, it becomes difficult for the cooling water to flow into the plurality of tubes 21 arranged near the end portion 310 of the first tank portion 31.

According to the heat exchanger 10 of the present embodiment described above, the actions and effects shown in the following (1) and (2) can be obtained.
(1) In the heat exchanger 10 having a structure as shown in FIG. 1, the cooling water flowing from the inflow pipe 40 into the first tank portion 31 is arranged in the vicinity of the end portion 310 of the first tank portion 31. While it is easy to distribute to the tube 21, it is difficult to distribute to the tube 21 arranged at a position separated from the end portion 310 of the first tank portion 31. In this regard, in the heat exchanger 10 of the present embodiment, as shown in FIG. 2, the cooling water is less likely to flow into the plurality of tubes 21 arranged near the end 310 of the first tank portion 31. The flow rate distribution of the plurality of tubes 21 can be intentionally biased. As a result, the deviation of the flow rate distribution of the tube 21 due to the position of the inflow pipe 40 can be offset, and as a result, the deviation of the flow rate distribution in the plurality of tubes 21 can be suppressed. Further, in the heat exchanger 10 of the present embodiment, since one end 210 of the tube 21 is not closed, the inside of the tube 21 is compared with the structure in which one end of the tube is closed as in the conventional heat exchanger. The flow of cooling water is unlikely to be disturbed. Therefore, it is possible to reduce noise.

(2) An inclined surface 403 inclined with respect to the tube stacking direction X is formed on the inner wall surface 402 of the opening 401 that opens inside the first tank portion 31 in the inflow pipe 40. According to such a configuration, it is possible to easily realize a structure in which the cooling water flows from the inflow pipe 40 to the first tank portion 31 at a predetermined angle θ with respect to the tube stacking direction X.

(Modification example)
Next, a modification of the heat exchanger 10 of the first embodiment will be described.
In the heat exchanger 10 of this modification, a so-called B-shaped tube having a structure as shown in FIG. 3 is adopted as the tube 21. As shown in FIG. 3, the tube 21 is formed with a partition wall 212 for partitioning the internal flow path W10 into two flow paths W11 and W12.

When the tube 21 having such a structure is used for the heat exchanger 10, the pressure loss of the cooling water flowing through the flow paths W11 and W12 of the tube 21 becomes larger than that of the tube having no partition wall 212. Therefore, the faster the flow velocity of the cooling water flowing inside the first tank portion 31, the more difficult it is for the cooling water to flow into the flow paths W11 and W12 of each tube 21. Inside the first tank portion 31, the flow velocity of the cooling water becomes the fastest in the vicinity of the opening 401 of the inflow pipe 40. By using the tube 21 as shown in FIG. 3, it becomes more difficult for the cooling water to flow into the tube 21 arranged near the opening 401 of the inflow pipe 40, so that each tube is caused by the position of the inflow pipe 40. It is possible to further alleviate the bias of the flow rate distribution of 21.

<Second Embodiment>
Next, the heat exchanger 10 of the second embodiment will be described. Hereinafter, the differences from the heat exchanger 10 of the first embodiment will be mainly described.
As shown in FIG. 4, in the heat exchanger 10 of the present embodiment, in order to allow the cooling water to flow from the inflow pipe 40 to the first tank portion 31 so as to form a predetermined angle θ with respect to the tube stacking direction X, A drift portion 404 is formed in the middle of the inflow pipe 40. The drift portion 404 is formed so as to be bent in the inflow pipe 40, and is formed so as to partially narrow the flow path cross-sectional area of the inflow pipe 40. With such a drift portion 404, the flow direction of the cooling water flowing inside the inflow pipe 40 can be changed. Specifically, as shown by the arrow D1 in FIG. 4, it is possible to allow the cooling water to flow from the inflow pipe 40 to the first tank portion 31 so as to form a predetermined angle θ with respect to the tube stacking direction X. Even the heat exchanger 10 having a structure like the present embodiment can obtain the same or similar operation and effect as the heat exchanger 10 of the first embodiment.

<Third Embodiment>
Next, the heat exchanger 10 of the third embodiment will be described. Hereinafter, the differences from the heat exchanger 10 of the first embodiment will be mainly described.
As shown in FIG. 5, in the heat exchanger 10 of the present embodiment, in order to allow the cooling water to flow from the inflow pipe 40 to the first tank portion 31 so as to form a predetermined angle θ with respect to the tube stacking direction X, A drift member 60 is provided inside the first tank portion 31. The drift member 60 is composed of a plate-shaped member having a through hole 61 at a position deviated from the axis m1. An inclined surface 62 that is inclined so as to form a predetermined angle with respect to the tube stacking direction X is formed on the inner peripheral surface of the through hole 61. As the cooling water flowing from the inflow pipe 40 into the first tank portion 31 flows through the through hole 61 along the inclined surface 62, as shown by the arrow D1 in FIG. 5, a predetermined angle θ with respect to the tube stacking direction X. It is possible to flow the cooling water from the inflow pipe 40 into the first tank portion 31 so as to form the above.

Even the heat exchanger 10 having a structure like the present embodiment can obtain the same or similar operation and effect as the heat exchanger 10 of the first embodiment.
<Fourth Embodiment>
Next, the heat exchanger 10 of the fourth embodiment will be described. Hereinafter, the differences from the heat exchanger 10 of the first embodiment will be mainly described.

As shown in FIG. 6, in the heat exchanger 10 of the present embodiment, in order to allow the cooling water to flow from the inflow pipe 40 to the first tank portion 31 so as to form a predetermined angle θ with respect to the tube stacking direction X, A drift structure 412 is provided at one end 410 of the side plate 41. As shown in FIG. 7, the drift structure 412 has a structure in which a part of the end portion 410 of the side plate 41 is partially projected. As shown in FIG. 6, the drift structure 412 projects into the first tank portion 31. Therefore, the cooling water flowing from the inflow pipe 40 into the first tank portion 31 is difficult to flow in the portion provided with the drift structure 412, while it is easy to flow in the portion not provided with the drift structure 412. As a result, as shown by the arrow D1 in FIG. 6, it is possible to allow the cooling water to flow from the inflow pipe 40 to the first tank portion 31 so as to form a predetermined angle θ with respect to the tube stacking direction X. ..

Even the heat exchanger 10 having a structure like the present embodiment can obtain the same or similar operation and effect as the heat exchanger 10 of the first embodiment.
<Fifth Embodiment>
Next, the heat exchanger 10 of the fifth embodiment will be described. Hereinafter, the differences from the heat exchanger 10 of the first embodiment will be mainly described.

As shown in FIG. 8, in the heat exchanger 10 of the present embodiment, in order to allow the cooling water to flow from the inflow pipe 40 to the first tank portion 31 so as to form a predetermined angle θ with respect to the tube stacking direction X, A drift structure 313 is provided on the peripheral wall 312 of the first tank portion 31. The drift structure 313 has a structure in which a part of the peripheral wall 312 of the first tank portion 31 is deformed so as to be recessed inward. Due to this drift structure 313, the cooling water flowing from the inflow pipe 40 into the first tank portion 31 becomes difficult to flow in the portion where the drift structure 313 is provided, while it becomes easy to flow in the portion where the drift structure 313 is not provided. .. This makes it possible to allow the cooling water to flow from the inflow pipe 40 into the first tank portion 31 so as to form a predetermined angle θ with respect to the tube stacking direction X.

Even the heat exchanger 10 having a structure like the present embodiment can obtain the same or similar operation and effect as the heat exchanger 10 of the first embodiment.
<Sixth Embodiment>
Next, the heat exchanger 10 of the sixth embodiment will be described. Hereinafter, the differences from the heat exchanger 10 of the first embodiment will be mainly described.

As shown in FIG. 9, in the heat exchanger 10 of the present embodiment, in order to allow the cooling water to flow from the inflow pipe 40 to the first tank portion 31 so as to form a predetermined angle θ with respect to the tube stacking direction X, The inflow pipe 40 is attached to the first tank portion 31 at an angle. Specifically, the inflow pipe 40 is attached to the first tank portion 31 so that its central axis m2 is inclined with respect to the tube stacking direction X. As a result, as shown by the arrow D1 in FIG. 9, the cooling water can flow from the inflow pipe 40 to the first tank portion 31 so as to form a predetermined angle θ with respect to the tube stacking direction X. ..

Even the heat exchanger 10 having a structure like the present embodiment can obtain the same or similar operation and effect as the heat exchanger 10 of the first embodiment.
<7th Embodiment>
Next, the heat exchanger 10 of the seventh embodiment will be described. Hereinafter, the differences from the heat exchanger 10 of the first embodiment will be mainly described.

As shown in FIG. 10, in the heat exchanger 10 of the present embodiment, in order to allow the cooling water to flow from the inflow pipe 40 to the first tank portion 31 so as to form a predetermined angle θ with respect to the tube stacking direction X, The inflow pipe 40 is attached at a position eccentric with respect to the first tank portion 31. That is, the inflow pipe 40 is attached to the first tank portion 31 so that its central axis m2 deviates from the central axis m1 of the first tank portion 31. As a result, as shown by the arrow D1 in FIG. 10, it is possible to allow the cooling water to flow from the inflow pipe 40 to the first tank portion 31 so as to form a predetermined angle θ with respect to the tube stacking direction X. ..

Even the heat exchanger 10 having a structure like the present embodiment can obtain the same or similar operation and effect as the heat exchanger 10 of the first embodiment.
<8th Embodiment>
Next, the heat exchanger 10 of the eighth embodiment will be described. Hereinafter, the differences from the heat exchanger 10 of the first embodiment will be mainly described.

As shown in FIG. 11, in the heat exchanger 10 of the present embodiment, in order to allow the cooling water to flow from the inflow pipe 40 to the first tank portion 31 so as to form a predetermined angle θ with respect to the tube stacking direction X, An inflow pipe 40 is attached to the side surface of the first tank portion 31. Specifically, the inflow pipe 40 is attached to the side surface of the first tank portion 31 located in the tube width direction Y. According to such a structure, the cooling water flowing from the inflow pipe 40 into the first tank portion 31 flows so as to be substantially orthogonal to the tube stacking direction X. That is, the angle θ in FIG. 11 is approximately 90 degrees.

Even the heat exchanger 10 having a structure like the present embodiment can obtain the same or similar operation and effect as the heat exchanger 10 of the first embodiment.
<9th embodiment>
Next, the heat exchanger 10 of the ninth embodiment will be described. Hereinafter, the differences from the heat exchanger 10 of the first embodiment will be mainly described.

As shown in FIG. 12, in the heat exchanger 10 of the present embodiment, in order to allow the cooling water to flow from the inflow pipe 40 to the first tank portion 31 so as to form a predetermined angle θ with respect to the tube stacking direction X, A drift member 70 is provided inside the first tank portion 31. As shown in FIGS. 13 and 14, the drift member 70 is composed of a member formed in a columnar shape about the axis m1. A through hole 71 is formed in the drift member 70 at a position deviated from the central axis m1. As the cooling water flowing through the inflow pipe 40 passes through the through hole 71 of the drift member 70, as shown by the arrow D1 in FIG. 12, the cooling water flows from the inflow pipe 40 so as to form a predetermined angle θ with respect to the tube stacking direction X. It is possible to allow the cooling water to flow into the first tank portion 31.

Even the heat exchanger 10 having a structure like the present embodiment can obtain the same or similar operation and effect as the heat exchanger 10 of the first embodiment.
<Other embodiments>
In addition, each embodiment can also be carried out in the following embodiments.

-In the heat exchanger 10 of each embodiment, any fluid other than cooling water can be adopted as the fluid flowing through the heat exchanger 10.
-The present disclosure is not limited to the above specific examples. Specific examples described above with appropriate design changes by those skilled in the art are also included in the scope of the present disclosure as long as they have the characteristics of the present disclosure. Each element included in each of the above-mentioned specific examples, and their arrangement, conditions, shape, and the like are not limited to those exemplified, and can be appropriately changed. The combinations of the elements included in each of the above-mentioned specific examples can be appropriately changed as long as there is no technical contradiction.

10: Heat exchanger 20: Heat exchange core part 21: Tube 31: First tank part 32: Second tank part 40: Inflow pipe 41: Side plate 43: Discharge pipe 60: Diffusion member 70: Diffusion member 212: Bulk partition 312 : Peripheral wall 313: Diagonal flow structure 402: Inner wall surface 403: Inclined surface 404: Diagonal flow portion 412: Diagonal flow structure

Claims (2)

A heat exchange core portion (20) in which a plurality of tubes (21) through which a fluid flows are laminated and arranged, and a heat exchange core portion (20).
A first tank portion (31) connected to one end of the plurality of the tubes and distributing the fluid to the plurality of the tubes, and a first tank portion (31).
A second tank portion (32) connected to the other ends of the plurality of the tubes and collecting the fluid that has passed through the plurality of the tubes, and a second tank portion (32).
A side plate (41) arranged at both ends of the heat exchange core portion in the tube stacking direction to reinforce the heat exchange core portion is provided.
When the direction in which the plurality of tubes are stacked and arranged is the tube stacking direction,
An inflow pipe (40) for allowing a fluid to flow into the inside of the first tank portion is connected to one end of the first tank portion located in the tube stacking direction.
A discharge pipe (43) for discharging the fluid inside the second tank portion is connected to one end of the second tank portion located on the same side as the inflow pipe in the tube stacking direction.
Both ends of the side plate are connected to the first tank portion and the second tank portion, respectively.
The inflow of the side plate to one end connected to the first tank portion so that the fluid flows from the inflow pipe to the first tank portion at a predetermined angle with respect to the tube stacking direction. A drift structure (412) that changes the flow direction of the fluid flowing into the first tank portion from the pipe is provided.
Heat exchanger. The heat exchanger according to claim 1, wherein the tube is formed with a partition wall (212) that divides the internal flow path into two flow paths.

Images