JP2020112322A - Heat exchanger - Google Patents

Abstract

To provide a heat exchanger capable of reducing noise while suppressing biased flow rate distribution in a plurality of tubes.SOLUTION: A heat exchanger includes a heat exchange core part and a first tank part 31. In the heat exchange core part, a plurality of tubes 21 in which fluid flows are disposed in a laminated manner. The first tank part 31 is connected to one ends of the plurality of tubes 21 to distribute cooling water to the plurality of tubes 21. An inflow pipe 40 for causing the cooling water to flow into the first tank part 31 is connected to one end 310 of the first tank part 31 located in the tube laminating direction X. The cooling water flows in from the inflow pipe 40 to the first tank part 31 so as to form a predetermined angle θ with respect to the tube laminating direction X.SELECTED DRAWING: Figure 2

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 stack, 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 a fluid to flow into the inlet tank. Of both ends of the outlet tank in the tube stacking direction, a discharge pipe for discharging the fluid in the outlet tank is provided at the end on the same side as the inflow port.

By the way, in the heat exchanger having such a structure, the fluid tends to flow into the tube arranged near the inflow pipe, while the fluid tends to hardly flow into the tube arranged apart 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, in the heat exchanger described in Patent Document 1 below, a plate-shaped member is provided inside the inlet tank. Among the plurality of tubes, the plate-shaped member partially closes an opening at one end of a predetermined number of tubes arranged on the same side as the inflow pipe and the discharge pipe in the tube stacking direction. The opening area at one end is reduced. As a result, it becomes difficult for the fluid to flow into the 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 by the plate-like member as in the heat exchanger described in Patent Document 1, when the fluid flows into the tube from the one end of the tube, Since the fluid collides with the plate member, the flow of the fluid in the tube is likely to be disturbed. Disturbances in the flow of fluid in the tube can result in noise.

The present disclosure has been made in view of such actual circumstances, and an object thereof is to provide a heat exchanger capable of reducing noise while suppressing deviation in flow rate distribution in a plurality of tubes.

A heat exchanger that solves the above problem includes a heat exchange core portion (20), a first tank portion (31), and a second tank portion (32). A plurality of tubes (21) through which fluid flows are stacked and arranged in the heat exchange core part. The first tank portion is connected to one end of the plurality of tubes and distributes the fluid to the plurality of tubes. The second tank unit is connected to the other ends of the plurality of tubes and collects the fluid that has passed through the plurality of tubes. When the direction in which a 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 part is provided at one end of the first tank part located in the tube stacking direction. ) Is connected. A discharge pipe (43) for discharging the fluid inside the second tank part is connected to one end of the second tank part located on the same side as the inflow pipe in the tube stacking direction. The fluid flows from the inflow pipe into the first tank portion at a predetermined angle with respect to the tube stacking direction.

According to this configuration, when the fluid flows from the inflow pipe into the first tank portion, the fluid flows so as to form a predetermined angle with respect to the tube stacking direction. Therefore, at one end of the first tank portion, the fluid flows in the predetermined direction. The velocity of the fluid flowing through the region along the line increases. As a result, the velocity distribution of the fluid flowing through the one end of the first tank portion becomes uneven. Due to this bias in the velocity distribution of the fluid, the pressure loss when the fluid flows into the tube increases 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 the one end of the first tank portion. By intentionally biasing the flow rate distribution of each tube in this way, it is possible to cancel the bias of the flow rate distribution of the tubes due to the position of the inflow pipe, thus suppressing the bias of the flow rate distribution in the plurality of tubes. be able to. Further, according to the above configuration, since it is not necessary to close one end of the tube, it is difficult for the flow of fluid in the tube to be disturbed. Therefore, noise can be reduced.

The above-mentioned means and the reference numerals in parentheses in the claims are an example 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 uneven distribution of flow rates 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 sectional view showing a sectional structure taken along line II-II of FIG. FIG. 3 is a cross-sectional view showing the cross-sectional structure of the tube of the modified example of the first embodiment. FIG. 4 is a sectional view showing the sectional structure of the heat exchanger of the second embodiment. FIG. 5: is sectional drawing which shows the cross-section of the heat exchanger of 3rd Embodiment. FIG. 6 is a sectional view showing the sectional structure of the heat exchanger of the fourth embodiment. FIG. 7: is a perspective view which shows the perspective structure of the edge part of the side plate of 4th Embodiment. FIG. 8: is sectional drawing which shows the cross-section of the heat exchanger of 5th Embodiment. FIG. 9: is sectional drawing which shows the cross-section of the heat exchanger of 6th Embodiment. FIG. 10: is sectional drawing which shows the cross-section of the heat exchanger of 7th Embodiment. FIG. 11: is sectional drawing which shows the cross-section of the heat exchanger of 8th Embodiment. FIG. 12: is sectional drawing which shows the cross-section of the heat exchanger of 9th Embodiment. FIG. 13: is sectional drawing which shows the cross-section of the inflow pipe of 9th Embodiment. FIG. 14 is a perspective view showing a perspective structure of a drift member according to 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 constituent elements in each drawing are denoted by the same reference numerals as much as possible, and redundant description will be 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 vehicle interior by blowing heated or cooled conditioned air into the vehicle interior. The heat exchanger 10 is arranged in an air conditioning duct through which conditioned air flows. Inside the heat exchanger 10, engine cooling water is circulated. 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 inside the air conditioning duct. The conditioned air heated by the heat exchanger 10 is blown into the vehicle compartment through the air conditioning duct to heat the vehicle compartment. 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 and 32, and side plates 41 and 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 includes a plurality of tubes 21 arranged in a stack at a predetermined interval in the X-axis direction in the figure, and a plurality of fins 22 arranged in a gap between adjacent tubes 21. Have In FIG. 1, only a part of the plurality of fins 22 is shown. Below, 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 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. Below, the Z-axis direction is also referred to as “tube longitudinal direction Z”. Further, one of the tube longitudinal directions Z is referred to as "Z1 direction", and the other direction is referred to as Z2 direction. Further, a 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 fins 22 are so-called corrugated fins formed by bending a thin and long metal plate into a wavy shape. The bent portion of the fin 22 is fixed to the outer peripheral surface of the adjacent tubes 21 and 21 by brazing. The fins 22 are provided to increase the heat transfer area of the tubes 21 and thereby increase the heat exchange efficiency between the cooling water and the air.

The tank portions 31 and 32 are cylindrical members formed so as to extend in the tube stacking direction X. As shown in FIG. 2, inside the first tank portion 31, an internal passage W20 through which cooling water flows is formed. One end portions 210 of the plurality of tubes 21 in the Z2 direction are connected to the first tank portion 31. One end portions 210 of the plurality of tubes 21 are arranged so as to penetrate the peripheral wall 312 of the first tank portion 31 and extend to the internal flow passage W20 of the first tank portion 31. Similarly, inside the second tank portion, an internal flow path through which cooling water flows is formed. 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. The inflow port 33 is provided at the end portion 310 of the first tank portion 31 in the X2 direction. The inflow port 33 is formed in a tubular shape. As shown in FIG. 2, the end portion 330 of the inflow port 33 in the X1 direction is joined 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 that of the first tank portion 31.

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

An inclined surface 403 is formed on the inner wall surface 402 of the opening portion 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. The respective end portions 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, 42 are provided to reinforce the heat exchange core section 20.

Next, an operation example of the heat exchanger 10 of this embodiment will be described.
In the heat exchanger 10, the single-phase cooling water flows into 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 from the one end portion 210 of each tube 21 into the internal flow path W10 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 passage W10 of each tube 21 and the air flowing between the adjacent tubes 21 and 21, whereby the heat of the cooling water is converted into 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. The flow of the cooling water from the opening 401 of the inflow pipe 40 in the direction indicated by the arrow D1 increases the speed of the cooling water flowing in the region A1 along the arrow D1 at the end portion 310 of the first tank portion 31. As a result, the velocity distribution of the cooling water flowing through the end portion 310 of the first tank portion 31 becomes uneven in the tube width direction Y. Due to this bias in the velocity 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 velocity 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 the structure as shown in FIG. 1, the cooling water flowing from the inflow pipe 40 into the first tank portion 31 is arranged near the end portion 310 of the first tank portion 31. While it is easy to distribute to the tube 21, it becomes 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 respect, in the heat exchanger 10 of the present embodiment, as shown in FIG. 2, it is 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, The flow rate distribution of the plurality of tubes 21 can be intentionally biased. As a result, the deviation of the flow distribution of the tubes 21 due to the position of the inflow pipe 40 can be offset, and as a result, the deviation of the flow distribution of the plurality of tubes 21 can be suppressed. Further, in the heat exchanger 10 of the present embodiment, the one end portion 210 of the tube 21 is not closed, and therefore, as compared with the structure in which one end portion of the tube is closed like the conventional heat exchanger, the inside of the tube 21 is Disturbance does not easily occur in the flow of cooling water. Therefore, it is possible to reduce noise.

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

(Modification)
Next, a modified example of the heat exchanger 10 of the first embodiment will be described.
In the heat exchanger 10 of this modification, a so-called B-type 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 that partitions the internal flow passage W10 into two flow passages 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 each of the flow paths W11 and W12 of the tube 21 becomes larger than that of the tube having no partition wall 212. Therefore, as the flow velocity of the cooling water flowing through the inside of the first tank portion 31 becomes faster, it becomes more difficult for the cooling water to flow into the flow passages W11 and W12 of each tube 21. Inside the first tank portion 31, the flow velocity of the cooling water is highest near 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, and thus each tube caused by the position of the inflow pipe 40. It is possible to further alleviate the bias in the flow distribution of 21.

<Second Embodiment>
Next, the heat exchanger 10 of the second embodiment will be described. Hereinafter, 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 at 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 uneven flow portion 404 is formed so as to be bent in the inflow pipe 40, and includes a portion formed to partially narrow the flow passage 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 an arrow D1 in FIG. 4, it becomes possible to flow the cooling water from the inflow pipe 40 into the first tank portion 31 at a predetermined angle θ with respect to the tube stacking direction X. Even with the heat exchanger 10 having the structure of this embodiment, the same or similar action and effect as the heat exchanger 10 of the first embodiment can be obtained.

<Third Embodiment>
Next, the heat exchanger 10 of the third embodiment will be described. Hereinafter, 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 into the first tank portion 31 at a predetermined angle θ with respect to the tube stacking direction X, The drift member 60 is provided inside the first tank portion 31. The drift member 60 is a plate-shaped member having a through hole 61 at a position displaced from the axis m1. On the inner peripheral surface of the through hole 61, an inclined surface 62 that is inclined so as to form a predetermined angle with respect to the tube stacking direction X is formed. 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 an arrow D1 in FIG. It is possible to flow the cooling water from the inflow pipe 40 into the first tank portion 31 so that

Even with the heat exchanger 10 having the structure of this embodiment, the same or similar action and effect as those of the heat exchanger 10 of the first embodiment can be obtained.
<Fourth Embodiment>
Next, the heat exchanger 10 of the fourth embodiment will be described. Hereinafter, 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 into the first tank portion 31 at a predetermined angle θ with respect to the tube stacking direction X, A drift structure 412 is provided at one end portion 410 of the side plate 41. As shown in FIG. 7, the drift structure 412 is formed by partially projecting a part of the end portion 410 of the side plate 41. 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 becomes difficult to flow in the portion where the non-uniform flow structure 412 is provided, but becomes easy to flow in the portion where the non-uniform flow structure 412 is not provided. As a result, as shown by the arrow D1 in FIG. 6, it is possible to flow the cooling water from the inflow pipe 40 into the first tank portion 31 at a predetermined angle θ with respect to the tube stacking direction X. ..

Even with the heat exchanger 10 having the structure of this embodiment, the same or similar action and effect as those of the heat exchanger 10 of the first embodiment can be obtained.
<Fifth Embodiment>
Next, the heat exchanger 10 of 5th Embodiment is demonstrated. Hereinafter, 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 into the first tank portion 31 at 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 non-uniform flow 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 non-uniform flow 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 non-uniform flow structure 313 is provided, and becomes easy to flow in the part where the non-uniform flow structure 313 is not provided. .. Thereby, it is possible to flow the cooling water 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 with the heat exchanger 10 having the structure of this embodiment, the same or similar action and effect as those of the heat exchanger 10 of the first embodiment can be obtained.
<Sixth Embodiment>
Next, the heat exchanger 10 of the sixth embodiment will be described. Hereinafter, 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 make the cooling water flow from the inflow pipe 40 into the first tank portion 31 at a predetermined angle θ with respect to the tube stacking direction X, The inflow pipe 40 is inclined and attached to the first tank portion 31. 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, it is possible to flow the cooling water from the inflow pipe 40 into the first tank portion 31 at a predetermined angle θ with respect to the tube stacking direction X. ..

Even with the heat exchanger 10 having the structure of this embodiment, the same or similar action and effect as those of the heat exchanger 10 of the first embodiment can be obtained.
<Seventh Embodiment>
Next, the heat exchanger 10 of the seventh embodiment will be described. Hereinafter, 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 into the first tank portion 31 at 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 eccentric position. That is, the inflow pipe 40 is attached to the first tank portion 31 such that the central axis m2 thereof 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 flow the cooling water from the inflow pipe 40 into the first tank portion 31 at a predetermined angle θ with respect to the tube stacking direction X. ..

Even with the heat exchanger 10 having the structure of this embodiment, the same or similar action and effect as those of the heat exchanger 10 of the first embodiment can be obtained.
<Eighth Embodiment>
Next, the heat exchanger 10 of the eighth embodiment will be described. Hereinafter, 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 into the first tank portion 31 at a predetermined angle θ with respect to the tube stacking direction X, The 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 with the heat exchanger 10 having the structure of this embodiment, the same or similar action and effect as those of the heat exchanger 10 of the first embodiment can be obtained.
<Ninth Embodiment>
Next, the heat exchanger 10 of the ninth embodiment will be described. Hereinafter, 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 into the first tank portion 31 at a predetermined angle θ with respect to the tube stacking direction X, The drift member 70 is provided inside the first tank portion 31. As shown in FIGS. 13 and 14, the drift member 70 is a member formed in a cylindrical shape around the axis m1. The drift member 70 has a through hole 71 formed at a position displaced 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, the inflow pipe 40 forms a predetermined angle θ with respect to the tube stacking direction X, as indicated by an arrow D1 in FIG. It is possible to allow the cooling water to flow into the first tank portion 31.

Even with the heat exchanger 10 having the structure of this embodiment, the same or similar action and effect as those of the heat exchanger 10 of the first embodiment can be obtained.
<Other Embodiments>
In addition, each embodiment can also be implemented in the following forms.

-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. A person skilled in the art appropriately modified the above-described specific examples is also included in the scope of the present disclosure as long as the features of the present disclosure are provided. Each element included in each of the above-described specific examples, and the arrangement, conditions, shape, and the like thereof are not limited to those illustrated, and can be appropriately changed. The respective elements included in the above-described specific examples can be appropriately combined 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: drift member 70: drift member 212: partition wall 312 : Peripheral wall 313: non-uniform flow structure 402: inner wall surface 403: inclined surface 404: non-uniform flow portion 412: non-uniform flow structure

Claims (11)

A heat exchange core part (20) in which a plurality of tubes (21) through which fluid flows are stacked and arranged;
A first tank portion (31) connected to one end of the plurality of tubes and distributing a fluid to the plurality of tubes;
A second tank part (32), which is connected to the other ends of the plurality of tubes and collects the fluid that has passed through the plurality of tubes.
When the tube stacking direction is a direction in which the plurality of tubes are stacked and arranged,
An inflow pipe (40) for allowing a fluid to flow into the first tank unit is connected to one end of the first tank unit located in the tube stacking direction,
A discharge pipe (43) for discharging the fluid inside the second tank part is connected to one end of the second tank part located on the same side as the inflow pipe in the tube stacking direction,
A heat exchanger in which a fluid flows from the inflow pipe into the first tank portion at a predetermined angle with respect to the tube stacking direction. On the inner wall surface (402) of the opening portion of the inflow pipe that opens to the inside of the first tank portion, fluid from the inflow pipe to the first tank portion is formed at a predetermined angle with respect to the tube stacking direction. The heat exchanger according to claim 1, wherein an inclined surface (403) that is inclined with respect to the tube stacking direction is formed so as to flow in. A biased flow that changes the flow direction of the fluid flowing in the inflow pipe so that the fluid flows from the inflow pipe into the first tank portion at a predetermined angle with respect to the tube stacking direction. The heat exchanger according to claim 1, wherein a part (404) is formed. Inside the first tank portion, the fluid flows from the inflow pipe into the first tank portion such that a fluid flows from the inflow pipe into the first tank portion at a predetermined angle with respect to the tube stacking direction. The heat exchanger according to claim 1, further comprising a drift member (60) for changing a flow direction of the generated fluid. Further comprising side plates (41) arranged at both ends of the heat exchange core portion in the tube stacking direction to reinforce the heat exchange core portion,
Both end portions of the side plate are respectively connected to the first tank portion and the second tank portion,
The one end of the side plate, which is connected to the first tank part, is made to flow into the first tank part from the inflow pipe at a predetermined angle with respect to the tube stacking direction. The heat exchanger according to claim 1, further comprising a biased flow structure (412) for changing a flow direction of the fluid flowing from the pipe into the first tank portion. A fluid flowing inside the inflow pipe is formed on the peripheral wall (312) of the first tank portion so that the fluid flows from the inflow pipe into the first tank portion at a predetermined angle with respect to the tube stacking direction. The heat exchanger according to claim 1, further comprising a drift structure (313) that changes a flow direction of the heat exchanger. The inflow pipe may have a central axis inclined with respect to the tube stacking direction so that a fluid may flow into the first tank portion from the inflow pipe at a predetermined angle with respect to the tube stacking direction. The heat exchanger according to claim 1, which is attached to the first tank portion. A central axis of the inflow pipe is displaced from a central axis of the first tank part so that the fluid flows from the inflow pipe into the first tank part at a predetermined angle with respect to the tube stacking direction. The heat exchanger according to claim 1, which is attached to the first tank portion. When the tube extending direction is the tube longitudinal direction, and the tube width direction is a direction orthogonal to both the tube stacking direction and the tube longitudinal direction,
The inflow pipe is attached to a side surface of the first tank portion positioned in the tube width direction so that the fluid flows from the inflow pipe into the first tank portion at a predetermined angle with respect to the tube stacking direction. The heat exchanger according to claim 1. The flow direction of the fluid flowing inside the inflow pipe is changed so that the fluid may flow from the inflow pipe into the first tank portion at a predetermined angle with respect to the tube stacking direction. The heat exchanger according to claim 1, further comprising a biasing member (70) for causing the flow to flow. The heat exchanger according to any one of claims 1 to 10, wherein a partition wall (212) for partitioning the internal flow passage into two flow passages is formed in the tube.

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