HEAT EXCHANGER

FIELD

The present invention relates to a multi-flow type heat exchanger.

BACKGROUND

Conventionally, as a multi-flow type heat exchanger, a laminated heat exchanger (evaporator), in which a plurality of core bodies (flat tubes) are laminated, has been known (for example, see Patent Literature 1). In this heat exchanger, two tanks are provided on the windward side and the leeward side on the upper side, and two tanks are provided on the windward side and the leeward side on the lower side. In the heat exchanger, both ends of the core bodies in a lamination direction are closed by an end plate. On one end of the end plate, a flow path has been formed, in which the flow path communicates the tanks on the windward side and the leeward side positioned on the upper side.

CITATION LIST
Patent Literature

Patent Literature 1: Japanese Laid-open Patent Publication No. 09-170851

SUMMARY
Technical Problem

In the heat exchanger disclosed in Patent Literature 1, a refrigerant, flowing in the tank, passes through the flow path formed on the end plate from one tank on the upper side, and flows into the other tank on the upper side. At this time, pressure of the flowing refrigerant is added to a plate surface of the end plate in a direction perpendicular to the plate surface. When the pressure is added to the end plate, the end plate may be deformed. Therefore, it is desirable to enhance the rigidity of the end plate. Here, increasing the thickness of the end plate or providing a reinforcing rib on the end plate is considered to enhance the rigidity of the end plate.

However, when the thickness of the end plate is increased, the weight of the heat exchanger is increased and the cost may also be increased by the increased thickness of the end plate. In addition, when the reinforcing rib is provided on the end plate, the structure becomes complicated. As a result, a part in which stress easily is concentrated, is formed. Therefore, it is difficult to suppress deformation of the end plate, and the cost may be increased since the structure becomes complicated.

It is an object of the present invention to provide a heat exchanger capable of suppressing pressure deformation with a simple configuration.

Solution to Problem

According to an aspect of the present invention, a heat exchanger includes: a plurality of flat tubes to be laminated; a plurality of fins provided between the adjacent flat tubes; a first tank communicating with a first refrigerant flow path formed inside the flat tube, provided on one side in a longitudinal direction of the flat tube, and provided over a lamination direction of the plurality of flat tubes; a second tank communicating with a second refrigerant flow path formed inside the flat tube, provided on one side in the longitudinal direction of the flat tube, and provided over the lamination direction and adjacent to the first tank; and a communication member including a wall body which forms a communication flow path to communicate the first tank with the second tank. When a direction which is perpendicular to the lamination direction and in which the first tank and the second tank are adjacent to each other is set to be a width direction, and a direction which is perpendicular to the width direction and the lamination direction is set to be a height direction, an outer shape of the wall body of the communication flow path, seen from the lamination direction, is formed to be long in the width direction compared with in the height direction and the communication flow path includes a throttle portion formed on the center in the width direction, an outer wall surface of the wall body in the throttle portion has a curved surface formed in a protruded shape inside the communication flow path with a predetermined radius of curvature R. When the length, in which an outer dimension in the height direction is the maximum, of the communication flow path is set to be H, and the length, in which an outer dimension in the width direction is the maximum, of the communication flow path is set to be W, the radius of curvature R of the throttle portion is R≧0.2 H, the length L, in which an outer dimension in the height direction is the minimum, of the throttle portion of the communication flow path is L≦0.9 H, and a part of the length H, in which the outer dimension in the height direction is the maximum, is provided in a position in the width direction outside by ¼ W or more from a part of the communication flow path being the length L.

According to this configuration, the pressure deformation of a communication member can be suppressed, by providing a throttle portion in a communication flow path and making the shape of the communication flow path as a predetermined shape. Here, only providing the throttle portion may cause concentration of stress at the throttle portion, and the communication member may be deformed by pressure. Therefore, a radius of curvature R of the throttle portion in the communication flow path is made R≧0.2 H, so that the gradient of the throttle portion becomes gentle and the concentration of the stress can be suppressed. In addition, the length L of the throttle portion is made L≦0.9 H, so that pressure receiving area can be reduced and the rigidity can be enhanced. Moreover, a part of the length H, in which an outer dimension in a height direction is the maximum, is provided in a position in a width direction outside by ¼ W or more from a part of the length L of the throttle portion. As a result, an opening of a first tank communicating with the communication flow path and an opening of a second tank communicating with the communication flow path do not overlap. Therefore, a pressure receiving surface of the communication flow path from the first tank and a pressure receiving surface of the communication flow path from the second tank do not overlap. Therefore, pressure increase by overlapping of the pressure receiving surfaces can be suppressed.

Advantageously, in the heat exchanger, when a line, passing through the part of the length H, in which the outer dimension in the height direction is the maximum, is set to be an axis line, an outer shape of a virtual oval, which is obtained by developing the outer part in the width direction from the axis line line-symmetrically around the axis line, is formed to be short in the width direction compared with in the height direction.

According to this configuration, the outer shape of a virtual oval can be formed to be short in a width direction compared with in the height direction. Therefore, the communication flow path can be made short in the width direction and the configuration of the heat exchanger itself can be made compact.

Advantageously, in the heat exchanger, the communication flow path is 0.5<W/H<1.0.

According to this configuration, the communication flow path can be long in the width direction compared with in the height direction. Therefore, a first lower tank and a second tank can be suitably connected to the communication flow path, without overlapping the first tank and the second tank adjacent to each other in the width direction.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a schematic configuration view of a heat exchanger according to the present embodiment.

FIG. 2 is a perspective view of surroundings of an end plate of the heat exchanger.

FIG. 3 is a sectional perspective view of surroundings of the end plate of the heat exchanger cut at a surface perpendicular to a width direction.

FIG. 4 is a partial sectional view of surroundings of the end plate of the heat exchanger cut at the surface perpendicular to the width direction.

FIG. 5 is a sectional view of a communication flow path cut at a surface perpendicular to a lamination direction.

DESCRIPTION OF EMBODIMENTS

Hereinafter, an embodiment according to the present invention will be described in detail with reference to the drawings. The present invention is not limited to this embodiment. In addition, components in the following embodiment include a component, which may be easily replaced by those skilled in the art, or the substantially same component.

Embodiment

FIG. 1 is a schematic configuration view of a heat exchanger according to the present embodiment. FIG. 2 is a perspective view of surroundings of an end plate of the heat exchanger. FIG. 3 is a sectional perspective view of surroundings of the end plate of the heat exchanger cut at a surface perpendicular to a width direction. FIG. 4 is a partial sectional view of surroundings of the end plate of the heat exchanger cut at the surface perpendicular to the width direction. FIG. 5 is a sectional view of a communication flow path cut at a surface perpendicular to a lamination direction. FIGS. 2 to 4 are figures in which the vertical direction (longitudinal direction) in FIG. 1 is reversed.

A heat exchanger 1 of the present embodiment is a multi-flow type laminated heat exchanger, and is used, for example, as an evaporator of an air conditioner mounted on an automobile. The heat exchanger 1 of the present embodiment can be applied to any of multi-flow type laminated heat exchangers, and is not particularly limited.

As illustrated in FIGS. 1 to 4, the heat exchanger 1 of the present embodiment includes a plurality of flat tubes 2, a plurality of corrugated fins 3 (see FIG. 4), and a pair of end plates 4. The plurality of flat tubes 2 is laminated in the lamination direction. The plurality of corrugated fins 3 is provided between flat tubes 2 adjacent to each other in the lamination direction. The pair of the end plates 4 is provided at both sides in the lamination direction. Then, the plurality of laminated flat tubes 2, the plurality of corrugated fins 3, and the pair of end plates 4 are integrally joined by brazing.

The flat tube 2 is formed to be extended in the longitudinal direction by joining a pair of molded plates formed by press molding. The flat tube 2 has a flat-shaped cross-section cut at a surface perpendicular to the longitudinal direction, and is laminated in the direction perpendicular to a flat surface. A first upper opening 11a and a second upper opening 12a are formed through the flat tube 2 in the lamination direction in one end (upper end) in the longitudinal direction. A first lower opening 21a and a second lower opening 22a are formed through the flat tube 2 in the lamination direction in the other end (lower end) in the longitudinal direction. The first upper opening 11a and the second upper opening 12a are provided side by side in the width direction, which is perpendicular to the longitudinal direction and the lamination direction. Similarly, the first lower opening 21a and the second lower opening 22a are provided side by side in the width direction.

The plurality of flat tubes 2 is laminated in the lamination direction, so that pluralities of first upper openings 11a and second upper openings 12a are coupled in the lamination direction. The plurality of first upper openings 11a coupled in the lamination direction functions as a first upper tank 11. Similarly, the plurality of second upper openings 12a coupled in the lamination direction functions as a second upper tank 12. In other words, the first upper opening 11a and the second upper opening 12a respectively becomes a part of the first upper tank 11 and the second upper tank 12. Therefore, each of the first upper tank 11 and the second upper tank 12 is formed to be extended in the lamination direction, at the end of one side in the longitudinal direction of the plurality of laminated flat tubes 2, adjacently in parallel in the width direction. At this time, air A flowing in the heat exchanger 1 flows from the upstream side toward the downstream side in the width direction. Therefore, the first upper tank 11 is provided on the downstream side in the width direction and the second upper tank 12 is provided on the upstream side in the width direction.

As illustrated in FIG. 2, the plurality of flat tubes 2 is laminated in the lamination direction, so that pluralities of first lower openings 21a and second lower openings 22a are coupled in the lamination direction as with the first upper opening 11a and the second upper opening 12a. The plurality of first lower openings 21a coupled in the lamination direction functions as a first lower tank 21. Similarly, the plurality of second lower openings 22a coupled in the lamination direction functions as a second lower tank 22. In other words, the first lower opening 21a and the second lower opening 22a respectively becomes a part of the first lower tank 21 and the second lower tank 22. Therefore, each of the first lower tank 21 and the second lower tank 22 is formed to be extended in the lamination direction, at the end of the other side in the longitudinal direction of the plurality of laminated flat tubes 2, adjacently in parallel in the width direction. The first lower tank 21 is provided on the downstream side in the width direction and the second lower tank 22 is provided on the upstream side in the width direction.

Although illustration is omitted, a first refrigerant flow path and a second refrigerant flow path are formed inside the flat tube 2. The first refrigerant flow path is a flow path which communicates the first upper tank 11 (first upper opening 11a) with the first lower tank 21 (first lower opening 21a). The second refrigerant flow path is a flow path which communicates the second upper tank 12 (second upper opening 12a) with the second lower tank 22 (second lower opening 22a).

As illustrated in FIG. 4, the corrugated fin 3 is a corrugated plate with a waveform of transverse waves toward the longitudinal direction, and mountain parts and valley parts are formed to be extended in the width direction. Thus, the air A flowing in the width direction of the heat exchanger 1 is cooled down by passing through the corrugated fin 3.

As illustrated in FIG. 1, the pair of end plates 4 blocks the end in the lamination direction of the first upper tank 11, the second upper tank 12, the first lower tank 21, and the second lower tank 22, communicates the first upper tank 11 with the second upper tank 12 adjacent to each other, and communicates the first lower tank 21 with the second lower tank 22 adjacent to each other.

The end plate 4 is formed to be extended in the longitudinal direction by joining a pair of molded plates formed by press molding as with the flat tube 2. A refrigerant inlet (Rin), from which a refrigerant flows into the heat exchanger 1, and a refrigerant outlet (Rout), out of which the refrigerant flows from the heat exchanger 1, are formed at one end (upper end) in the longitudinal direction at one end plate 4 of the pair of end plates 4. The refrigerant inlet (Rin) is connected to the first upper tank 11 and the refrigerant outlet (Rout) is connected to the second upper tank 12. In addition, a communication flow path 31, which communicates the end of the first lower tank 21 with the end of the second lower tank 22, is formed at the other end (lower end) in the longitudinal direction at the other end plate 4 of the pair of end plates 4.

In addition, a partition part 18 is installed in the intermediate part in the lamination direction of the first lower tank 21. Similarly, a partition part 19 is installed in the intermediate part in the lamination direction of the second upper tank 12.

As illustrated in FIG. 1, when the refrigerant flows from outside into the heat exchanger 1 with the above configuration, the refrigerant flows into one end in the lamination direction of the first upper tank 11 through the refrigerant inlet (Rin). The refrigerant, which has flowed into one end of the first upper tank 11, flows in the first refrigerant flow path in the flat tube 2 and flows into the first lower tank 21, on one end side (right side in FIG. 1) of the heat exchanger 1 relative to the partition part 18. Since the first lower tank 21 is partitioned by the partition part 18, the refrigerant, which has flowed in the first lower tank 21, flows in the first refrigerant flow path in the flat tube 2 again and flows into the first upper tank 11. Then, the refrigerant, which has flowed into the first upper tank 11, flows into the first upper tank 11 on the other end side (left in FIG. 1) of the heat exchanger 1 relative to the partition part 18.

The refrigerant, which has flowed into the first upper tank 11 on the other side, flows in the first refrigerant flow path in the flat tube 2 and flows into the first lower tank 21. The refrigerant, which has flowed into the first lower tank 21, flows toward the other end (left in FIG. 1) in the lamination direction of the first lower tank 21. The refrigerant, which has flowed into the other end of the first lower tank 21, flows into the other end in the lamination direction of the second lower tank 22 through the communication flow path 31.

The refrigerant, which has flowed into the other end of the second lower tank 22, flows in the second refrigerant flow path in the flat tube 2 and flows into the second upper tank 12, on the other end side of the heat exchanger 1 relative to the partition part 19. Since the second upper tank 12 is partitioned by the partition part 19, the refrigerant, which has flowed in second upper tank 12, flows in the second refrigerant flow path in the flat tube 2 again, and flows into the second lower tank 22. Then, the refrigerant, which has flowed into the second lower tank 22, flows into the second lower tank 22 on one end side (right in FIG. 1) of the heat exchanger 1 relative to the partition part 19.

The refrigerant, which has flowed into the second lower tank 22 on one side, flows in the second refrigerant flow path in the flat tube 2 and flows into the second upper tank 12. The refrigerant, which has flowed into the second upper tank 12, flows toward one end side (right in FIG. 1) in the lamination direction of the second upper tank 12. The refrigerant, which has flowed into one end of the second upper tank 12, flows outside the heat exchanger 1 through the refrigerant outlet (Rout).

Although in the present embodiment, the heat exchanger 1 has been configured in the above-described manner, the configuration is not limited to the above-described configuration. The position and the number of installation of the partition parts 18 and 19, the position and the number of installation of the communication flow path 31, and the position of the refrigerant inlet (Rin) and the refrigerant outlet (Rout) can be appropriately changed, so that the flow path, in which the refrigerant flows, is designed to be a predetermined flow path.

Next, the communication flow path 31 will be described with reference to FIGS. 2 to 5. As illustrated in FIG. 2, the communication flow path 31 provided on the end plate 4 (communication member) of the present embodiment is a flow path which communicates the first lower tank 21 with the second lower tank 22. In FIGS. 2 to 4, the communication flow path 31 is illustrated to be positioned on the upper right side. Although the present embodiment is described by being applied in the communication flow path 31, which communicates the first lower tank 21 with the second lower tank 22, the flow path is not particularly limited as long as it communicates adjacent tanks.

The flow path of the communication flow path 31 is formed by a wall body 32 provided on the end plate 4. As illustrated in FIG. 5, the outer shape of the wall body 32 of the communication flow path 31 is long in the width direction, when seen from the lamination direction, compared with in a height direction (longitudinal direction) perpendicular to the lamination direction and the width direction.

The outer shape of the wall body 32 of the communication flow path 31 is vertically symmetric (symmetric in the height direction) and bilaterally symmetric (symmetric in the width direction), when seen from the lamination direction. A throttle portion 34 is formed in the center in the width direction of this communication flow path 31. An outer wall surface of the wall body 32 in the throttle portion 34 has a curved surface formed in a protruded shape inside the communication flow path 31 with a predetermined radius of curvature R. Therefore, as illustrated in FIG. 3, the communication flow path 31 is the flow path, in which the center in the width direction is narrow and both sides in the width direction are wide. The thickness of the wall body 32 of the communication flow path 31 is, for example, 0.5 mm to 1.0 mm.

Here, as illustrated in FIG. 5, the length, in which an outer dimension (dimension of the outer wall surface of the wall body 32) in the height direction is the maximum, of the communication flow path 31 seen from the lamination direction, is set to be H. That is, the length H is the length between a pair of top parts 32a, in which the outer dimension in the height direction is the maximum. At this time, since the communication flow path 31 is symmetric in the width direction, the pair of top parts 32a in the length H is provided in each of both sides in the width direction.

In addition, the length, in which an outer dimension in the height direction is the minimum, of the communication flow path 31 seen from the lamination direction, is set to be L. That is, the length L is the length between a pair of valley parts 32b, which is formed on the throttle portion 34, in which the outer dimension in the height direction is the minimum. Here, the length L is the length which passes through the center in the width direction.

Moreover, the length, in which an outer dimension in the width direction is the maximum, of the communication flow path 31 seen from the lamination direction, is set to be W. That is, the length W is the length between a pair of top parts 32c, in which the outer dimension in the width direction is the maximum. Specifically, the length W is W<40 mm.

Then, since the communication flow path 31 is long in the width direction compared with in the height direction (longitudinal direction), 0.5<H/W<1.0 is satisfied. Therefore, the first lower tank 21 and the second lower tank 22 adjacent to each other in the width direction can be suitably connected to the communication flow path 31.

The communication flow path 31 configured in the above manner is provided with the throttle portion 34 in the center in the width direction, so that pressure deformation of the communication flow path 31 is suppressed. However, only providing the throttle portion 34 may cause concentration of stress at the throttle portion 34.

Therefore, the shape of the communication flow path 31 is made as the shape described below.

In the communication flow path 31, the radius of curvature R of the wall body 32 in the throttle portion 34 is R≧0.2 H. That is, in the throttle portion 34, the radius of curvature R is formed to be R≧0.2 H, so that the gradient of the throttle portion 34 becomes gentle and the concentration of the stress can be suppressed.

In addition, in the communication flow path 31, the length L of the throttle portion 34 in the height direction is L≦0.9 H. That is, in the throttle portion 34, the length L is formed to be L≦0.9 H, so that pressure receiving area in a surface perpendicular to the lamination direction of the communication flow path 31 is reduced and the rigidity can be enhanced by the wall body 32 of the throttle portion 34.

Moreover, in the communication flow path 31, the top part 32a of the length H is positioned in the width direction outside by more than ¼ W from the valley part 32b of the length L. That is, when a line, passing through the top parts 32a of the length H, is set to be an axis line I, and a shape, which is obtained by developing the outer part in the width direction from the axis line I line-symmetrically around the axis line I, is set to be a virtual oval O, the communication flow path 31 is shaped, so that outer diameters of virtual ovals O at both sides in the width direction do not overlap. That is, the length C of the virtual oval O in the width direction is C≦W/2. Therefore, a pressure receiving surface of the communication flow path 31 from the first lower tank 21 in the lamination direction, and a pressure receiving surface of the communication flow path 31 from the second lower tank 22 do not overlap. As a result, pressure increase caused by overlapping of the pressure receiving surfaces can be suppressed. At this time, the outer shape of the virtual oval O is short in the width direction compared with in the height direction.

As described above, according to the present embodiment, the pressure deformation of the end plate 4 can be suppressed, by providing the throttle portion 34 in the communication flow path 31 and making the shape of the communication flow path 31 as the above-described shape.

In addition, according to the configuration of the present embodiment, the outer shape of the virtual oval O can be formed to be short in the width direction compared with in the height direction. Therefore, the communication flow path 31 can be made short in the width direction and the configuration of the heat exchanger 1 itself can be made compact.

In addition, according to the present embodiment, the communication flow path 31 can be made long in the width direction compared with in the height direction. Therefore, the first lower tank 21 and the second lower tank 22 adjacent to each other in the width direction can be suitably connected to the communication flow path 31

Although the present embodiment is applied to the communication flow path 31, which communicates the first lower tank 21 with the second lower tank 22, the present embodiment may be applied to a communication flow path, which communicates the first upper tank 11 with the second upper tank 12.

REFERENCE SIGNS LIST

1 heat exchanger

2 flat tube

3 corrugated fin

4 end plate

11 first upper tank

11
a first upper opening

12 second upper tank

12
a second upper opening

21 first lower tank

21
a first lower opening

22 second lower tank

22
a second lower opening

31 communication flow path

32 wall body

32
a top part in the height direction

32
b valley part in the height direction

32
c top part in the width direction

34 throttle portion

Rin refrigerant inlet

Rout refrigerant outlet

I axis line

O virtual oval

HEAT EXCHANGER

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