JP6284384B2 - Heat exchanger - Google Patents

Description

  The present invention relates to a heat exchanger capable of cooling the air by circulating a refrigerant therein and allowing air to pass through to exchange heat with the refrigerant.

  Conventionally, in a vehicle such as an automobile, a heat exchanger such as a condenser in which a refrigerant circulates and a radiator in which cooling water circulates has been used. This heat exchanger is disclosed in, for example, Patent Document 1. And a pair of tanks through which the refrigerant and the like circulate, a plurality of tubes connected between the tanks, and a plurality of fins provided between the tubes. The fin is formed, for example, by bending a thin plate made of a metal material into a wave shape by press molding or the like, and a plurality of louvers are formed along the direction in which air flows in the heat exchanger.

  And the heat exchanger mentioned above is arrange | positioned at the vehicle front side, for example in the engine room of a vehicle, and when driving | running | working wind passes between a tube, a fin, and a louver at the time of vehicle travel, air, a refrigerant | coolant, etc. Heat is exchanged between them, and the refrigerant and the like are cooled.

Japanese Patent No. 4456750

  In recent years, each component has been reduced in weight in order to promote the reduction in fuel consumption of vehicles, and as part of this, fin thickness (plate thickness) is reduced in heat exchangers. However, the strength of the fins decreases with the thinning of the fins, and the fins are likely to be deformed by hitting a stepping stone from the front when the vehicle is running or by the water pressure of a high-pressure washing machine when washing the vehicle. There is a problem that the deformed fins obstruct the air flow and the heat exchange performance is lowered.

  The present invention has been made in consideration of the above-described problems, and an object of the present invention is to provide a heat exchanger that can suppress deformation of the fins and maintain desired heat exchange performance.

In order to achieve the above-mentioned object, the present invention provides a set of tanks spaced apart from each other, a plurality of tubes whose longitudinal ends are respectively connected to the tanks, and adjacent tubes. In a heat exchanger having a plurality of fins provided between them and performing heat exchange between air passing through the fins and a medium flowing through the tube,
The fin has a plurality of louvers arranged so as to be separated from each other along the air blowing direction, and the louver opens so as to be inclined with respect to the blowing direction, and the fin ends of the fins along the blowing direction. A connecting portion that connects the louvers arranged adjacent to each other to each other ,
Louvers connected connecting part, the inclination angle with respect to the blowing direction with respect to the unconnected other louver of the connecting portion is smaller, characterized in Rukoto.

According to the present invention, in the heat exchanger having a plurality of fins between adjacent tubes, the fins are provided with a plurality of louvers arranged so as to be separated from each other along the air blowing direction. Are inclined so as to be inclined with respect to the blowing direction, and adjacent louvers are connected to each other by a connecting portion at the fin end portion of the fin along the blowing direction.

Accordingly, since the strength can be improved by connecting the louvers at the connection portion at the fin end portion of the fin , for example, a stepping stone hits the fin end portion of the fin when the heat exchanger is mounted on the vehicle. Even in this case, the deformation of the fins with increased strength is reliably suppressed. As a result, an increase in air flow resistance due to the deformation of the fin is prevented, and desired heat exchange performance can be obtained by allowing air to smoothly pass from the upstream side to the downstream side of the heat exchanger. . In addition, by forming the louver connected to the connecting portion with a small inclination angle with respect to the blowing direction with respect to the other louvers not connected to the connecting portion, the fin end portion that becomes the upstream side or the downstream side when the air flows is used. Since the flow path resistance can be reduced, air can be further smoothly circulated downstream.

Moreover, it is good for a connection part to connect the louvers arrange | positioned at the fin edge part used as the upstream of the ventilation direction at least. Thereby, it becomes possible to improve the intensity | strength of the edge part which becomes the front at the time of vehicle mounting, and can suppress the deformation | transformation of the fin resulting from contact with a stepping stone etc. suitably.

Furthermore, the inclination angle of the louvers, the smallest fin end portion side, by forming so as to gradually increase toward the flat part provided in parallel airflow direction substantially from the fin end, downstream from the upstream side It is possible to reduce the flow path resistance of the air flowing through the inside of the heat exchanger to the side and smoothly distribute it.

  Furthermore, by integrally forming the connection portion with the fin, it is possible to improve the manufacturability compared to the case where the connection portion is formed in a separate process, and it is preferable that the number of parts does not increase. is there.

  Furthermore, the connecting portion may connect the downstream end portion of one louver and the upstream end portion of the other louver.

  According to the present invention, the following effects can be obtained.

  That is, since the strength can be improved by connecting the louvers at the connection portion at the end portion along the blowing direction of the fin constituting the heat exchanger, for example, when the heat exchanger is mounted on the vehicle, Even if a stepping stone hits the part, the deformation of the fins with increased strength is surely suppressed, and it is avoided that the flow of air is obstructed with the deformation. Can be smoothly passed from the upstream side to the downstream side, and the desired heat exchange performance can be maintained.

It is the whole heat exchanger front view concerning an embodiment of the invention. It is an enlarged front view which shows the fin vicinity in the heat exchanger of FIG. It is sectional drawing along the III-III line of FIG. It is sectional drawing which shows the fin of the heat exchanger which concerns on a 1st modification. It is sectional drawing which shows the fin of the heat exchanger which concerns on a 2nd modification.

  Preferred embodiments of the heat exchanger according to the present invention will be described below and described in detail with reference to the accompanying drawings. In FIG. 1, reference numeral 10 indicates a heat exchanger according to an embodiment of the present invention.

  The heat exchanger 10 is used, for example, as a condenser that is mounted in an engine room of a vehicle and in which a refrigerant (medium) circulates, and as shown in FIG. The first and second tanks 12, 14, the plurality of tubes 16 connecting the first tank 12 and the second tank 14, and the plurality of fins 18 provided between the tubes 16 and bent in a wave shape. In the thickness direction of the heat exchanger 10 perpendicular to the longitudinal direction of the first and second tanks 12 and 14 (in FIG. 1, from the front of the page to the back direction, in FIG. 3, the direction of arrow F). By passing, heat exchange with the refrigerant is performed.

  Here, the case where the heat exchanger 10 is arranged and used so that the first tank 12 is on the upper side and the second tank 14 is on the lower side as shown in FIG. 1 will be described.

  The first and second tanks 12 and 14 are, for example, formed in a tubular shape with both ends closed, and at one end of the first tank 12, an introduction pipe 20 into which a refrigerant is introduced from the outside, and a heat exchanger The lead-out pipes 22 through which the refrigerant circulated in the interior of the pipe 10 is connected. The introduction pipe 20 and the outlet pipe 22 are connected so as to be parallel to the thickness direction of the heat exchanger 10.

  The tube 16 is formed of, for example, a flat tube made of an aluminum material, and has substantially the same cross-sectional shape along the longitudinal direction. The tube 16 extends in the vertical direction between the first tank 12 and the second tank 14, and one end portion thereof is connected to the first tank 12 to communicate with each other, and the other end portion is the second tank. A plurality of tanks 14 are provided so as to communicate with each other by being connected to the tank 14 and to be spaced apart at equal intervals along the longitudinal direction of the first and second tanks 12 and 14. As a result, the refrigerant supplied into the first tank 12 is supplied into the second tank 14 through the plurality of tubes 16 and circulates again to circulate toward the first tank 12 side.

  As shown in FIGS. 1 to 3, the fins 18 are bent into a corrugated cross section by press-molding a thin plate made of, for example, an aluminum material, and alternately come into contact with two adjacent tubes 16. And is formed in a wavy cross-sectional shape so as to extend a predetermined width along the thickness direction (arrow A direction) of the heat exchanger 10. Air flows along the width direction (arrow A direction) of the fin 18, and the wall 24 along the air flow direction F is substantially perpendicular to the extending direction of the tube 16 as shown in FIG. A flat portion 26 along the flow direction F and a plurality of louver portions 28 notched so as to be inclined at a predetermined angle with respect to the flat portion 26 are formed.

  The flat portions 26 and the louver portions 28 are not limited to being formed one by one with respect to the wall portion 24, and a plurality of sets of the flat portions 26 and the louver portions 28 are formed as one set. Also good.

  The flat portion 26 is formed, for example, at a substantially central portion of the wall portion 24 along the flow direction F, and the louver portion 28 is formed on the upstream side in the flow direction F (arrow A1 direction) with respect to the flat portion 26. And an outlet louver 32 formed on the downstream side (in the direction of arrow A2) in the flow direction F with respect to the flat portion 26.

  A plurality of the inlet louvers 30 are formed so as to be inclined at substantially the same angle with respect to the flat portion 26 and to be spaced apart from each other along the extending direction of the wall portion 24 (direction of arrow A). A plurality of outlet louvers 32 are formed so as to be inclined at substantially the same angle with respect to the flat portion 26, and are spaced apart from each other along the extending direction of the wall portion 24 (direction of arrow A). 30 and the outlet louver 32 are formed in the same quantity so as to be substantially symmetrical about the flat portion 26.

  Further, both end portions along the extending direction of the wall portion 24 (arrow A direction) are formed in a flat plate shape that is substantially flush with the flat portion 26, and are connected to the upstream end portion 24a. The inlet louver 30 on the side and the inlet louver 30 adjacent to the inlet louver 30 are connected by a first connection wall (connecting portion) 34.

  The first connection wall 34 is formed integrally with the inlet louver 30 by, for example, press molding or the like, and has a downstream end portion of the inlet louver 30 that is the most upstream side and an upstream end portion of the adjacent inlet louver 30. By connecting, it is formed so as to be substantially orthogonal to the inclined inlet louver 30.

  On the other hand, in the wall 24, the most downstream outlet louver 32 connected to the other end 24 b on the downstream side and the outlet louver 32 adjacent to the outlet louver 32 are connected by the second connecting wall (connecting part) 36. Connected.

  The second connection wall 36 is formed integrally with the outlet louver 32 by, for example, press molding or the like, and has an upstream end of the outlet louver 32 that is the most downstream side and a downstream end of the adjacent outlet louver 32. By connecting, it is formed so as to be substantially orthogonal to the inclined outlet louver 32.

  That is, the opening is closed by connecting the two adjacent inlet louvers 30 by the first connection wall 34, and the two connecting louvers 32 are connected by the second connection wall 36. The opening part opened between louvers is obstruct | occluded.

  As shown in FIG. 3, the air from the upstream side of the fin 18 is guided from the one end portion 24 a of the wall portion 24 to the space above the wall portion 24 by the inlet louver 30 along the flat portion 26. After being distributed, the outlet louver 32 leads again to the space below the wall portion 24 and flows to the downstream side on the other end portion 24 b side of the wall portion 24. That is, the air flows in a wave shape in the vertical direction of the wall portion 24 with the flat portion 26 interposed therebetween.

  The heat exchanger 10 according to the embodiment of the present invention is basically configured as described above. Next, the operation and effect of the heat exchanger 10 will be described.

  First, in the heat exchanger 10, the refrigerant is supplied from a pipe (not shown) into the first tank 12 through the introduction pipe 20, flows through the plurality of tubes 16 to the second tank 14 side, and again to the first tank 12 side. Is distributed from the outlet pipe 22 to a pipe (not shown). At this time, heat exchange is performed between the refrigerant flowing through the tubes 16 and the air passing through the fins 18, and the refrigerant is cooled and led out and circulated to a compressor (not shown).

  For example, when the heat exchanger 10 described above is mounted as a condenser in an engine room of a vehicle, a stepping stone or the like hits one end portion 18a of the fin 18 on the front side of the vehicle when the vehicle is traveling. Is assumed. Further, it is assumed that water pressure is applied to the one end portion 18 a of the fin 18 when the vehicle is cleaned using the high-pressure washer. Even in such a case, the first connecting wall 34 connects the inlet louver 30 disposed on the most upstream side on the one end 18a side of the fin 18 and the adjacent inlet louver 30 to increase the strength. Therefore, the one end portion 18a of the fin 18 is not easily deformed by the stepping stone, water pressure, or the like.

  As a result, the deformation of the fins 18 obstructs the flow of air and does not increase the flow resistance of the air, and allows the air to pass smoothly from the upstream side to the downstream side of the heat exchanger 10. Thus, the desired heat exchange performance can be obtained.

  Further, not only the first connection wall 34 is provided in the inlet louver 30 of the fin 18 on the upstream side, but also the second connection wall 36 is similarly provided between the two outlet louvers 32 adjacent to the most downstream side, Both end portions of the wall portion 24 of the fin 18 can be made symmetrical. As a result, the manufacturing distortion at both ends of the fin 18 can be made substantially uniform to ensure stable quality, and the productivity when the fin 18 including the louver 28 is formed by press molding or the like can be improved. Moreover, even when the heat exchanger 10 is arranged so that the other end portion 18b of the fin 18 is on the upstream side, desired strength and heat exchange performance can be obtained. Furthermore, since the strength of the fin 18 on the side of the other end 18b can be increased by providing the second connection wall 36, for example, even when another component comes into contact with the fin 18 from the other end 18b side, deformation occurs. Can be suitably suppressed.

  Further, as shown in FIG. 3, the one end portion 18 a of the fin 18 is formed in a corrugated cross section by the first connection wall 34 and the two inlet louvers 30. Compared with the case, the effect as a reinforcing rib is acquired. Therefore, further improvement in strength in the vicinity of the one end portion 18a of the fin 18 is obtained, and deformation can be more preferably suppressed. Similarly, since the other end portion 18b of the fin 18 is also formed in a corrugated cross section by the second connection wall 36 and the two outlet louvers 32, it is reinforced compared to the case where it is simply flat like the flat portion 26. The effect as a rib is acquired. As a result, further improvement in strength in the vicinity of the other end portion 18b of the fin 18 is obtained, and deformation can be more suitably suppressed.

  Further, like the fins 52 of the heat exchanger 50 according to the first modification shown in FIG. 4, the inlet louver 54a arranged on the most upstream side (in the direction of arrow A1), and the inlet louver adjacent to the inlet louver 54a 54b is formed with a smaller inclination angle θ with respect to the flat portion 26 than the other inlet louvers 54c, and the two inlet louvers 54a, 54b having a smaller inclination angle θ are connected to each other by a first connection wall (connection portion) 56. Similarly, the outlet louver 58a disposed on the most downstream side (in the direction of arrow A2) and the outlet louver 58b adjacent to the outlet louver 58a are inclined with respect to the flat portion 26 as compared with the other outlet louvers 58c. A small θ may be formed, and the two outlet louvers 58 a and 58 b having a small inclination angle θ may be connected by the second connection wall (connection portion) 60.

  That is, in the fin 52, the inlet louvers 54a and 54b and the outlet louvers 58a and 58b provided on the one end 24a side and the other end 24b side of the wall portion 24 are looser than the other inlet louvers 54c and outlet louvers 58c. It is formed at an angle.

  As described above, in the fin 52 according to the first modification, the inlet louver 54a and the adjacent inlet louver 54b provided on the most upstream side on the one end portion 52a side of the fin 52 are air in comparison with the other inlet louvers 54c. Since the inclination angle θ with respect to the flow direction F is small, the resistance when the air flows is reduced, and the air can be circulated more smoothly in the heat exchanger 50. Similarly, on the other end 52b side of the fin 52, the most downstream outlet louver 58a and the adjacent outlet louver 58b are formed so that the inclination angle θ with respect to the air flow direction F is smaller than that of the other outlet louvers 58c. Therefore, resistance when the air flows downstream is reduced, and the air can be circulated in the heat exchanger 50 more smoothly.

  In other words, in the heat exchanger 50, air stagnation in the vicinity of the most upstream inlet louver 54a and the first connection wall 56 on the one end 24a side of the fin 52 can be suitably suppressed.

  As a result, the heat exchange performance can be further enhanced by allowing air to smoothly flow through the heat exchanger 50.

  Further, in the heat exchanger 70 according to the second modification shown in FIG. 5, the fins are formed so that the inclination angles θ of the plurality of inlet louvers 62 a to 62 g and the outlet louvers 64 a to 64 g gradually increase toward the flat portion 26. It differs from the fin 52 which concerns on the 1st modification mentioned above by the point in which 66 is formed.

  In the fin 66, the inclination angle θ of the plurality of inlet louvers 62b to 62g provided on the flat portion 26 side (arrow A2 direction) is flat with respect to the inlet louver 62a arranged on the most upstream side (arrow A1 direction). It is formed so as to gradually increase toward the portion 26 side (arrow A2 direction). In other words, among the plurality of inlet louvers 62a to 62g, the inlet louver 62a on the one end 24a side (arrow A1 direction) has the smallest inclination angle θ, and the inlet louver 62g on the flat part 26 side (arrow A2 direction). Is formed so that the inclination angle θ is the largest.

  On the other hand, the plurality of outlet louvers 64a to 64g constituting the fin 66 are a plurality of outlets provided on the flat portion 26 side (arrow A1 direction) with respect to the outlet louver 64a arranged on the most downstream side (arrow A2 direction). The louvers 64b to 64g are formed so that the inclination angle θ gradually increases toward the flat portion 26 side (arrow A1 direction). In other words, out of the plurality of outlet louvers 64a to 64g, the outlet louver 64a on the other end 24b side (arrow A2 direction) has the smallest inclination angle θ, and the outlet louver on the flat part 26 side (arrow A1 direction). The inclination angle θ of 64 g is formed to be the largest.

  As described above, in the fin 66 according to the second modified example, the plurality of inlet louvers 62a to 62g gradually move toward the air flow direction F from the most upstream inlet louver 62a toward the flat portion 26 side (arrow A2 direction). Since the inclination angle θ is gradually increased, the air flows from the upstream side to the downstream side (in the direction of arrow A2) on the one end portion 66a side of the fin 66 as compared with the fin 52 according to the first modification. The resistance at the time of flowing can be further reduced, and air stagnation in the vicinity of the one end portion 66a can be more suitably suppressed. As a result, air can be circulated more smoothly along the heat exchanger 70.

  Further, the second deformation portion 66b of the fin 66 is also formed so that the inclination angle θ gradually decreases from the most upstream outlet louver 64g toward the most downstream outlet louver 64a. Compared with the fin 52 according to the example, the resistance when the air flows downstream (in the direction of the arrow A2) is further reduced, and the air can be circulated in the heat exchanger 70 more smoothly. Become.

  The heat exchanger according to the present invention is not limited to the above-described embodiment, and can of course have various configurations without departing from the gist of the present invention.

DESCRIPTION OF SYMBOLS 10, 50, 70 ... Heat exchanger 12 ... 1st tank 14 ... 2nd tank 16 ... Tube 18, 52, 66 ... Fin 24 ... Wall part 28 ... Louver part 30, 54a-54c, 62a-62g ... Inlet louver 32 , 58a to 58c, 64a to 64g ... outlet louvers 34, 56 ... first connection wall 36, 60 ... second connection wall

Claims (5)

A pair of tanks arranged at intervals from each other, a plurality of tubes whose both ends along the longitudinal direction are respectively connected to the tank, and a plurality of fins provided between the adjacent tubes In the heat exchanger for performing heat exchange between the air passing through the fin and the medium flowing through the tube,
The fin has a plurality of louvers arranged so as to be separated from each other along the air blowing direction, and the louvers open so as to be inclined with respect to the blowing direction, along the blowing direction. In addition, a connecting portion that connects the louvers arranged adjacent to each other at the fin ends of the fins ,
Wherein the louvers connected thereto of the connection portion, a heat exchanger, characterized in Rukoto inclination angle with respect to the blowing direction with respect to the other louvers that are not connected to the connecting portion is formed smaller. The heat exchanger according to claim 1, wherein
The said connection part connects the louvers arrange | positioned at the fin edge part used as the upstream of the said ventilation direction at least, The heat exchanger characterized by the above-mentioned. The heat exchanger according to claim 1 or 2 ,
The inclination angle of the louver is the smallest at the fin end portion side, and is formed so as to gradually increase from the fin end portion toward a flat portion provided substantially parallel to the blowing direction. Exchanger. In the heat exchanger as described in any one of Claims 1-3 ,
The heat exchanger according to claim 1, wherein the connecting portion is integrally formed with the fin. In the heat exchanger as described in any one of Claims 1-4 ,
The said connection part connects the downstream edge part in one louver, and the upstream edge part in the other louver, The heat exchanger characterized by the above-mentioned.

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