JP2007218455A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger capable of reducing water-passing resistance and controlling and improving a distribution of flow rate. <P>SOLUTION: This heat exchanger comprises a pair of tanks 110, 120, a core plate 140 fixed to the tanks 110, 120, and a core portion 130 connected with the core plate 140 at its longitudinal end portion and constituted by stacking a plurality of tubes 132 communicated with the tanks 110, 120, and one of the tanks 110 is provided with an inflow port 111 for allowing the fluid to flow in the direction approximately orthogonal to the stacking direction of the tubes 132, and an approximately wedge-shaped first projecting portion 115 formed on a position where the fluid flowing in from the inflow port 111 collides with an inner face of the tank 110 to change the flowing direction so that the fluid flows in the stacking direction of the tubes 132. Thus, the water-passing resistance can be reduced, and the distribution of flow rate can be improved. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a heat exchanger used in a radiator for cooling an engine, for example.

  2. Description of the Related Art Conventionally, a radiator having a structure in which a plurality of tubes are stacked to form a core portion, and a tank is fixed to a core plate to which ends of these tubes are connected is generally known. The radiator tank having such a structure is provided with an inflow port connected to the engine coolant pipe. The cooling water flows in through the inlet in a direction substantially perpendicular to the tank longitudinal direction, flows along the tank longitudinal direction, that is, the stacking direction of the tubes, and flows into each tube.

  However, in the case of the above configuration, the cooling water that has flowed in from the inflow port once collides with the inner surface of the tank, and is branched in the longitudinal direction of the tank, and then flows into each tube. Therefore, there is a problem that water resistance increases due to a collision.

  In addition, since the cooling water that flows in from the inlet is likely to flow into the tube immediately below the inlet, it is difficult for the cooling water to flow into the tube at a position away from the inlet. There is concern about the deterioration of heat dissipation efficiency and the durability due to the generation of thermal stress.

  In particular, in recent years, as part of improving the performance of radiators, the size of the core portion has been increased by reducing the size of the tank in order to effectively utilize the limited installation space. For example, as shown in FIG. 10A to FIG. 10C, as a radiator that achieves such downsizing, the height of the tank 110 is lowered, and a part of the outer periphery of the inflow port 111 is part of the tank 110. Some have a shape protruding outward.

  In other words, a part of the outer periphery of the inflow port 111 is formed so as to protrude outward from the height H of the tank 110 by about h. In the case of such a shape, in particular, there is a problem that the cooling water is less likely to flow into the tube at a position away from the inlet 111 and the flow velocity distribution is more likely to occur.

  Then, the 1st objective of this invention is in view of the said point, and is providing the heat exchanger which can aim at reduction of water flow resistance. A second object of the present invention is to provide a heat exchanger capable of suppressing the flow velocity distribution of the entire heat exchanger and improving the flow velocity distribution.

  In order to achieve the above object, the technical means described in claims 1 to 7 are employed. That is, in the first aspect of the invention, a pair of tanks (110, 120), a core plate (140) fixed to the tanks (110, 120), and a longitudinal end portion of the core plate (140). A core portion (130) in which a plurality of tubes (132) communicating with the inside of the tank (110, 120) are stacked, and one of the tanks (110, 120) is connected to one of the tanks (110). (132) is formed at a portion where the fluid flows in in a direction substantially perpendicular to the stacking direction of (132), and a portion where the fluid flowing from the inlet (111) collides with the inner surface of the tank (110, 120). And a first protrusion (115) that changes the flow direction so that the fluid flows in the stacking direction of the tubes (132).

  According to the present invention, the fluid flowing in from the inflow port (111) can smoothly change the flow direction in the stacking direction of the tube (132) by the first protrusion (115). It is possible to reduce the water flow resistance due to the cooling water flowing into the tank (110) colliding with the inner wall surface of the tank (110). Moreover, the reachability of the flow to the end of the tube (132) in the stacking direction becomes good, and the flow velocity distribution can be suppressed and the flow velocity distribution can be improved.

  The invention according to claim 2 is characterized in that the first protrusion (115) is formed so as to protrude in a substantially wedge shape toward the opening of the inflow port (111). According to the present invention, by forming the first protrusion (115) in a substantially wedge shape, the flow direction can be smoothly changed in the longitudinal direction of the tank (110), so that the water resistance due to the collision can be reduced. The tank (110) can be downsized.

  The invention according to claim 3 is characterized in that the first projecting portion (115) is formed with a substantially triangular convex portion toward the opening of the inflow port (111). According to this invention, since the flow direction can be smoothly changed in the longitudinal direction of the tank (110) by the first projecting portion (115) formed of a substantially triangular convex portion, the water flow resistance due to the collision can be reduced.

  Further, since the flow immediately below the inlet (111) is further suppressed, the reachability of the flow to the longitudinal end of the tank (110) is improved, and the flow velocity distribution can be suppressed and the flow velocity distribution can be improved.

  The invention according to claim 4 is characterized in that the first projecting portion (115) is formed such that a substantially triangular bottom portion extends in a longitudinal direction of the tank (110). According to this invention, since the guide plate (guide vane) is formed in the longitudinal direction, the flow velocity distribution in the entire heat exchanger can be suppressed and the flow velocity distribution can be improved.

  In the invention according to claim 5, the inflow port (111) is integrally provided with the second protrusion (117) for guiding the flow direction before the inflowing fluid collides with the inner surface of the tank (110, 120). It is characterized by being formed.

  According to the present invention, for example, if the second protrusion (117) is formed in a shape that suppresses downward flow, the flow directly below the inflow port (111) can be suppressed. Therefore, the reachability of the flow to the longitudinal end of the tank (110, 120) is good, and the flow rate distribution of the entire heat exchanger can be suppressed and the flow rate distribution can be improved.

  In the invention according to claim 6, the second projecting portion (117) has a shape in which the inflowing fluid can easily flow toward the first projecting portion (115) formed in the portion colliding with the inner surface of the tank (110, 120). It is characterized by being formed. According to this invention, it is possible to reduce the water flow resistance of the inflowing fluid that flows to the first protrusion (115) by the second protrusion (117).

  The invention according to claim 7 is characterized in that the height of the tank (110, 120) in the longitudinal direction of the tube is smaller than the opening diameter of the inlet (111). According to the present invention, the fluid flow velocity distribution can be improved particularly in the heat exchanger having the tank (110) having a shape in which the fluid flow velocity distribution in the tank (110) is likely to be generated.

  In addition, the code | symbol in the bracket | parenthesis of each said means shows a corresponding relationship with the specific means of embodiment mentioned later.

(First embodiment)
Hereinafter, the heat exchanger in 1st Embodiment of this invention is demonstrated based on FIG. 1 thru | or FIG. FIG. 1 is a front view showing a schematic structure of a radiator 100 in which the present invention is applied to a radiator for cooling an engine. FIG. 2 is a perspective view showing a joint structure between a tank 110 and a tube 132 of the radiator 100. It is.

  The radiator 100 according to the present embodiment is an automobile radiator mounted in front of the engine room. As shown in FIG. 1, the radiator 100 is a so-called down flow type in which engine cooling water (hereinafter referred to as cooling water) flowing in the tube 132 of the core portion 130 is directed downward from above in the drawing. The basic configuration includes a core portion 130, an upper tank 110, and a lower tank 120.

  The core unit 130 is a heat exchanging unit that cools the cooling water flowing inside, and includes a fin 131, a tube 132, a side plate 133, and a core plate 140. The fin 131 is formed into a wave shape from a thin strip material, and a slit-like louver (not shown) is provided on the inside.

  Further, the tube 132 is bent from a thin strip material so that the cross section is flat, and the ends thereof are welded. In FIG. 1, the fins 131 and the tubes 132 are alternately stacked in the left-right direction, and the side plate 133 is applied to the outermost side of the left and right outermost fins 131 as a reinforcing member having a substantially U-shaped cross section. I'm trying to get in touch.

  The core plate 140 is formed by flat drawing or the like, is disposed so as to extend in the stacking direction of the tubes 132, and is located at a position corresponding to an end portion in the longitudinal direction of the tube 132 (hereinafter referred to as a tube end portion). A plurality of insertion holes 142 as tube insertion portions are provided. The core portion 130 is formed by inserting the end portion of the tube 132 into the insertion hole 142.

  And each member which comprises the core part 130 consists of aluminum alloy excellent in characteristics, such as an intensity | strength characteristic and corrosion resistance, and the core part 130 is formed by brazing these integrally.

  The upper tank 110 is mechanically connected to the upper core plate 140 in the drawing, and the lower tank 120 is mechanically connected to the lower core plate 140 in the drawing by caulking or the like. The upper tank 110 and the lower tank 120 are formed by molding with resin (for example, polyamide resin).

  The upper tank 110 is integrally formed with an inlet pipe 111 as an inflow port on one side surface, and the lower tank 120 is integrally formed with an outlet pipe 121 on one side surface. The tank structure near the inlet pipe 111 will be described later. Further, the inlet pipe 111 and the outlet pipe 112 are connected to an engine coolant circuit through a rubber hose (not shown).

  By the way, since the upper tank 110 and the lower tank 120 have substantially the same structure, the joint structure between the core plate 140 and the core part 130 will be described below using the upper tank 110 side.

  As shown in FIG. 2, the resin upper tank 110 has a substantially U-shaped cross-section and a box-shaped container body having an opening on the core plate 140 side. The opening side end surface of the upper tank 110 is inserted into a mounting groove 143 formed on the outer peripheral portion of the core plate 140 and having a packing 150 as a seal member mounted therein, and a caulking claw 144 of the core plate 140 is formed. The upper tank 110 is fixed to the outer stepped surface 112 by caulking.

  That is, the upper tank 110 and the core plate 140 form a substantial tank space. The end of the tube 132 is joined to the core plate 140 of the substantial tank space, so that the inside of the tube 132 communicates with the tank space.

  A region inside the mounting groove 143 of the core plate 140 forms a substantial bottom surface 141 on the side of the core 130 formed by the upper tank 110 and the core plate 140. The bottom surface portion 141 is a reference surface portion of the core plate 140, and the side surface of the tank space of the bottom surface portion 141 is a tank inner bottom surface 141a.

  The mounting groove 143 is provided on the outer periphery of the bottom surface 141a, and the pressing surface 143a that presses the packing 150 toward the upper tank 110 when caulking is fixed is formed so as to protrude from the bottom surface 141a toward the center of the core portion 130. Yes.

  Next, the tank structure in the vicinity of the inlet pipe 111, which is a feature of the present invention, will be described with reference to FIGS. FIG. 3 shows a tank structure near the inlet pipe 111, where (a) is a partial plan view of (b), (b) is a partial front view, and (c) is a partial bottom view of (b). FIG. 4 is a cross-sectional view taken along line AA shown in FIG.

  In the upper tank 110 of the present embodiment, as shown in FIGS. 3 and 4, the inlet pipe 111 has cooling water in the longitudinal direction of the upper tank 110, that is, in the direction substantially perpendicular to the weir layer direction of the tube 132. Is formed in a pipe shape so as to flow in, and is integrally formed so that a part of the outer periphery of the inlet pipe 111 protrudes outward of the upper tank 110.

  That is, the inlet pipe 111 into which the cooling water flows in a direction substantially orthogonal to the flow direction of the cooling water flowing in the upper tank 110 is formed. Thereby, the cooling water flowing in from the inlet pipe 111 collides with the inner surface of the upper tank 110 and the flow is divided in the left-right direction.

  Therefore, in the present invention, as shown in FIG. 3C and FIG. 4, the inclined portion 116 and the lower portion of the cooling water flowing from the inlet pipe 111 collide with the inner surface of the upper tank 110. 1 protrusion 115 is formed.

  The inclined portion 116 is a guide plate (guide vane) for smoothly flowing the cooling water flowing in from the inlet pipe 111 to the first protruding portion 115, and the downstream side of the inlet pipe 111 and the first protruding portion 115 described later. Are integrally formed so as to be connected to the apex 115a to be inclined.

  The first protrusion 115 smoothly changes the flow direction of the cooling water flowing in from the inlet pipe 111 in the left-right direction. Specifically, the first protrusion 115 is formed in a shape protruding substantially in a wedge shape toward the opening of the inlet pipe 111. is doing.

  More specifically, the substantially wedge-shaped first protrusion 115 is formed such that a wedge-shaped apex 115a is positioned on, for example, the center of the inlet pipe 111 in the lateral direction, and a slope 115b extending in the left-right direction from the apex 115a. And forming the apex 115a so as to protrude most toward the opening of the inlet pipe 111, and forming the inclined surface 115b extending from the apex 115a gradually in the left-right direction so that the height is gradually reduced. Yes.

  Thereby, the cooling water flowing in from the inlet pipe 111 is diverted in the left-right direction by the apex 115a, and the diverted flow can be smoothly changed in the left-right direction using the slope 115b as a guide plate (guide vane).

  Further, since the inclined portion 116 is formed on the upstream side of the substantially wedge-shaped first protrusion 115, the cooling water flowing from the inlet pipe 111 can be smoothly guided to the first protrusion 115. Therefore, the flow resistance of the water due to the collision can be reduced by the smooth flow of the cooling water. Moreover, according to the tank structure of the above structure, size reduction of the tanks 110 and 120 can be achieved.

  In the present embodiment, the first protrusion 115 is described as being formed in a substantially wedge shape. However, the substantially wedge shape is a mountain shape having a vertex 115a and a slope 115b extending from the vertex 115a, or a mountain shape. It may be.

  According to the heat exchanger according to the first embodiment described above, the inlet pipe 111 is formed so that a part of the outer periphery thereof protrudes to the outside of the upper tank 110, and the first protrusion 115 is formed of the inlet pipe 111. It is formed so as to protrude in a substantially wedge shape toward the opening.

  Thereby, the cooling water flowing in from the inlet pipe 111 is diverted in the left-right direction by the apex 115a of the first projecting portion 115, and the diverted flow uses the slope 115b of the first projecting portion 115 as a guide plate (guide vane) in the left-right direction. The flow direction can be changed smoothly. Therefore, water resistance due to collision can be reduced. Moreover, according to the tank structure of the above structure, size reduction of the tanks 110 and 120 can be achieved.

  In addition, since the inclined portion 116 is formed on the downstream side of the inlet pipe 111 so as to be led to the first projecting portion 115, the water flow resistance due to the collision can be further reduced.

(Second Embodiment)
In the first embodiment described above, the inclined portion 116 and the wedge-shaped first protruding portion 115 are formed in a portion where the cooling water flowing from the inlet pipe 111 of the upper tank 110 collides with the inner surface of the upper tank 110. However, the present invention is not limited to this, and a wedge-shaped first protrusion 115 may be formed.

  Specifically, as shown in FIGS. 5A to 5C, the downstream end of the inlet pipe 111 is connected in an R shape so that the cooling water flowing from the inlet pipe 111 collides with the inner surface of the upper tank 110. A wedge-shaped first protrusion 115 is formed on the entire portion.

  The substantially wedge-shaped first protrusion 115 forms a wedge-shaped apex 115a so as to be located, for example, on the center of the inlet pipe 111 in the lateral direction, and forms a slope 115b extending in the left-right direction from the apex 115a. The apex 115a is formed so as to protrude most toward the opening of the inlet pipe 111, and the inclined surface 115b extending from the apex 115a is formed so as to gradually protrude in the left-right direction so that the height is gradually reduced.

  That is, in this embodiment, the cooling water flowing from the inlet pipe 111 is formed so as to collide with the wedge-shaped first protrusion 115. Thereby, the cooling water flowing in from the inlet pipe 111 is diverted in the left-right direction by the apex 115a, and the diverted flow can be smoothly changed in the left-right direction using the slope 115b as a guide plate (guide vane).

  Therefore, the flow resistance of the water due to the collision can be reduced by the smooth flow of the cooling water. Moreover, according to the tank structure of the above structure, size reduction of the tanks 110 and 120 can be achieved.

(Third embodiment)
In the above embodiment, the first protrusion 115 protruding in a substantially wedge shape toward the opening of the inlet pipe 111 is formed at the portion where the cooling water flowing in from the inlet pipe 111 collides with the inner surface of the upper tank 110. However, the present invention is not limited to this. Instead, the first protrusion 115 made of a substantially triangular convex portion may be formed toward the opening of the inlet pipe 111.

  Specifically, as shown in FIGS. 6A to 6C, the cooling water flowing in from the inlet pipe 111 collides with the inner surface of the upper tank 110, for example, protrudes on the axis of the inlet pipe 111. It is formed so that the vertex 115a of the portion is located, and is formed in a substantially triangular shape having a slope 115b extending in the left-right direction from the vertex 115a.

  And the 1st protrusion part 115 which consists of a substantially triangular convex part is formed so that the bottom face 115c facing the vertex 115a may be located above the opening end of the upper tank 110. By the way, in the radiator which has the upper tank 110 with the long left-right direction, there exists a possibility that flow velocity distribution may generate | occur | produce because the reachability of the flow of the cooling water to a right-and-left end falls.

  Therefore, in the present embodiment, the downward flow that is changed in the left-right direction by the inclined surface 115b is suppressed by the first protrusion 115 that is a substantially triangular convex portion. According to this, since the downward flow can be suppressed by the first projecting portion 115, the reachability of the flow to the longitudinal end of the upper tank 110 becomes good, and the flow velocity distribution can be suppressed and the flow velocity distribution can be improved.

  Further, since the flow direction can be smoothly changed in the longitudinal direction of the upper tank 110 by the first projecting portion 115 formed of a substantially triangular convex portion, the water flow resistance due to the collision can be reduced. Further, the size of the upper tank 110 can be reduced.

(Fourth embodiment)
This embodiment shows a modification of the third embodiment, and is formed so that the bottom of the convex portion extends in the longitudinal direction of the upper tank 110 in the first projecting portion 115 made of a substantially triangular convex portion. is doing. Specifically, as shown in FIGS. 7A to 7C, the bottom portion 115d of the first projecting portion 115 formed of a substantially triangular convex portion is formed to extend in the longitudinal direction.

  The bottom 115d is a guide plate (guide vane) for guiding the flow changed in the left-right direction by the apex 115a and the slope 115b to the end in the longitudinal direction of the upper tank 110. Thereby, the flow velocity distribution in the whole radiator can be suppressed and the flow velocity distribution can be improved.

(Fifth embodiment)
In the present embodiment, the tank structure is configured such that the downward flow to the tube 132 just below the inlet pipe 111 is suppressed and the cooling water can be easily applied to the first protrusion 115 formed at the portion that collides with the inner surface of the upper tank 110. .

  Specifically, as shown in FIG. 8A, first, the cooling water flowing in from the inlet pipe 111 collides with the inner surface of the upper tank 110 and protrudes in a substantially wedge shape toward the opening of the inlet pipe 111. One protrusion 115 is formed.

  And the 2nd protrusion part 117 is formed in the terminal side below the inner surface of the inlet pipe 111 which is the upstream of this 1st protrusion part 115. As shown in FIG. The second projecting portion 117 is a guide portion formed in an inclined shape that gradually protrudes toward the inner surface side from the opening side to the end side of the inlet pipe 111, and the cooling water flowing in from the inlet pipe 111 is slightly transferred to the inner surface of the upper tank 110. It can flow upward.

  Moreover, the external shape of the 2nd protrusion part 117 is formed in the shape shown in FIG.8 (b) or FIG.8 (c). That is, in FIG. 8B, it is formed in a slope shape, and in FIG. 8C, it is formed in a mountain shape or a substantially wedge shape with the apex protruding. In addition, the 2nd protrusion part 117 formed in the mountain shape or substantially wedge shape is formed so that the flow of a cooling water may be changed to the left-right direction similarly to the 1st protrusion part 115 demonstrated in the above embodiment.

  According to the tank structure having the above configuration, the cooling water flowing from the inlet pipe 111 is likely to flow toward the upper side of the first protrusion 115 by the second protrusion 117. The first protrusion 115 makes it easy to flow in the left-right direction. That is, the downward flow to the tube 132 immediately below the inlet pipe 111 is suppressed by the second protrusion 117.

  In addition, since the cooling water easily flows above the first protrusion 115 by the second protrusion 117, most of the cooling water can be easily changed in the left-right direction by the first protrusion 115. Therefore, it is easy for the cooling water to hit the first protrusion 115.

  In other words, since the downward flow can be suppressed by the second projecting portion 117, the reachability of the flow to the longitudinal end of the upper tank 110 becomes good, and the flow velocity distribution of the entire radiator 100 can be suppressed and the flow velocity distribution can be improved. Further, the flow resistance of the cooling water flowing to the first protrusion 115 can be reduced by the second protrusion 117.

  In addition, in this embodiment, although it comprised with the tank structure which combined the 1st protrusion part 115 and the 2nd protrusion part 117 of the shape demonstrated in 2nd Embodiment, it demonstrated not only in this but in the above embodiment. You may make it comprise the tank structure which combined the 1st protrusion part 115 and the 2nd protrusion part 117 of this embodiment.

(Sixth embodiment)
In the present embodiment, the tank structure is formed when the inlet pipe 111 is formed on the end side of the upper tank 110, and the first projecting portion is provided at a portion where the cooling water flowing from the inlet pipe 111 collides with the inner surface of the upper tank 110. 115 and a second protrusion 117 is formed on the lower end of the inner surface of the inlet pipe 111.

  Specifically, the second protrusion 117 when the inlet pipe 111 is formed on the right end side of the upper tank 110 is formed in an inclined shape that gradually protrudes from the opening side to the end side of the inlet pipe 111 toward the inner surface side. As shown in FIG. 9, the second protrusion 117 having a shape inclined in the left direction so as to easily flow in the left direction is formed.

  Although the first protrusion 115 formed at the portion that collides with the inner surface of the upper tank 110 is not shown in the figure, the apex 115a is located on the right side of the opening center of the inlet pipe 111 so that it flows easily in the left direction. It is formed by shifting in the direction.

  In addition, when the formation position of the inlet pipe 111 is on the left end side of the upper tank 110, the left pipe is easy to flow in the right direction with the shape inclined to the lower side so that the left pipe is easy to flow in the left direction. What is necessary is just to form the 2nd protrusion part 117 of the shape where the right direction inclined downward. In other words, the first protrusion 115 and the second protrusion 117 may be formed according to the desired flow direction.

  According to the tank structure having the above-described configuration, the second projecting portion 117 can guide in the desired flow direction, so that the flow reachability to the end in the longitudinal direction of the upper tank 110 is improved, and the flow velocity distribution of the entire radiator 100 is achieved. Suppression and improvement of flow velocity distribution.

(Other embodiments)
In the above embodiment, the inlet pipe 111 formed in the upper tank 110 is formed in the substantially central portion of the upper tank 110, and the apex 115a of the first protrusion 115 is formed on the lateral center line of the inlet pipe 111. However, this is not a limitation.

  For example, when the formation position of the inlet pipe 111 is not formed at a substantially central portion, based on the ratio of the length in the left-right direction of the inlet pipe 111, the top of the first protrusion 115 on the horizontal center line of the inlet pipe 111 115a may be formed with a deviation from 115a.

  In the above-described embodiment, the embodiment applied to the radiator having the resin tank in which the inlet pipe 111 is integrated has been described. However, the heat exchanger in which the aluminum tank is fixed by brazing or the like is also described. The present invention can be applied.

  In the above embodiment, the relationship between the height of the tank 110 and the opening diameter of the inlet pipe 111 has not been described. However, in general, the heat of the shape in which the height of the tank 110 is smaller than the opening diameter of the inlet pipe 111. In the exchanger, the flow rate distribution of the fluid can be improved because the flow rate distribution of the cooling water in the tank 110 is easily generated.

  In the above embodiment, the present invention is applied to the radiator 100. However, the present invention can also be applied to heat exchangers other than the radiator 100, such as an intercooler, an oil cooler, and an EGR gas cooler.

It is a front view showing a schematic structure of radiator 100 in a 1st embodiment of the present invention. It is a fragmentary perspective view which shows the junction part structure of the tank 110 and the tube 132 of the radiator 100 in 1st Embodiment of this invention. (A) which shows the upper tank structure of the inlet pipe 111 vicinity in 1st Embodiment of this invention is a partial top view, (b) is a partial front view, (c) is a partial bottom view. It is AA sectional drawing shown in FIG.3 (b). (A) which shows the upper tank structure of the inlet pipe 111 vicinity in 2nd Embodiment of this invention is a side view, (b) is a partial top view, (c) is a partial back view. (A) which shows the upper tank structure of the inlet pipe 111 vicinity in 3rd Embodiment of this invention is a side view, (b) is a partial top view, (c) is a partial back view. (A) which shows the upper tank structure of the inlet pipe 111 vicinity in 4th Embodiment of this invention is a side view, (b) is a partial top view, (c) is a partial back view. (A) which shows the upper tank structure of the inlet pipe 111 vicinity in 5th Embodiment of this invention is a side view, (b) and (c) are A arrow directional views shown to (a). It is the elements on larger scale which show the upper tank structure of the inlet pipe 111 vicinity in 6th Embodiment of this invention. (A) which shows the upper tank structure of the inlet pipe 111 vicinity in a prior art is a perspective view, (b) is a partial front view, (c) is a side view.

Explanation of symbols

110 ... Upper tank (tank)
111 ... Inlet pipe (inlet)
115 ... 1st protrusion 117 ... 2nd protrusion 120 ... Lower tank (tank)
130 ... Core part 132 ... Tube 140 ... Core plate (tank)

Claims (7)

A pair of tanks (110, 120);
A core plate (140) fixed to the tank (110, 120);
A core portion (130) having a longitudinal end connected to the core plate (140) and a plurality of tubes (132) communicating with the inside of the tank (110, 120);
An inflow port (111) for allowing fluid to flow into one tank (110) of the pair of tanks (110, 120) in a direction substantially perpendicular to the stacking direction of the tubes (132);
A first protrusion (which is formed in a portion where the fluid flowing in from the inlet (111) collides with the inner surface of the tank (110, 120) and changes the flow direction so that the fluid flows in the stacking direction of the tubes (132) ( 115).   The heat exchanger according to claim 1, wherein the first protrusion (115) is formed so as to protrude in a substantially wedge shape toward the opening of the inflow port (111).   The heat exchanger according to claim 1, wherein the first protrusion (115) is formed with a substantially triangular convex portion toward the opening of the inflow port (111).   The heat exchanger according to claim 3, wherein the first protrusion (115) is formed so that the substantially triangular bottom extends in a longitudinal direction of the tank (110).   The inflow port (111) is integrally formed with a second protrusion (117) for guiding the flow direction before the inflowing fluid collides with the inner surface of the tank (110, 120). The heat exchanger according to any one of claims 1 to 5.   The second protrusion (117) is formed in a shape that allows the inflowing fluid to easily flow toward the first protrusion (115) formed at a portion that collides with the inner surface of the tank (110, 120). The heat exchanger according to claim 5, wherein   The heat exchanger according to any one of claims 1 to 6, wherein a height of the tank (110, 120) in a longitudinal direction of the tank (110, 120) is smaller than an opening diameter of the inlet (111).

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