JP2013204855A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger suppressing the bending of a fin, and preventing a decrease of a heat transfer amount.SOLUTION: A heat exchanger includes a fin having a rib and a plurality of heat transfer tube inserts, and heat transfer tubes inserted into the heat transfer tube inserts. The rib is formed at a position crossing over a line connecting with one edge of the fin and ends of one edge sides of the heat transfer tube inserts. By this, when an external force is applied to the fin, the bending of the fin in parallel with an arrangement direction of the heat transfer tube inserts is suppressed, and a decrease of the heat transfer amount can be prevented.

Description

  The present invention relates to a fin-and-tube heat exchanger.

  Air conditioners, automobile radiators, and the like transport heat from one relatively hot place to another relatively cool place via a fluid called a refrigerant. In many cases, a heat exchanger is used as means for efficiently absorbing heat from the above-mentioned relatively high-temperature place and efficiently dissipating heat from the refrigerant to a relatively low-temperature place. In the air conditioner, this heat exchanger is often used in the form of fin and tube. This fin-and-tube type heat exchanger is a heat transfer tube for flowing a refrigerant inside to exchange heat with outside air. It is attached.

  When using such a heat exchanger for an air conditioner, when manufacturing the heat exchanger or assembling the heat exchanger to the air conditioner, it is unavoidable or a large force is applied to the fins as needed, Fins sometimes bent. As a specific example of bending, if the heat exchanger is manufactured, the heat exchanger suddenly collides with another object during work, or the heat exchanger is being transported in the factory. May be gripped with a large force. In addition, when the heat exchanger is assembled to the air conditioner, the entire heat exchanger may be bent into an L shape.

  When the fins are bent in this way, the gaps between the fins are originally shielded by the bent portions of the fins. When it is a heat exchanger of an air conditioner and the heat exchanger performs heat exchange between the refrigerant in the heat transfer tube and the air outside the heat exchanger, a part of the gap between the fins is caused by the bent part of the fin. When shielded, air does not flow as intended in the design of the heat exchanger, and as a result, the amount of heat transfer decreases and the performance of the heat exchanger decreases.

  In order to prevent such bending of the fin, there have been some examples in which the tensile strength of the fin material is improved or the fin strength is improved by adding a reinforcing shape called a rib to the fin. As an example of improving the fin strength by the rib, for example, a heat exchanger in which a rib extending substantially parallel to the longitudinal direction of the fin is added to the outer edge of the fin to improve the fin strength is disclosed in Patent Document 1 and Patent Document 2 is disclosed. By providing ribs on the fin, the moment of inertia of the cross section of the fin increases and the strength increases.

JP 2006-153290 A Japanese Utility Model Publication No. 5-90173

  However, in these heat exchangers, in the vicinity of the hole for inserting the heat transfer tube, the fin is bent along the arrangement direction of the hole for inserting the heat transfer tube, so that the rib that extends substantially parallel to the longitudinal direction of the fin is bent. There is a problem that there is a place where it is not possible to suppress.

  This invention is made | formed in view of these subjects, and it aims at providing the heat exchanger which suppresses the bending of a fin and prevents the fall of the amount of heat transfer.

  The heat exchanger according to the present invention is a heat exchanger including a first fin having a rib and a plurality of heat transfer tube insertion portions, and a heat transfer tube inserted into the heat transfer tube insertion portion, wherein the rib is the first The heat exchanger is formed from a side of the fin to a position exceeding a line connecting the end of one side of the heat transfer tube insertion portion.

  According to the heat exchanger of the present invention, the heat exchanger includes a first fin having a rib and a plurality of heat transfer tube insertion portions, and a heat transfer tube inserted into the heat transfer tube insertion portion. Since it is formed from the one side of the first fin to the position connecting the end of the one side of the heat transfer tube insertion portion, it is possible to suppress the bending of the fin and prevent the heat transfer amount from decreasing.

It is the perspective view of the heat exchanger in Embodiment 1 of this invention, the top view of a fin, and a side view. It is a top view of the fin in Embodiment 1 of this invention. It is a perspective view of the heat exchanger in Embodiment 2 of this invention, and a top view of a fin. It is a top view of the fin in Embodiment 3 of this invention. It is the top view and partial enlarged view of the fin in Embodiment 4 of this invention. It is the external appearance perspective view of the conventional heat exchanger, and the top view of a fin. It is AA sectional drawing of the conventional heat exchanger. It is a schematic diagram explaining the bending process of a heat exchanger. It is a schematic diagram of the bending apparatus of a heat exchanger. It is a top view of the fin with a rib of the conventional heat exchanger.

Embodiments of the present invention will be described below.
Embodiment 1 FIG.

  Fig.1 (a) is a perspective view which shows typically the structure of the heat exchanger in Embodiment 1 of this invention. The heat exchanger according to the present embodiment includes a heat transfer tube and fins. FIG.1 (b) is a top view of the fin of the heat exchanger shown to Fig.1 (a). FIG.1 (c) is a top view which shows an example of the size of a fin. FIG.1 (d) is a side view which shows an example of the size of a fin.

  First, the structure of the heat exchanger in this Embodiment is demonstrated based on a figure. In the heat exchanger according to the first embodiment, heat transfer tubes 2 in which refrigerant flows are arranged at predetermined intervals, and heat exchange fins 1 that are stacked in parallel at predetermined intervals are assembled to the heat transfer tubes 2. ing.

  The fin 1 is a rectangular flat plate, and a plurality of heat transfer tube insertion portions 3 and ribs 8 are formed along the longitudinal direction of the fin 1. The fin 1 is formed of a thin plate having a thickness of about 0.1 to 0.2 mm, and the stacking interval of the fins 1 is determined by the characteristics of the heat exchanger, but is generally about 1.0 mm to 2.0 mm. is there. An air passage portion is formed by the gap between the fins 1 and 1 stacked. In the heat exchanger according to the first embodiment, a plurality of fins 1 having the same shape are stacked at a predetermined interval. The raw material of the fin 1 is mainly aluminum or an aluminum alloy.

  The heat transfer tube insertion portion 3 is a U-shaped notch that penetrates the plate surface of the fin 1 and opens on one side 1 a of the long sides 1 a and 1 b of the fin 1, along the longitudinal direction of the fin 1. It is formed at a predetermined interval. The shape of the heat transfer tube insertion portion 3 is formed in a shape that substantially follows a part of the outer surface of the heat transfer tube 2.

  The rib 8 is a reinforcing portion formed in a convex shape, and is opposite to the other side 1b of the long sides 1a and 1b of the fin 1, that is, the long side 1a on the side where the heat transfer tube insertion portion 3 is formed. It is formed at a predetermined interval along the long side 1b on the side. By providing the ribs 8 on the fins 1, the cross-sectional secondary moment of the fins 1 increases, so that the strength of the fins 1 can be improved. The heat transfer tube insertion portion 3 and the rib 8 are molded by the same progressive press machine when the fin 1 is shaped.

  The heat transfer tube 2 is a flat tube that has a hollow through which refrigerant flows and has a flat cross section. The fins 1 and the heat transfer tubes 2 are assembled using, for example, a fin insertion device that fits the fins 1 one by one into the heat transfer tubes 2 arranged at a predetermined interval. Further, the fin 1 and the heat transfer tube 2 may be assembled by inserting the heat transfer tube 2 into the heat transfer tube insertion portion 3 of the fin 1 held with a predetermined gap. The assembled fin 1 and the heat transfer tube 2 are joined by an adhesive or brazing. When joining by brazing, after arrange | positioning brazing | wax material in the contact part vicinity of the fin 1 and the heat exchanger tube 2, it throws into an electric furnace, and the fin 1 and the heat exchanger tube 2 are joined. In the heat exchanger of the first embodiment, a plurality of fins 1 having the same shape are used.

Next, the shape of the rib 8 will be described in detail.
The rib 8 is integrally formed from the other side 1b of the fin 1, that is, from the end of the fin 1 to a position exceeding the virtual line 4 indicated by a broken line in FIG. The imaginary line 4 is a heat transfer tube adjacent to the end 3a on the other side 1b side of the fin 1 among the peripheral portions of the heat transfer tube insertion portion 3 formed so as to open to one side 1a of the fin 1. These are lines connected in sequence between the insertion portions 3. Of the plate surface of the fin 1, a region 5 a between the virtual line 4 and one side 1 a of the fin 1 (a white portion in FIG. 1B) is connected to the heat transfer tube insertion portion 3 with the heat transfer tube 2. In the state where is inserted, the possibility of bending is low. On the other hand, of the plate surface of the fin 1, a region 5 b between the virtual line 4 and the other side 1 b of the fin 1 (the portion indicated by the oblique lines in FIG. 1B) is located in the heat transfer tube insertion portion 3. Even in the state where the heat transfer tube 2 is inserted, there is a high possibility that the fin 1 is bent along the arrangement direction of the heat transfer tube insertion portion 3 in the vicinity of the heat transfer tube insertion portion 3. Therefore, the rib 8 that starts from the end of the fin 1 and passes through the region 5b where the fin 1 is likely to be bent to reach a part of the region 5a where the fin 1 is unlikely to be bent is integrated with the fin 1. By forming, the rigidity of the fin 1 can be raised.

  The size of the rib 8 formed in the region 5a sandwiched between the virtual line 4 and one side 1a of the fin 1 is not particularly defined. However, if the rib 8 is integrally formed from one side 1a of the fin 1 to the other side 1b, the fin 1 may be bent along the rib 8 and the flatness in the longitudinal direction of the fin 1 may be impaired. is there. Therefore, in the region 5a, it is preferable not to form a rib from the virtual line 4 to one side 1a of the fin 1 but to form the rib 8 in a part of the region.

  The rib 8 is arrange | positioned in all the places between adjacent heat exchanger tube insertion parts 3 as shown in FIG.1 (b). Although not shown, a rib 8 may be arranged between the short side of the fin 1 and the heat transfer tube insertion portion 3. The fin 1 has a rib 8 having the same shape.

  FIG. 1C and FIG. 1D are examples of the size of the fin 1. When the width in the short direction of the fin 1 is 20 mm, the thickness is 0.1 mm, the width in the longitudinal direction of the heat transfer tube insertion portion 3 is 15 mm, the width in the short direction is 3 mm, and the pitch of the heat transfer tube insertion portion 3 is 15 mm, For example, the rib 8 may be formed so that the width in the same direction as the short direction of the fin 1 is 7 mm, the width in the same direction as the longitudinal direction of the fin 1 is 1 mm, and the height is 1 mm.

  Next, in the conventional heat exchanger, the deformation of the fin when a force is applied from the outside will be described. FIG. 6A is an external perspective view of a conventional heat exchanger provided with a conventional fin 61 and a heat transfer tube 62. FIG.6 (b) is a top view of the fin 61 used with the conventional heat exchanger. 7 is a cross-sectional view taken along line AA in FIG. 6, FIG. 7A is a cross-sectional view of the heat exchanger before applying an external force, and FIG. 7B is a heat exchange in which the fins 61 are deformed by the external force. FIG. 7C is a cross-sectional view showing a state in which air is sent to the heat exchanger in which the fins 61 are deformed by an external force. FIGS. 8A and 8B are side views of the heat exchanger as viewed from the short side of the fin 61, and are schematic diagrams illustrating bending of the heat exchanger. FIG. 9A and FIG. 9B are side views of the state in which the heat exchanger is installed in the bending device as viewed from the short side of the fin 61. FIG. 10 is a plan view of a conventional fin 81 with ribs.

  As shown in FIG. 6A, in the conventional heat exchanger, circular heat transfer tubes 62 through which refrigerant flows are inserted into fins 61 stacked at predetermined intervals. As shown in FIG. 6B, the fins 61 are thin plates in which the heat transfer tube insertion portions 63 are arranged at a predetermined interval.

  In a heat exchanger not provided with a conventional rib, as shown in FIG. 7A, when an external force in the direction of arrow F is applied to the long side of the fin 61, the fin 61 is As shown in FIG. 3, the fin 61 is often bent in the out-of-plane direction. Such bending of the fin 61 occurs, for example, when the entire heat exchanger is bent into an L shape as shown in FIGS. 8 (a) and 8 (b). When bending the heat exchanger into an L shape, as shown in FIG. 9A, a heat exchanger is installed on the fixed plate 71 and the movable plate 72 of the L-shaped bending device, and the movable plate 72 and The bending piece 74 is rotated. Therefore, an external force is applied to the long side of the fin 61.

  When such an external force is applied to the fin 61, the heat transfer tube 62 is hardly deformed, but the fin 61 is often bent. The place where the possibility that the fin 61 is bent is high is a range shown by hatching in FIG. That is, the regions 65b and 65c between the virtual lines 64a and 64b indicated by broken lines in FIG. 6B and the long sides 61a and 61b of the fin 61 are fins along the arrangement direction of the heat transfer tube insertion portion 63. The imaginary lines 64a and 64b are connected to the end portion 63a on the long side 61a side of the peripheral portion of the heat transfer tube insertion portion 63 formed away from the end of the fin 61. The line 64b connects the line 64a and the end 63b on the long side 61b side.

  When the fins 61 are bent in this manner, the air passage portion that is the gap between the fins 61 that is originally formed is shielded by the bent portions of the fins 61. More specifically, when it is a heat exchanger of an air conditioner and the heat exchanger performs heat exchange between the refrigerant in the heat transfer tube 62 and the air outside the heat exchanger, generally, in FIG. The air flow parallel to the plate surface of the fin 61 indicated by the arrow W1 is created by the fan 66, and heat transfer is promoted. However, when the fin 61 is bent in the out-of-plane direction, as indicated by an arrow W2 in FIG. 7C, a part of the gap between the fins 61 is shielded by the bent portion, and the air is intended for the heat exchanger design. No longer flows. As a result, the amount of heat transfer decreases and the performance of the heat exchanger decreases.

  In order to prevent such bending of the fin, conventionally, a rib 87 extending substantially parallel to the longitudinal direction of the fin 81 as shown in FIG. 10 is added to the fin 81 to improve the strength of the fin 81. It was. However, in the rib 87 extending substantially parallel to the longitudinal direction of the fin 81, the fin 81 is bent along the arrangement direction of the heat transfer tube insertion portion 83 in the vicinity of the heat transfer tube insertion portion 83 as shown by a broken line in FIG. There was a problem that it was not possible to suppress this.

  On the other hand, in the heat exchanger according to the first embodiment, the rib 8 is integrally formed from one side 1b of the fin 1 to a position exceeding the line 4 connecting the end on the one side 1b side of the heat transfer tube insertion portion 3. ing. The rib 8 increases the cross-sectional secondary moment of the fin 1 and improves the strength of the fin 1. As a result, it is possible to suppress the bending of the fin along the arrangement direction of the heat transfer tube insertion portion 3 when an external force is applied to the fin 1.

  As described above, in the heat exchanger according to the first embodiment, the strength of the fins 1 is extremely increased by the ribs 8. Therefore, even if the fins are unavoidable or require a large force, 1 bend can be prevented. This makes it possible to obtain heat exchangers and air conditioners with very low performance variations and stable quality.

  Further, in the heat exchanger according to the first embodiment, since the rib 8 having a shape along the air inflow direction is provided, an increase in pressure loss in the air passage portion due to the rib 8 can be suppressed.

  In the first embodiment, the ribs are arranged on the long side of the fin. However, the same effect can be obtained even if the rib is arranged on the short side of the fin.

In the first embodiment, the heat transfer tube 2 is a flat tube and the heat transfer tube insertion portion 3 is a U-shaped notch opened on one side of the fin 1. However, the present invention is not limited to this. Absent. For example, when the heat transfer tube insertion portion 3 is arranged in a tactile manner, or as shown in FIGS. 2A and 2B, the heat transfer tube is a circular tube, or the heat transfer tube insertion portion is on one side of the fin. The present invention can also be applied to a configuration that is not open. As shown in FIG. 2A, when there are a plurality of regions 15 a and 15 b where the fin 61 is likely to be bent along the arrangement direction of the heat transfer tube insertion portion 63, ribs are provided according to the direction in which an external force is applied. What is necessary is just to determine an area | region. That is, you may provide a rib along both the long sides 11a and 11b of the fin 11. FIG.
Embodiment 2. FIG.

  The structure of the heat exchanger in Embodiment 2 of this invention is demonstrated using FIG. Fig.3 (a) is a perspective view which shows typically the structure of the heat exchanger in Embodiment 2 of this invention. FIGS. 3B and 3C are plan views of fins of the heat exchanger shown in FIG. This embodiment is mainly different from the first embodiment in that two types of fins having different shapes are provided. In the second embodiment, the same elements as those in the first embodiment are denoted by the same reference numerals, and the description thereof is not repeated.

  The structure of the heat exchanger in this Embodiment is demonstrated based on a figure. In the heat exchanger according to the second embodiment, the heat transfer tubes 2 through which the refrigerant flows are arranged at predetermined intervals, and the first fins 1 and the second fins 31 stacked in parallel at the predetermined intervals are transferred. The heat tubes 2 are alternately assembled.

  The first fin 1 has the same shape as the fin 1 of the first embodiment, and includes a heat transfer tube insertion portion 3 and a rib 8. The second fin 31 includes a heat transfer tube insertion portion 33 having the same shape as the heat transfer tube insertion portion 3 of the first fin 1. The second fin 31 is formed in the same shape as the first fin 1 except that the second fin 31 is not provided with a rib. The first fins 1 and the second fins 31 are alternately stacked, and the heat transfer tubes 2 are inserted into the heat transfer tube insertion portions 3 and 33.

  With this configuration, the strength of the fins 1 can be extremely increased, the bending of the fins 1 when an external force is applied to the heat exchanger can be prevented, and the performance stability of the heat exchanger can be improved. Furthermore, since the ratio of the ribs 8 occupying the air passage portion is reduced as compared with the first embodiment, it is possible to suppress an increase in pressure loss of the air passage portion due to the ribs 8 as compared with the first embodiment. A heat exchanger having better heat exchange performance than that of the first embodiment is obtained.

In particular, when an external force is simultaneously applied to a plurality of fins, such as when bending the entire heat exchanger into an L shape, even if fins 31 without ribs are mixed in the laminated fins, The strength can be increased to prevent bending.
Embodiment 3 FIG.

  The structure of the heat exchanger in Embodiment 3 of this invention is demonstrated using FIG. FIG. 4 is a plan view of the fins of the heat exchanger according to Embodiment 3 of the present invention. In this embodiment, as compared with the first embodiment, the configuration of the fins is different and the positions where the ribs are mainly provided are different. In the present embodiment, the same elements as those in the first embodiment are denoted by the same reference numerals, and the description thereof will not be repeated.

  Based on the figure, the structure of the fin 41 of the heat exchanger in this Embodiment is demonstrated. The fin 41 of the heat exchanger according to the third embodiment includes a heat transfer tube insertion portion 43 having the same shape as the heat exchanger according to the first embodiment, and a rib 48. However, in the first embodiment, the ribs 8 are arranged at all locations between the adjacent heat transfer tube insertion portions 3, but in the present embodiment, one rib between the adjacent heat transfer tube insertion portions 3 is arranged. A rib 8 is arranged at the portion. Therefore, there is a portion where the rib 48 is not provided between the adjacent heat transfer tube insertion portions 43.

  With this configuration, the strength of the fin 41 can be extremely increased, the bending of the fin 41 when an external force is applied to the heat exchanger can be prevented, and the performance stability of the heat exchanger can be improved. Furthermore, since the ratio of the ribs 48 occupying the air passage portion is reduced as compared with the first embodiment, it is possible to suppress an increase in pressure loss of the air passage portion due to the ribs 48 as compared with the first embodiment. A heat exchanger having better heat exchange performance than that of the first embodiment is obtained.

In particular, in the longitudinal direction of the fin 41, when the position to which an external force is applied is limited, the strength of the fin even if the rib is provided only at a part of the portion between the adjacent heat transfer tube insertion portions 43. It becomes possible to prevent the bending by increasing.
Embodiment 4 FIG.

  The structure of the heat exchanger in Embodiment 4 of this invention is demonstrated using FIG. Fig.5 (a) is a top view of the fin of the heat exchanger in Embodiment 4 of this invention. FIG. 5 (b) is a partially enlarged view in which a portion surrounded by a broken-line circle in FIG. 5 (a) is enlarged. In this embodiment, the configuration of the fin is compared with that of the first embodiment. The main difference is the rib shape. In the present embodiment, the same elements as those in the first embodiment are denoted by the same reference numerals, and the description thereof will not be repeated.

  Based on the figure, the structure of the fin 51 of the heat exchanger in this Embodiment is demonstrated. The fin 51 of the heat exchanger according to the fourth embodiment includes a heat transfer tube insertion portion 53 and a rib 58.

  Similarly to the heat transfer tube insertion portion 3 of the heat exchanger of the first embodiment, the heat transfer tube insertion portion 53 penetrates the plate surface of the fin 51, and on one side 51 a of the long sides 51 a and 51 b of the fin 51. Opened U-shaped notches are formed at predetermined intervals along the longitudinal direction of the fin 1.

  The rib 58 is a reinforcing portion formed in a convex shape, and is opposite to the other side 1b of the long sides 51a and 51b of the fin 51, that is, the long side 51a on the side where the heat transfer tube insertion portion 53 is formed. It is formed at a predetermined interval along the long side 51b on the side.

  The rib 58 is divided into a plurality of parts in a range extending from the other side 51b of the fin 51 to a position exceeding a virtual line 54 indicated by a broken line in FIG. In the fourth embodiment, the case of dividing by three ribs will be described as an example, but the present invention is not limited to this. The divided ribs 58a, 58b, and 58c pass from the other side 51b of the fin 51 through the region 55b where the fin 51 between the other side 51b of the fin 51 and the virtual line 54 is likely to be bent, The range up to a part of the region 55a between the virtual line 54 and one side 51a of the fin 51 is divided and reinforced. That is, when all the divided ribs 58a, 58b, and 58c are added together, the hypothetical line 54 and one side of the fin pass from the other side 51b of the fin 51 via the region 55b where the fin 51 is likely to be bent. The entire range up to a part of the area between 51a is covered.

  The divided ribs 58a, 58b, and 58c are arranged one by one in the region between the adjacent heat transfer tube insertion portions 53, respectively. Further, the divided ribs 58a, 58b, and 58c overlap with any of the other divided ribs 58a, 58b, and 58c in the direction parallel to the long side of the fin 51. For example, a region A between two broken lines in FIG. 5B is an overlapping region between the ribs 58 b and the ribs 58 c in a direction parallel to the long side 51 b of the fin 51.

  With this configuration, the strength of the fins 51 can be extremely increased, the bending of the fins 51 when an external force is applied to the heat exchanger can be prevented, and the performance stability of the heat exchanger can be improved. Furthermore, since the ratio of the ribs 58 occupying the air passage portion is reduced as compared with the first embodiment, it is possible to suppress an increase in pressure loss of the air passage portion due to the ribs 58 as compared with the first embodiment. A heat exchanger having better heat exchange performance than that of the first embodiment is obtained.

  DESCRIPTION OF SYMBOLS 1 1st fin, 2 Heat transfer tube, 3 Heat transfer tube insertion part, 4 Virtual line, 8 Rib, 13 Heat transfer tube insertion part, 31 2nd fin.

Claims (4)

A first fin having a rib and a plurality of heat transfer tube inserts;
A heat exchanger comprising a heat transfer tube inserted into the heat transfer tube insertion portion,
The heat exchanger according to claim 1, wherein the rib is formed from one side of the first fin to a position exceeding a line connecting the end of the one side of the heat transfer tube insertion portion. 2. The heat exchanger according to claim 1, wherein the rib is integrally formed from one side of the first fin to a position exceeding a line connecting the end of the one side of the heat transfer tube insertion portion. The heat exchanger according to claim 1, wherein the rib is divided into a plurality of parts, and the divided ribs overlap in a direction parallel to one side of the first fin. A second fin without ribs,
The heat exchanger according to any one of claims 1 to 3, wherein the first fin and the second fin are stacked.

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