JP2018124047A - Heat exchanger, method for manufacturing the same, and radiator - Google Patents

Abstract

In a heat exchanger, heat transfer performance is improved by increasing a heat transfer area between a refrigerant pipe and a corrugated fin. A heat exchanger is arranged in a refrigerant pipe formed with a plurality of stages by being bent in a meandering manner, and a plurality of stages formed in the refrigerant pipe, and each of the plurality of stages is arranged in each stage. A plurality of corrugated fins through which refrigerant pipes are inserted, and each corrugated fin of each of the plurality of corrugated fins is a member provided in insertion holes 131f and 132f through which the refrigerant pipes of the corrugated fins are inserted. For example, collars 133f and 134f which are members for bringing the refrigerant pipe into surface contact with the fins are provided. [Selection] Figure 4

Description

  The present invention relates to a heat exchanger, a manufacturing method thereof, and a heat radiator.

  Orientation of a small chamber in which a plurality of corrugated fins formed by bending a thin plate into a corrugated shape so that the holes provided in the vertical wall of the fin are located on the same straight line are formed in the straight portion of the meandering pipe by the flat portion and the bent portion of the corrugated fin There is known a heat exchanger in which these are matched (for example, see Patent Document 1).

JP-A-9-105566

  Here, in the heat exchanger, when the refrigerant pipe is inserted into the insertion hole with the insertion hole only in the corrugated fin, the refrigerant pipe and the corrugated fin are in line contact and the heat transfer area is reduced. Heat transfer performance is not improved because it cannot be increased.

  An object of the present invention is to improve heat transfer performance by increasing a heat transfer area between a refrigerant pipe and a corrugated fin in a heat exchanger. Moreover, in the heat dissipating body formed by combining a plurality of heat dissipating fins, the heat dissipating performance is improved by increasing the area of each heat dissipating fin in contact with the air. Furthermore, in heat exchangers, when the heat transfer area is increased as a radiator, water droplets generated on the surface of adjacent radiator fins at the time of defrosting are reduced by reducing the overlap of the radiator fins on the adjacent surfaces of adjacent radiators. It starts to flow well.

  For this purpose, the present invention is arranged in a refrigerant pipe formed with a plurality of stages by being bent in a meandering manner, and each of the plurality of stages formed in the refrigerant pipe, and each of the plurality of stages is provided. A heat exchanger comprising: a plurality of radiators each having a refrigerant pipe inserted through each of the stages. Further, the present invention provides a refrigerant pipe formed in a plurality of stages by being bent in a meandering manner, and a plurality of stages formed in the refrigerant pipe, and a refrigerant pipe is provided in each of the plurality of stages. A plurality of corrugated fins (heat radiating bodies) inserted therein, each corrugated fin of the plurality of corrugated fins being a member provided in an insertion hole through which a refrigerant pipe of each corrugated fin is inserted, A heat exchanger having a contact member which is a member for bringing a refrigerant tube into surface contact is provided.

  Here, the contact member may be integrally formed in the insertion hole.

  The refrigerant pipe is in surface contact with the contact member by being expanded after being inserted into the insertion hole in a state having a diameter smaller than the diameter of the insertion hole of each corrugated fin of the plurality of corrugated fins. It may be. Further, the refrigerant pipe may be one in which the outer diameter of the portion that does not contact the contact member is larger than the outer diameter of the portion that contacts the contact member.

  In addition, the heat exchanger is configured such that the refrigerant pipe is expanded after the expansion of the refrigerant pipe with respect to the area of the portion subjected to the heat exchange effect by one of the refrigerant pipes in a plane substantially orthogonal to the refrigerant pipe of each corrugated fin of the plurality of corrugated fins. The area ratio may be 0.02 or more and less than 0.1.

  Further, the plurality of corrugated fins include a first corrugated fin having a first inter-fin distance and a second corrugated fin having a second inter-fin distance that is longer than the first inter-fin distance. It may be. In that case, a 1st corrugated fin is arrange | positioned in the downstream stage of the flow of the air produced | generated by the ventilation fan among the several stages formed in the refrigerant pipe, and a 2nd corrugated fin is an refrigerant pipe. Of the plurality of stages formed, the stage may be arranged at a stage upstream of the air flow. The first inter-fin distance and the second inter-fin distance may be 3 mm or more and 20 mm or less.

  Furthermore, each corrugated fin of the plurality of corrugated fins includes a first plane substantially orthogonal to the refrigerant pipe, a second plane adjacent to the first plane and substantially orthogonal to the refrigerant pipe, and a first plane. Adjacent to the second plane on the opposite side and bridging between the third plane, which is substantially orthogonal to the refrigerant pipe, and the first plane and the second plane, the flow of air generated by the blower fan is approximately The first bridging portion parallel to the second bridging portion is bridged between the second plane and the third plane on the opposite side of the refrigerant pipe from the first bridging portion, and is substantially parallel to the air flow. It may be included. In that case, at least one of the first bridging portion and the second bridging portion may be recessed in the direction of the refrigerant pipe. Further, at least one of the first bridging portion and the second bridging portion may be cut and raised in the direction of the refrigerant pipe in the direction of air flow.

  The plurality of corrugated fins includes a first corrugated fin disposed at a first position shifted in a depth direction of the plurality of corrugated fins from the central axis of the air flow path generated by the blower fan, and It may include a second corrugated fin disposed at a second position shifted in the direction opposite to the depth direction of the plurality of corrugated fins from the central axis of the flow path. In that case, the first position is a position when the first corrugated fin contacts the wall surface in the depth direction of the duct forming the air flow path, and the second position is the second corrugated fin of the duct. It may be a position when contacting the wall surface in the direction opposite to the depth direction. Further, the difference between the length in the depth direction of the duct and the length in the depth direction of the plurality of corrugated fins is t, the length in the width direction of the bridging portion that bridges the fins in the plurality of corrugated fins is W, and the wall surface of the duct Where the heat transfer coefficient at h1 is h1 and the heat transfer coefficient at the position where the distance from the wall of the duct is t2 is h2, the condition of t / W <(2 × h2−h1) / {2 × (h1 + h2)} May be satisfied.

  Furthermore, each corrugated fin of the plurality of corrugated fins has a notch on the downstream side of the air flow generated by the blower fan, the refrigerant pipe has a flat shape, and each corrugated fin of the plurality of corrugated fins It may be press-fitted into the notch portion. In this case, when the width in the direction parallel to the air flow in the cross section of the refrigerant pipe is A and the width in the direction perpendicular to the air flow in the cross section of the refrigerant pipe is B, the condition of A / B> 1 is satisfied. It can be satisfied.

  Furthermore, the heat exchanger may be one in which two or more corrugated fins are arranged in the depth direction.

  Furthermore, when the area where the fins of the corrugated fins of the plurality of corrugated fins are in contact with the refrigerant pipe is S1, and the area of the refrigerant pipe between the corrugated fins of the plurality of corrugated fins is S2, S2 / S1 May be 0 or more and 40 or less.

  On the other hand, the present invention provides a manufacturing step for manufacturing a plurality of corrugated fins, an insertion step for inserting a refrigerant pipe through the plurality of corrugated fins, a plurality of stages formed in the refrigerant pipe, and a plurality of corrugated fins in the plurality of stages. Each of a plurality of stages, and a bending step of bending the refrigerant pipe in a meandering manner so that the refrigerant pipe is inserted into each corrugated fin of the plurality of corrugated fins. There is also provided a method for manufacturing a heat exchanger in which a contact member for bringing a refrigerant pipe into surface contact with each corrugated fin of the fin is formed in an insertion hole through which the refrigerant pipe of each corrugated fin is inserted.

  Further, the present invention is a radiator that dissipates heat generated from a refrigerant pipe of a heat exchanger, wherein the radiator includes a plurality of heat dissipating fins arranged side by side on the refrigerant pipe, and each heat dissipating fin is attached to the refrigerant pipe. Provided is a heat radiator characterized by comprising a pair of heat radiating plates to be inserted and an expansion plate spanned between the pair of heat radiating plates.

  Here, in the radiator, adjacent radiating fins are arranged such that the expansion plate of the one radiating fin is disposed on one side of the refrigerant tube, and the expansion plate of the other radiating fin is opposite to the one side of the refrigerant tube. It may be configured to be arranged in In that case, the adjacent radiating fins may be arranged so as to partially face each other's expansion plates, and the adjacent radiating fins are arranged so as not to face each other's expansion plates. It may be a thing.

  Further, the heat dissipating body includes a heat dissipating plate in which each adjacent heat dissipating fin is disposed on the other heat dissipating fin side of the one heat dissipating fin, and a heat dissipating member disposed on the one heat dissipating fin side of the other heat dissipating fin. The board may be arranged at equal intervals.

  In addition, the present invention provides a refrigerant pipe in which a plurality of stages are formed by being bent in a meandering manner, and a heat dissipating body through which air generated by a blower fan is disposed at each of the stages formed in the refrigerant pipe. And a heat dissipating member in which the adjacent heat dissipating fins are arranged so as not to oppose each other's expansion plate is arranged on the upstream side of the air flow, and downstream of the air flow A heat exchanger is provided in which a heat dissipating member in which the adjacent heat dissipating fins are disposed so as to partially face each other's expansion plates is disposed on a side step.

  Further, the present invention is a radiator that dissipates heat generated from a refrigerant tube of a heat exchanger, wherein the radiator includes a plurality of heat dissipating fins arranged side by side on the refrigerant tube, and each heat dissipating fin includes a refrigerant tube. There is provided a heat radiating body comprising: a heat radiating plate inserted through the heat radiating plate; and an expansion plate extending from the heat radiating plate along the refrigerant pipe.

  Here, the adjacent radiating fins may extend the extension plates in the same direction, and may arrange the extension plates on the opposite side with the refrigerant pipe interposed therebetween.

  In addition, the present invention includes a refrigerant pipe formed with a plurality of stages by being bent in a meandering manner, and a heat dissipator disposed on each of the stages formed in the refrigerant pipe. A plurality of heat radiating plates inserted through the refrigerant pipe, and an expansion plate extending along a surface adjacent to the heat radiating body disposed in the adjacent stage, and connected to any one of the heat radiating plates, Provided is a heat exchanger in which the heat dissipating members arranged in the adjacent steps are arranged so as not to overlap part or all of the mutual expansion plates arranged on the adjacent surfaces.

  According to the present invention, in the heat exchanger, the heat transfer performance can be improved by increasing the heat transfer area between the refrigerant pipe and the corrugated fin. Moreover, according to this invention, in the thermal radiation body formed combining several thermal radiation fin, the thermal radiation performance is improved by extending the surface which contacts air. Furthermore, according to the present invention, in the heat exchanger, when the heat transfer area is increased as a radiator, by reducing the overlap of the radiator fins on the adjacent surfaces of the adjacent radiators, the adjacent radiator fins at the time of defrosting can be reduced. Water droplets generated on the surface will flow down efficiently.

It is a whole block diagram of the heat exchanger in the 1st Embodiment of this invention. It is the figure which showed the structure of the 1st step | paragraph corrugated fin of the heat exchanger in the 1st Embodiment of this invention. It is the figure which showed the structure of the 6th step | paragraph corrugated fin of the heat exchanger in the 1st Embodiment of this invention. FIG. 3 is an enlarged view of a part of a sixth-stage corrugated fin of the heat exchanger in the first embodiment of the present invention. It is a figure for demonstrating the relationship between the area of the orthogonal surface of the corrugated fin of the heat exchanger in embodiment of this invention, and the cross-sectional area of a refrigerant pipe. It is the figure which showed the manufacturing method of the heat exchanger in the 1st Embodiment of this invention. It is the figure which showed the structure of the corrugated fin of the heat exchanger in the 2nd Embodiment of this invention. It is the figure which showed the structure of the corrugated fin of the heat exchanger in the 3rd Embodiment of this invention. It is the figure which showed the structure of the heat exchanger in the 1st Embodiment of this invention for the comparison with the heat exchanger in the 4th Embodiment of this invention. It is sectional drawing of the corrugated fin in the 1st Embodiment of this invention for the comparison with the corrugated fin in the 4th Embodiment of this invention. It is the figure which showed the structure of the heat exchanger in the 4th Embodiment of this invention. It is sectional drawing of the corrugated fin in the 4th Embodiment of this invention. It is the graph which showed the result of having verified the heat exchange performance of the heat exchanger in the 1st and 4th embodiment of this invention. (A) is the figure which showed the structure of the heat exchanger in the 5th Embodiment of this invention, (b) is sectional drawing of the heat exchanger in the 5th Embodiment of this invention. It is the figure which showed the definition of the flat direction of the refrigerant pipe which is a flat pipe in the 5th Embodiment of this invention. It is the figure which showed the result of having verified the heat exchange performance of the heat exchanger when a refrigerant | coolant pipe | tube is a round tube and it is a flat tube. It is the graph which showed the difference in the heat exchange performance of the heat exchanger when a refrigerant | coolant pipe | tube is a round tube and it is a flat tube. It is the figure which showed the structure of the heat exchanger in the 6th Embodiment of this invention. It is a figure for demonstrating the relationship between the area which the fin of the corrugated fin and refrigerant pipe of the heat exchanger in the 7th Embodiment of this invention contact, and the area of the refrigerant pipe between fins. It is the figure which showed typically the heat radiator in the 8th Embodiment of this invention. It is the figure which showed typically the heat radiator in the 9th Embodiment of this invention. It is the figure which showed typically the heat radiator in the 10th Embodiment of this invention. It is the figure which showed typically the heat exchanger in the 11th Embodiment of this invention. It is the figure which showed typically the heat exchanger in the 12th Embodiment of this invention.

  [Outline of First to Seventh Embodiments] In the first to seventh embodiments of the present invention, heat is exchanged between a refrigerant compressed and circulated by a compressor and air blown by a blower fan. In the exchanger, by using an independent substantially rectangular corrugated fin, the assembly and reliability of the heat exchanger are improved, and the heat transfer performance is improved by increasing the heat transfer area.

  Further, by combining independent substantially rectangular corrugated fins having different fin-to-fin distances, it is possible to arbitrarily set the optimum heat exchanger configuration according to the applied device and part.

  Furthermore, by using a flat refrigerant pipe, the wind loss is reduced and the heat exchange performance is improved.

  1ST EMBODIMENT FIG. 1: is a whole block diagram of the heat exchanger 1 in 1st Embodiment. As illustrated, the heat exchanger 1 according to the first embodiment includes corrugated fins 10a, 10b, 10c, 10d, 10e, and 10f, a refrigerant pipe 20, and end plates 30 and 40.

  The corrugated fins 10a, 10b, 10c, 10d, 10e, and 10f are mutually independent corrugated fins, and are the first stage, the second stage, the third stage, the fourth stage, the fifth stage, and the sixth stage of the heat exchanger 1. One corrugated fin arranged in each eye. Details of the corrugated fins 10a, 10b, 10c, 10d, 10e, and 10f will be described later.

  The refrigerant pipe 20 is a pair of pipes through which the refrigerant flows. The pair of pipes are bent in a meandering manner and inserted through the corrugated fins 10a, 10b, 10c, 10d, 10e, and 10f. That is, the pair of pipes are inserted into the corrugated fins 10a, then bent into a U shape, inserted into the corrugated fins 10b, and then inserted into the corrugated fins 10c, 10d, and 10e in the same manner. Finally, the pair of pipes are inserted into the corrugated fins 10f and then joined together by a U-shaped pipe. Thereby, the refrigerant flows into one of the pair of pipes, flows through the heat exchanger 1, and then flows out from the other of the pair of pipes. The refrigerant pipe 20 is closely fixed to the corrugated fins 10a, 10b, 10c, 10d, 10e, and 10f by expanding the pipe.

  The end plate 30 includes a U-shaped portion of the refrigerant tube 20 between the corrugated fins 10a and 10b, a U-shaped portion of the refrigerant tube 20 between the corrugated fins 10c and 10d, and a refrigerant tube between the corrugated fins 10e and 10f. The 20 U-shaped portion is a plate material provided to suppress spreading due to stress.

  The end plate 40 is for suppressing the U-shaped portion of the refrigerant tube 20 between the corrugated fins 10b and 10c and the U-shaped portion of the refrigerant tube 20 between the corrugated fins 10d and 10e from spreading due to stress. It is the provided board | plate material.

  In addition, the heat exchanger 1 shall receive the flow of air in the direction shown by the arrow 50 from the fan which is not shown in figure.

  Next, the corrugated fins 10a, 10b, 10c, 10d, 10e, and 10f shown in FIG. 1 will be described in detail.

  FIG. 2 is a diagram showing the configuration of the corrugated fin 10a.

  As shown in the figure, the corrugated fin 10a includes an aluminum flat plate, an orthogonal surface 11a substantially orthogonal to the refrigerant tube 20, a flat peak surface 12a, an orthogonal surface 13a substantially orthogonal to the refrigerant tube 20, and a flat valley surface 14a. It is formed by bending to repeat. In the present embodiment, the corrugated fin 10a is provided as an example of the first corrugated fin. Moreover, the orthogonal surface 11a is provided as an example of the first plane, the orthogonal surface 13a is provided as an example of the second plane, and the orthogonal surface is orthogonal to the opposite side of the orthogonal surface 11a as an example of the third plane. An orthogonal surface that is adjacent to the surface 13a and substantially orthogonal to the refrigerant pipe 20 is provided. Furthermore, as an example of a first bridging portion that bridges between the first plane and the second plane, a mountain surface 12a is provided, and a second bridge that bridges between the second plane and the third plane is provided. As an example of the two bridging portions, a trough surface 14a is provided. Here, since the orthogonal surface 11a and the mountain surface 12a, the mountain surface 12a and the orthogonal surface 13a, and the orthogonal surface 13a and the valley surface 14a are substantially perpendicular to each other, the corrugated fin 10a is bent into a substantially rectangular shape. It is a thing. In FIG. 2, the distance (inter-fin distance) between the orthogonal surface 11a and the orthogonal surface 13a is 5 mm. The distance between the orthogonal surface 11a and the orthogonal surface 13a is an example of a first inter-fin distance.

  Further, the orthogonal surface 11a has an insertion hole 111a through which one of the pair of pipes of the refrigerant pipe 20 is inserted, and an insertion hole 112a through which the other of the pair of pipes of the refrigerant pipe 20 is inserted. Further, the orthogonal surface 13a includes an insertion hole 131a through which one of the pair of pipes of the refrigerant pipe 20 is inserted and an insertion hole 132a through which the other of the pair of pipes of the refrigerant pipe 20 is inserted. The insertion holes 131a and 132a do not appear in the drawing.

  The corrugated fins 10b, 10c, 10d, and 10e have the same configuration as that of the corrugated fin 10a, and a description thereof will be omitted.

  FIG. 3 is a diagram showing the configuration of the corrugated fin 10f.

  As shown in the figure, the corrugated fin 10f includes an aluminum flat plate, an orthogonal surface 11f that is substantially orthogonal to the refrigerant tube 20, a flat peak surface 12f, an orthogonal surface 13f that is approximately orthogonal to the refrigerant tube 20, and a flat valley surface 14f. It is formed by bending to repeat. In the present embodiment, a corrugated fin 10f is provided as an example of the second corrugated fin. In addition, an orthogonal surface 11f is provided as an example of the first plane, an orthogonal surface 13f is provided as an example of the second plane, and an orthogonal surface is provided on the opposite side of the orthogonal surface 11f as an example of the third plane. An orthogonal surface that is adjacent to the surface 13f and substantially orthogonal to the refrigerant pipe 20 is provided. Further, as an example of a first bridging portion that bridges between the first plane and the second plane, a mountain surface 12f is provided, and a second bridge that bridges between the second plane and the third plane is provided. As an example of the two bridging portions, a valley surface 14f is provided. Here, since the orthogonal surface 11f and the mountain surface 12f, the mountain surface 12f and the orthogonal surface 13f, and the orthogonal surface 13f and the valley surface 14f are substantially perpendicular to each other, the corrugated fin 10f is bent into a substantially rectangular shape. It is a thing. In FIG. 3, the distance (inter-fin distance) between the orthogonal surface 11f and the orthogonal surface 13f is 10 mm. The distance between the orthogonal surface 11f and the orthogonal surface 13f is an example of a second inter-fin distance.

  Further, the orthogonal surface 11f has an insertion hole 111f through which one of the pair of pipes of the refrigerant pipe 20 is inserted, and an insertion hole 112f through which the other of the pair of pipes of the refrigerant pipe 20 is inserted. Further, the orthogonal surface 13f has an insertion hole 131f through which one of the pair of pipes of the refrigerant pipe 20 is inserted, and an insertion hole 132f through which the other of the pair of pipes of the refrigerant pipe 20 is inserted.

  2 and 3 show the case where the distance between the fins is 5 mm and 10 mm, the present invention is not limited to this. For example, when using the heat exchanger 1 as an evaporator, the distance between fins should just be 3 mm or more and 20 mm or less. When the distance between the fins is less than 3 mm, it cannot be used as an evaporator in consideration of frost clogging between the fins. When the distance between the fins exceeds 20 mm, the fins are increased in size to ensure heat exchange performance. Because it becomes impractical.

  Next, the corrugated fins 10a, 10b, 10c, 10d, 10e, and 10f shown in FIGS. 2 and 3 will be described in more detail.

  FIG. 4 is an enlarged view of a part of the corrugated fin 10f. As shown in the drawing, in the insertion holes 111f and 112f of the orthogonal surface 11f of the corrugated fin 10f, collars 113f and 114f as examples of contact members for bringing the pair of pipes of the refrigerant pipe 20 into surface contact with the corrugated fin 10f, respectively. Is provided. In addition, the insertion holes 131f and 132f of the orthogonal surface 13f of the corrugated fin 10f are provided with collars 133f and 134f as examples of contact members for bringing the pair of pipes of the refrigerant pipe 20 into surface contact with the corrugated fin 10f. ing. However, here, since it is assumed that the flat plate is bent into a substantially rectangular shape with the collars 113f, 114f, 133f, and 134f formed on one side, only the collars 133f and 134f appear in the drawing.

  The corrugated fins 10a, 10b, 10c, 10d, and 10e are also provided with a collar as an example of a contact member, but the description is omitted because it is similar to the corrugated fin 10f.

  Next, the relationship between the area of the orthogonal surface 11 of the corrugated fin 10 and the cross-sectional area of the refrigerant pipe 20 will be described. In the following, the corrugated fins 10a, 10b, 10c, 10d, 10e, and 10f are referred to as corrugated fins 10 without being distinguished from each other.

  FIG. 5 is a view for explaining the relationship between the area of the orthogonal surface 11 of the corrugated fin 10 and the cross-sectional area of the refrigerant pipe 20. As shown in the drawing, the outer diameter of the expanded refrigerant pipe 20 is 8.5 mm. For example, the refrigerant tube 20 having an outer diameter of 8.0 mm may be expanded to 8.5 mm. The lengths of the two sides of the orthogonal plane 11 are 28 mm and 60 mm. Then, the cross-sectional area A of the refrigerant pipe 20 after the expansion is 56.7 mm 2 (= π × (8.5 mm / 2) 2). On the other hand, the area B of the portion that receives the heat exchange effect of one of the refrigerant tubes 20 in the orthogonal plane 11 is 840 mm 2 (= (28 mm × 60 mm) / 2). Therefore, the ratio A / B of A to B is 0.0675 (= 56.7 mm2 / 840 mm2), and is set to satisfy 0.02 ≦ A / B <0.1.

  If A / B is less than 0.02, the outer diameter (and inner diameter) of the refrigerant pipe 20 becomes extremely small with respect to the area of the orthogonal plane 11. For example, as shown in FIG. 5, if the lengths of the two sides of the orthogonal plane 11 are 28 mm and 60 mm, the outer diameter of the expanded refrigerant pipe 20 is 4 if A / B is less than 0.02. The outer diameter of the refrigerant pipe 20 before expansion is less than about 4.5. Therefore, the expansion of the refrigerant pipe 20 becomes very difficult.

  Further, when A / B is 0.1 or more, the area of the orthogonal plane 11 is too small with respect to the refrigerant pipe 20. For example, as shown in FIG. 5, if the outer diameter of the refrigerant pipe 20 after expansion is 8.5 mm and the length of the vertical side of the orthogonal surface 11 is 28 mm, A / B is 0.1 or more. The length of the horizontal side of the orthogonal surface 11 is 40 mm or less. Accordingly, sufficient heat exchange performance cannot be obtained, which is not practical.

  Next, a method for manufacturing the heat exchanger 1 in the first embodiment will be described.

  FIG. 6 is a diagram illustrating a method for manufacturing the heat exchanger 1 according to the first embodiment. However, this manufacturing method is merely an example, and any manufacturing method may be adopted as long as the heat exchanger 1 described with reference to FIGS. 1 to 4 can be obtained as a result. Moreover, a part or all of this manufacturing method may be performed using a machine.

  First, in the fin manufacturing process, first, through holes 601 are made in the flat plate 60 by the molds 611 and 612 (step 101). Next, the collar 602 is molded by raising the peripheral portion of the insertion hole 601 of the flat plate 60 with the molds 621 and 622 (step 102). Next, the flat plate 60 is bent into a substantially rectangular shape (also called a pulse shape) by the molds 631 and 632 (step 103). Then, the corrugated fin 10 shown in FIG. 2 or 3 is completed (step 104). Here, since it is assumed that the heat exchanger 1 shown in FIG. 1 is manufactured, it is assumed that six corrugated fins 10 are manufactured.

  Secondly, in the refrigerant tube inserting and expanding step, first, the manufacturer manually inserts the corrugated fins 10 into the fin holding jig 64 one by one (step 201). In the drawing, only one state where one corrugated fin 10 is inserted into one fin holding jig 64 is shown. However, when six corrugated fins 10 are manufactured in the fin manufacturing process, Each of the corrugated fins 10 is inserted into each of the six fin holding jigs 64. Next, the refrigerant pipe 20 is inserted into the fin holding jig 64 (step 202). Although only the state in which the refrigerant tube 20 is inserted into one fin holding jig 64 is shown in the figure, when six corrugated fins 10 are manufactured in the fin manufacturing process, they are arranged in a line. The refrigerant pipe 20 is inserted into the six fin holding jigs 64. At this time, the corrugated fin 10 and the refrigerant pipe 20 are not in close contact with each other, but then the corrugated fin 10 and the refrigerant pipe 20 are in close contact with each other by the pipe expansion jig 65 being expanded. (Step 203). In the figure, only a state where one corrugated fin 10 is brought into close contact with one refrigerant pipe 20 is shown. However, when six corrugated fins 10 are manufactured in the fin manufacturing process, six corrugated fins 10 are manufactured. The corrugated fins 10 are brought into close contact with one refrigerant pipe 20 at the same time.

  Thirdly, in the refrigerant pipe bending process, the refrigerant pipe 20 is bent so that a bent portion is formed in the lower part of the figure in a state where the refrigerant pipe 20 is inserted into and closely attached to the corrugated fin 10 (step 301). At the same time, it is bent so that a bent portion is formed in the upper part of the figure (step 302). Note that the bending in step 301 and the bending in step 302 may be performed simultaneously.

  And as shown to the last process, the heat exchanger 1 is completed.

  Thus, in 1st Embodiment, the fin of each step of the heat exchanger 1 was made into the substantially rectangular corrugated fin 10 which became independent. Thereby, the heat transfer area can be expanded within the same occupied volume, and the heat exchange performance can be improved. In addition, a large number of fins can be integrated into one corrugated fin 10.

  Further, since the corrugated fin 10 having a substantially rectangular shape is independent at each stage, it is possible to adopt a manufacturing method similar to that for inserting the fins one by one into the jig. On the other hand, the trouble of inserting the fins into the jig one by one is saved, leading to a reduction in manufacturing time.

  Furthermore, since the number of parts constituting the heat exchanger 1 is also greatly reduced, the parts management can be improved.

  In the first embodiment, the collars 113, 114, 133, and 134 are integrally formed in the insertion holes 111, 112, 131, and 132 of the corrugated fin 10. When the refrigerant pipe 20 is inserted through the insertion holes 111, 112, 131, 132 with only the insertion holes 111, 112, 131, 132 opened in the corrugated fin 10, the refrigerant pipe 20, the corrugated fin 10, In the first embodiment, heat transfer is performed in a surface contact between the refrigerant pipe 20 and the corrugated fin 10, and the refrigerant pipe 20 and the corrugated fin 10 are in the first embodiment. The heat transfer area can be increased, and the heat transfer performance is improved.

  Furthermore, in the first embodiment, the refrigerant pipe 20 is inserted into the insertion holes 111, 112, 131, 132 with a diameter smaller than the diameter of the insertion holes 111, 112, 131, 132 of the corrugated fin 10. After that, it was expanded. Thereby, compared with press-fitting the refrigerant pipe 20 having a diameter larger than the diameter of the insertion holes 111, 112, 131, 132, the adhesiveness is excellent, so that the heat transfer performance is improved, and thus heat exchange. This leads to improved performance.

  Furthermore, since the substantially rectangular corrugated fins 10 are independent at each stage, it is possible to easily vary the distance between the fins partially at a low cost in accordance with the intended use and applicable model. For example, in the case of a refrigerator or the like, condensation or freezing is likely to occur on the windward side, and as a result, the flow of the wind is hindered and the heat exchange performance may be deteriorated. Therefore, it is possible to prevent performance degradation by making the distance between fins on the leeward side longer than the distance between fins on the leeward side.

  [Second Embodiment] The heat exchanger 1 in the second embodiment is the heat in the first embodiment, except that the number of pipes of the refrigerant pipe 20 inserted through the corrugated fins 70 is one. Since it is the same as the exchanger 1, the description thereof is omitted, and here, only the corrugated fin 70 in the second embodiment will be described.

  FIG. 7 is a diagram showing the configuration of the corrugated fin 70 in the second embodiment.

  As shown in the drawing, the corrugated fin 70 according to the second embodiment includes an aluminum flat plate, an orthogonal surface 71 that is substantially orthogonal to the refrigerant pipe 20, a crest surface 72, an orthogonal surface 73 that is substantially orthogonal to the refrigerant pipe 20, and a valley. The surface 74 is formed by being bent so as to be repeated. In the present embodiment, the orthogonal plane 71 is provided as an example of the first plane, the orthogonal plane 73 is provided as an example of the second plane, and the orthogonal plane 71 is set as an example of the third plane. On the opposite side, an orthogonal surface that is adjacent to the orthogonal surface 73 and substantially orthogonal to the refrigerant pipe 20 is provided. Furthermore, as an example of a first bridging portion that bridges between the first plane and the second plane, a mountain surface 72 is provided, and a second bridge that bridges between the second plane and the third plane is provided. A valley surface 74 is provided as an example of the two bridging portions. Here, since the orthogonal surface 71 and the mountain surface 72, the mountain surface 72 and the orthogonal surface 73, and the orthogonal surface 73 and the valley surface 74 are substantially perpendicular to each other, the corrugated fin 70 is bent into a substantially rectangular shape. It is a thing.

  The orthogonal surface 71 has an insertion hole 711 through which the refrigerant tube 20 is inserted, and the orthogonal surface 73 has an insertion hole 731 through which the refrigerant tube 20 is inserted. Furthermore, although an enlarged view is not shown, also in the second embodiment, the insertion holes 711 and 731 are each provided with a collar as an example of a contact member.

  In addition, in the second embodiment, a substantially M-shaped portion 721 is provided on the mountain surface 72 and a substantially M-shaped portion 741 is provided on the valley surface 74. Alternatively, a substantially M-shaped portion may be provided on one of the mountain surface 72 and the valley surface 74.

  Thus, in the second embodiment, at least one of the peak surface 72 and the valley surface 74 is recessed in the direction of the refrigerant pipe 20. Thereby, it becomes possible to increase a heat-transfer area rather than the corrugated fin 10 in 1st Embodiment, and the improvement of heat exchange performance can be anticipated. Moreover, since the performance of the heat exchanger 1 is improved while ensuring a certain distance between the fins, there is little performance degradation due to frost clogging between the fins due to frost formation when used as an evaporator.

  [Third Embodiment] The heat exchanger 1 in the third embodiment also has the heat in the first embodiment except that the number of pipes of the refrigerant pipe 20 inserted through the corrugated fins 80 is one. Since it is the same as the exchanger 1, the description is omitted, and only the corrugated fin 80 in the third embodiment will be described here.

  FIG. 8 is a diagram showing the configuration of the corrugated fin 80 according to the third embodiment.

  As shown in the figure, the corrugated fin 80 according to the third embodiment includes an aluminum flat plate, an orthogonal surface 81 that is substantially orthogonal to the refrigerant tube 20, a flat peak surface 82, and an orthogonal surface 83 that is approximately orthogonal to the refrigerant tube 20. The flat valley surface 84 is bent so as to be repeated. In the present embodiment, the orthogonal plane 81 is provided as an example of the first plane, the orthogonal plane 83 is provided as an example of the second plane, and the orthogonal plane 81 is set as an example of the third plane. On the opposite side, an orthogonal surface that is adjacent to the orthogonal surface 83 and substantially orthogonal to the refrigerant pipe 20 is provided. Further, as an example of a first bridging portion that bridges between the first plane and the second plane, a mountain surface 82 is provided, and a second bridge that bridges between the second plane and the third plane is provided. A valley surface 84 is provided as an example of the two bridging portions. Here, since the orthogonal surface 81 and the mountain surface 82, the mountain surface 82 and the orthogonal surface 83, and the orthogonal surface 83 and the valley surface 84 are substantially perpendicular, the corrugated fin 80 is bent into a substantially rectangular shape. It is a thing.

  The orthogonal surface 81 has an insertion hole 811 through which the refrigerant tube 20 is inserted, and the orthogonal surface 83 has an insertion hole 831 through which the refrigerant tube 20 is inserted. Furthermore, although an enlarged view is not shown, also in the third embodiment, the insertion holes 811 and 831 are each provided with a collar as an example of a contact member.

  In addition, in the third embodiment, a louver (cut and raised) 821 is provided on the mountain surface 82 and a louver 841 is provided on the valley surface 84. Alternatively, a louver may be provided on one of the mountain surface 82 and the valley surface 84.

  As described above, in the third embodiment, at least one of the peak surface 82 and the valley surface 84 is cut up in the direction of the refrigerant pipe 20 in the direction of the air flow. Thereby, it becomes possible to make the air which passes the heat exchanger 1 turbulent, and the improvement of heat exchange performance can be anticipated.

  [Fourth Embodiment] FIG. 9 is a diagram showing a structure of a heat exchanger 1 in the first embodiment for comparison with the heat exchanger 1 in the fourth embodiment. As illustrated, the heat exchanger 1 in the first embodiment includes corrugated fins 10 a to 10 m and a refrigerant pipe 20.

  The corrugated fins 10a to 10m are multi-stage corrugated fins that are in thermal contact with the refrigerant pipe 20 and exchange heat with air. In FIG. 1, the number of corrugated fins 10 is six, but in FIG. 9, the number of corrugated fins 10 is 13, and thus corrugated fins 10 a to 10 m are shown.

  The refrigerant pipe 20 is a pipe through which the refrigerant flows. In FIG. 1, the refrigerant pipe 20 is a pair of pipes, but in FIG. 9, the refrigerant pipe 20 is a single pipe.

  In the heat exchanger 1, it is assumed that there is an air flow in a direction indicated by an arrow 50 from a fan (not shown).

  By the way, heat transfer between the fin and air is performed by forced convection heat transfer. Since the forced convection heat transfer coefficient (hereinafter also simply referred to as “heat transfer coefficient”) is generally proportional to the Reynolds number to the 0.8th power, the higher the air velocity, the higher the heat transfer coefficient. The velocity of air is zero on the duct wall surface, which is a stationary wall, increases from the duct wall surface toward the center of the duct, and is highest at the center of the duct. Accordingly, the heat transfer coefficient in the fins of the heat exchanger 1 is also different between the center of the duct and the vicinity of the duct wall surface, and is low near the duct wall surface.

  In addition, the forced convection heat transfer coefficient is greatly affected by the temperature boundary layer generated between the air and the fin surface. The temperature boundary layer is generated when the temperature of the air decreases due to contact between the air and the fins. The temperature boundary layer is theoretically zero in thickness where air and fin first contact, and increases in thickness as it flows downstream. On the upstream side, heat exchange is increased because air and fins exchange heat with a thin temperature boundary layer interposed therebetween. On the other hand, on the downstream side, heat exchange is performed with a thick boundary layer interposed therebetween, so that the heat transfer coefficient is low. The improvement in heat transfer performance that occurs at the part where air and fins first collide in this way is said to be the “leading edge effect”. In order to improve the heat exchange performance in the heat exchanger 1, it is essential to effectively utilize this leading edge effect.

  FIG. 10 is an enlarged view of a part of the corrugated fin 10 according to the first embodiment. As shown in the figure, the corrugated fin 10 according to the first embodiment has a structure in which adjacent ones of independent fins are connected to each other. That is, the corrugated fin 10 includes, in addition to the orthogonal surface 11, the mountain surface 12, the orthogonal surface 13 and the valley surface 14 shown in FIGS. 2 and 3, the orthogonal surface 15, the mountain surface 16, the orthogonal surface 17 and A trough 18 is provided. However, in the present embodiment, the orthogonal surfaces 11, 13, 15, and 17 corresponding to one independent fin are called the expanded heat transfer surfaces 11, 13, 15, and 17, respectively, and the expanded heat transfer surface. The mountain surface 12, the valley surface 14, the mountain surface 16, and the valley surface 18 that connect 11, 13, 15, 17, etc. will be referred to as the coupling surfaces 12, 14, 16, and 18. In this Embodiment, the connection surfaces 12, 14, 16, and 18 are provided as an example of the bridge | crosslinking part which bridge | crosslinks between fins.

  In FIG. 10, D is the depth of the duct (the depth of the corrugated fin 10), H is the height of the corrugated fin 10, and W is the connection length (the air flow of the connection surfaces 12, 14, 16, 18). The length of the side perpendicular to the flow direction).

  Although not shown in FIG. 10, insertion holes are formed in the enlarged heat transfer surfaces 11, 13, 15, and 17, and the refrigerant pipe 20 is inserted into the insertion holes. Specifically, by inserting a mandrel having a diameter larger than the inner diameter of the refrigerant tube 20 into the refrigerant tube 20 and expanding the diameter of the refrigerant tube 20, the refrigerant tube 20 and the expanded heat transfer are expanded. The surfaces 11, 13, 15, 17 can be brought into thermal contact. At that time, since the connection surfaces 12, 14, 16, and 18 connect the expanded heat transfer surfaces 11, 13, 15, and 17, the distance between the adjacent expanded heat transfer surfaces 11, 13, 15, and 17 is maintained. This eliminates the need for a jig for adjusting the fin pitch.

  Moreover, in the heat exchanger 1 used as the evaporator for refrigerators, in order to enlarge the refrigerator internal volume, the thickness of the heat exchanger 1 in the depth direction of a refrigerator is suppressed to about 40 mm to 70 mm, for example. Further, the height of the corrugated fins 10 is set to 28 mm, for example, and the corrugated fins 10 are stacked in the flow direction of the air flowing through the ducts to secure a heat transfer area. Furthermore, a gap of, for example, about 2 mm is provided between adjacent corrugated fins 10.

  FIG. 11 is a diagram showing the structure of the heat exchanger 1 in the fourth embodiment. As shown in the drawing, the corrugated fin 10 in the fourth embodiment is formed by bending in a wave shape in the same manner as the corrugated fin 10 in the first embodiment. Similarly to FIG. 9, there is an air flow in a direction indicated by an arrow 50 from a fan (not shown). However, in the fourth embodiment, the depth of the corrugated fin 10 is shorter than the depth of the duct. In the figure, the corrugated fin 10 at the most upstream stage is installed so as to be in contact with the duct wall surface on the near side, and the corrugated fin 10 at the next stage is installed so as to be in contact with the duct wall surface on the back side. The third stage is installed on the front side, the fourth stage is on the back side, and so on.

  FIG. 12 is an enlarged view of a part of the corrugated fin 10 according to the fourth embodiment. As shown in the figure, the corrugated fin 10 according to the fourth embodiment is similar to the corrugated fin 10 according to the first embodiment, with the enlarged heat transfer surfaces 11, 13, 15, 17 and the connecting surfaces 12, 14, 16. , 18.

  In FIG. 12, D is the depth of the duct, H is the height of the corrugated fin 10, and W is the connection length (the side perpendicular to the air flow direction of the connection surfaces 12, 14, 16, 18). Length), and t is the difference between the depth of the duct and the depth of the corrugated fin 10.

  By the way, the heat exchange performance is represented by the product of the heat transfer area and the forced convection heat transfer coefficient. The range in which the heat exchange performance is improved in the fourth embodiment will be described below using a simple model. Here, the forced convection heat transfer coefficient at the duct wall surface is h1, and the forced convection heat transfer coefficient at a position t [mm] away from the duct is h2.

  Then, the product K1 of the forced convection heat transfer coefficient and the heat transfer area from a position t [mm] away from the duct of the corrugated fin 10 in the first embodiment to the duct wall surface is expressed by the following equation.

  K1 = h1 × W × H + {(h1 + h2) / 2} × 4t × H

  Thus, in 1st Embodiment, since the corrugated fin 10 is installed so that it may touch a duct wall surface, the surface where the corrugated fin 10 and a duct wall surface contact does not touch air, but is excluded from a heat-transfer area. Has been.

  On the other hand, the product K2 of the forced convection heat transfer coefficient and the heat transfer area from the position t [mm] away from the duct wall of the corrugated fin 10 in the fourth embodiment to the duct wall surface is expressed by the following equation. .

  K2 = h2 × 2W × H

  Since the heat exchange performance is improved when K2 is larger than K1, the conditions for improving the heat exchange performance are expressed by the following equations.

  K2−K1 = h2 × 2W × H−h1 × W × H − {(h1 + h2) / 2} × 4t × H> 0

  (2 × h2−h1) × W × H> (h1 + h2) × 2t × H

  t / W <(2 × h2−h1) / {2 × (h1 + h2)}

  If the air velocity on the duct wall surface is 0 and the forced convection heat transfer coefficient h1 on the duct wall surface is 0, the following condition is satisfied.

  t / W <1

  That is, if t <W, the heat exchange performance is improved.

  For example, when corrugated fins 10 having a depth D of 60 mm and a height H of 28 mm and a connection length W of 5 mm are arranged in steps, the depth of the corrugated fins 10 for improving heat exchange performance is as follows: Is calculated as follows.

  D-t = D-W = 60.0-5.0 = 55.0 [mm]

  Therefore, if the depth of the corrugated fin 10 is longer than 55 mm and shorter than 60 mm, the heat exchange performance is improved.

  FIG. 13 is a graph showing the results of verifying the heat exchange performance of the heat exchanger 1 in the first and fourth embodiments by simulation. As shown in the drawing, the heat exchange amount of the heat exchanger 1 in the first embodiment was 61.7 W. On the other hand, the heat exchange amount of the heat exchanger 1 to which the corrugated fin 10 having a depth shorter than the depth of the duct in the fourth embodiment is 64.4 W, and the heat exchange amount is increased by about 4.4%. Confirmed to do.

  Although the fourth embodiment has been described on the assumption of the structure shown in FIGS. 11 and 12, this is merely an example. For example, the corrugated fins 10 at each stage may be installed with a gap between the duct wall surfaces without being installed so as to be in contact with the duct wall surfaces. Further, the corrugated fins 10 at each stage are not installed so that the shifting directions are alternated between the front side and the back side, but one corrugated fin 10 is shifted to a position on the back side, and another corrugated fin 10 is placed. May be installed so as to be shifted to a position on the near side. In this case, a certain corrugated fin 10 is an example of a first corrugated fin, and a position on the far side is an example of a first position. Another corrugated fin 10 is an example of a second corrugated fin, and a position on the near side is an example of a second position.

  Fifth Embodiment FIG. 14A is a diagram illustrating the structure of the heat exchanger 1 in the fifth embodiment. As shown in the figure, the heat exchanger 1 in the fifth embodiment includes corrugated fins 90 a, 90 b, 90 c, 90 d, 90 e, 90 f and a refrigerant pipe 20.

  FIG.14 (b) is sectional drawing by the plane perpendicular | vertical to the refrigerant | coolant pipe | tube 20 of the heat exchanger 1 shown to Fig.14 (a). As shown in the figure, in the fifth embodiment, notches are provided in the corrugated fins 90a, 90b, 90c, 90d, 90e, and 90f, and the refrigerant pipe 20 that is a flat tube is press-fitted into these notches. Yes.

  14A and 14B, the heat exchanger 1 is assumed to receive an air flow in a direction indicated by an arrow 50 from a fan (not shown).

  FIG. 15 is a diagram showing the definition of the flat direction of the refrigerant pipe 20 that is a flat pipe. Also here, the refrigerant pipe 20 is assumed to receive an air flow in a direction indicated by an arrow 50 from a fan (not shown). As shown in the drawing, the width of the cross section of the refrigerant pipe 20 in the direction parallel to the air flow direction is A, and the width of the cross section of the refrigerant pipe 20 in the direction perpendicular to the air flow direction is B.

  Here, when the following conditions are satisfied, that is, when the flat shape of the refrigerant tube 20 follows the air flow direction, the wind loss is reduced and the area on the back side where no wind is present. Since the heat exchange area is increased by decreasing, the heat exchange performance is improved.

  A / B> 1

  FIG. 16 is a diagram illustrating a result of verifying the heat exchange performance of the heat exchanger 1 when the refrigerant tube 20 is a round tube and when the refrigerant tube 20 is a flat tube. Here, the round tube has a circular shape with an outer diameter of 8.5 mm, and the flat tube has a flat shape of 2 mm. That is, in the case of a round tube, A and B are 8.5 mm, the circumference is 26.7 mm, in the case of a flat tube, A is 9.6 mm, B is 6.5 mm, and the circumference is a round tube. Same as 26.7 mm. Then, as shown in the drawing, the length of the region where the contact flow velocity to the refrigerant pipe 20 is 0.1 m / s or more is 18.8 mm at the lowest stage in the round pipe, and 14.3 mm from the second stage onward. there were. On the other hand, in the flat tube, it was 21.9 mm at the lowest level and 18.0 mm after the second level from the bottom.

  FIG. 17 is a graph showing the difference in heat exchange performance of the heat exchanger 1 when the refrigerant tube 20 is a round tube and when it is a flat tube. As shown in the figure, when the refrigerant tube 20 is a flat tube, the heat exchange region is increased by 16% at the lowest level and by 26% from the second level after the lower level, compared with the case where the refrigerant tube 20 is a round tube. Confirmed to do.

  [Sixth Embodiment] FIG. 18 is a diagram illustrating a structure of a heat exchanger 1 according to a sixth embodiment. As illustrated, the heat exchanger 1 according to the sixth embodiment includes corrugated fin groups 110 and 120 and end plates 30 and 40 arranged in parallel in the depth direction.

  The corrugated fin groups 110 and 120 are the corrugated fin group in which the corrugated fins 10 are stacked as shown in the first embodiment, the corrugated fin group in which the corrugated fins 70 in the second embodiment are stacked, and the third embodiment. Corrugated fin group in which the corrugated fins 80 are stacked, the corrugated fin group in which the corrugated fins 10 are stacked as shown in the fourth embodiment, and the corrugated fin group in which the corrugated fins 90 in the fifth embodiment are stacked. Any of them. Here, two corrugated fin groups are arranged in parallel here, but three or more corrugated fin groups may be arranged in parallel.

  Since the end plates 30 and 40 are the same as those described in the first embodiment, description thereof is omitted here.

  According to the heat exchanger in the sixth embodiment, it is possible to adjust the heat exchange performance to be optimum according to the intended use and the application model.

  [Seventh Embodiment] Next, the area of the refrigerant tube 20 between the orthogonal surface 11 and the orthogonal surface 11 (between the fins) and the area where the orthogonal surface 11 (fin) of the corrugated fin 10 contacts the refrigerant tube 20. Will be described.

  FIG. 19 illustrates the relationship between the area where the orthogonal surface 11 (fin) of the corrugated fin 10 is in contact with the refrigerant tube 20 and the area of the refrigerant tube 20 between the orthogonal surface 11 and the orthogonal surface 11 (between the fins). FIG. As shown in the figure, when the former area is S1 and the latter area is S2, in the seventh embodiment, S2 / S1 is set to 0 or more and 40 or less.

  According to the heat exchanger in 7th Embodiment, it becomes possible to suppress that performance falls by the growth of dust or frost.

  [Effects of First to Seventh Embodiments] In the first to seventh embodiments of the present invention, the corrugated fins 10 are independent, substantially rectangular fins, so that the heat exchanger 1 is easily assembled and reliable. The heat exchange performance can be improved by improving the heat transfer area and increasing the heat transfer area.

  In addition, by combining independent substantially rectangular corrugated fins 10 having different fin-to-fin distances, it is possible to arbitrarily set the optimum configuration of the heat exchanger 1 according to the applied device and part.

  Furthermore, by using the flat refrigerant tube 20, it is possible to reduce the wind loss and improve the heat exchange performance.

  [Outline of Eighth to Tenth Embodiments] In the eighth to tenth embodiments of the present invention, in a radiator formed by combining a plurality of radiating fins inserted through a refrigerant pipe, with respect to the radiating fins. By providing the expansion plate, the heat transfer area is increased and the heat dissipation performance is improved.

  Moreover, productivity is improved by employ | adopting the same shape as the several radiation fin which forms a heat radiator.

  [Eighth Embodiment] As shown in FIG. 20, the heat dissipating body 200 according to the present embodiment dissipates heat generated from the refrigerant pipe 20, and a plurality of heat dissipating fins 210 arranged side by side on the refrigerant pipe 20. It has.

  The heat radiating fins 210 include a pair of heat radiating plates 211 that are inserted into the refrigerant pipe 20 with a space therebetween, and an expansion plate 212 that is bridged between the pair of heat radiating bodies 211. Note that the pair of heat radiation plates 211 are substantially orthogonal to the refrigerant pipe 20, and the extension plate 212 extends along the refrigerant pipe 20. The radiating fins 210 in the present embodiment are formed by bending a rectangular flat plate into a substantially rectangular shape (substantially U shape).

  In the following description, the heat dissipating fin 210 that disposes the expansion plate 212 on one side with respect to the refrigerant pipe 20 is referred to as a first heat dissipating fin 210a, and the expansion plate 212 is on the opposite side to the one side with respect to the refrigerant pipe 20. The heat dissipating fins 210 to be disposed are referred to as second heat dissipating fins 210b.

  The first radiating fins 210 a and the second radiating fins 210 b are alternately arranged with respect to the longitudinal direction of the refrigerant pipe 20. Further, the adjacent first and second heat dissipating fins 210a and 210b are arranged such that the expansion plates 212a and 212b are arranged in parallel with the refrigerant pipe 20 in between, and a part thereof is opposed. Yes.

  By arranging in this way, the heat radiating plate 211a on one side (right side in FIG. 20) of the first heat radiating fin 210a is arranged between the heat radiating plates 211b of the second heat radiating fins 210b adjacent on the one side. The heat radiating plate 211a on the other side (the left side in FIG. 20) of the first heat radiating fin 210a is disposed between the heat radiating plates 211b of the second heat radiating fins 210b adjacent on the other side. In addition, the heat radiating plate 212b on one side of the second heat radiating fin 210b is disposed between the heat radiating plates 211a of the first radiating fins 210a adjacent on the one side, and the heat radiating plate 212b on the other side of the second heat radiating fin 210b. However, it is arrange | positioned between the both heat sinks 211a of the 1st radiation fin 210a adjacent on the other side.

In addition, the adjacent first and second heat dissipating fins 210a and 210b have an interval x ₁ between the heat dissipating plates 211a and 211b arranged on the other heat dissipating fin 210 side (that is, the second heat dissipating of the first heat dissipating fin 210a). The distance x) between the heat radiation plate 211a disposed on the fin 210b side and the heat radiation plate 211b disposed on the first heat radiation fin 210a side of the second heat radiation fin 210b is disposed at a predetermined distance. Further, the interval x ₂ between the first heat radiating fin 210a adjacent _and are arranged so that the distance x ₃ between the second heat radiating fins 210b adjacent becomes the predetermined distance. Accordingly, the intervals x ₁ , x ₂ , and x ₃ are all equal intervals, and all the radiator plates 211 a and 211 b inserted through the refrigerant pipe 20 are arranged at equal intervals. The distance _{x 1} are each is preferably set to 3mm or more 30mm or less.

  [Ninth Embodiment] A heat dissipating body 200 'according to the present embodiment includes an arrangement of the first heat dissipating fins 210a and the second heat dissipating fins 210b with respect to the refrigerant pipe 20 in the heat dissipating body 200 according to the eighth embodiment. Is a change.

  Specifically, in the heat radiating body 200 ′, the first heat radiating fins 210 a and the second heat radiating fins 210 b are alternately arranged in the longitudinal direction of the refrigerant pipe 20. Moreover, the adjacent 1st radiation fin 210a and the 2nd radiation fin 210b arrange | position the mutual expansion plates 212a and 212b in parallel so that the refrigerant pipe 20 may be pinched | interposed, and it may arrange | position so that it may not oppose.

  Moreover, the adjacent 1st radiation fin 210a and 2nd radiation fin 210b are arrange | positioned so that the space | interval y of the heat sinks 211a and 211b arrange | positioned at the mutual other radiation fin 210 side may become predetermined spacing. The interval y is preferably 3 mm or more and 30 mm or less.

  [Tenth Embodiment] As shown in FIG. 22, a heat dissipating body 300 according to this embodiment includes heat dissipating fins 310 having different shapes from the heat dissipating body 200 according to the eighth embodiment. A plurality are arranged side by side.

  The radiating fin 310 includes a radiating plate 311 inserted into the refrigerant tube 20 and an expansion plate 312 extending from the radiating plate 311 along the refrigerant tube 20. In addition, the radiation fin 310 in this embodiment is formed by bending a rectangular plate material into an L shape.

  In the following description, the radiating fin 310 that arranges the expansion plate 312 on one side with respect to the refrigerant pipe 20 is referred to as a first radiating fin 310 a, and the expansion plate 312 is arranged on the opposite side to the one side with respect to the refrigerant pipe 20. The radiation fin 310 is referred to as a second radiation fin 310b.

  The first radiating fins 310 a and the second radiating fins 310 b are alternately arranged with respect to the longitudinal direction of the refrigerant pipe 20. Moreover, the adjacent 1st radiation fin 310a and the 2nd radiation fin 310b arrange | position the mutual expansion plates 312a and 312b in parallel through the refrigerant | coolant pipe | tube 20, and are arrange | positioned so that it may not oppose. Thereby, the heat radiator 300 has a corrugated fin shape as a whole.

  Moreover, the adjacent 1st radiation fin 310a and the 2nd radiation fin 310b are arrange | positioned so that the space | interval z of adjacent heat sink 311a, 311b may become a predetermined space | interval. This interval z is the same or slightly longer than the width of the extension plates 312a, 312b. The interval z is preferably 3 mm or more and 30 mm or less.

  [Outline of Eighth to Tenth Embodiments] With such a configuration, the air passing through each radiating fin comes into contact with not only the radiating plate inserted into the refrigerant pipe but also the expansion plate. As a result, the heat transfer area of each radiating fin is increased, and the heat radiation efficiency is improved. Moreover, since it can form from the radiation fin of the same shape, production cost can be reduced. In particular, according to the radiator according to the eighth embodiment, since the expansion plates of adjacent radiating fins are partially facing each other, the heat transfer area is increased as compared with the corrugated fins, and the radiating efficiency is remarkably improved. .

  [Outline of Eleventh Embodiment] In the heat exchanger, generation of frost in a portion located on the upstream side of the air flow generated by the blower fan is suppressed. Furthermore, each heat radiator is formed by heat fins having the same shape, thereby reducing production costs.

  Eleventh Embodiment The heat exchanger 1 according to the present embodiment uses the radiator 200 according to the eighth embodiment and the radiator 200 ′ according to the ninth embodiment. It is a thing. Specifically, as shown in FIG. 24, the heat exchanger 1 according to the present embodiment is formed in the refrigerant pipe 20 having a plurality of stages formed by being bent in a meandering manner, and the refrigerant pipe 20. The radiators 200 and 200 'are arranged in each stage and through which air generated by the blower fan passes. In FIG. 24, the air generated by the blower fan flows from the lower side toward the upper side.

And in the 1st step | stage and 2nd step | paragraph arrange | positioned upstream with respect to the flow of air, the thermal radiation body 200 'is arrange | positioned, and the 3rd step | paragraph arrange | positioned downstream with respect to the air flow and In the fourth stage, a heat radiating body 200 is arranged. In the present embodiment, the heat dissipating fins 210 of the heat dissipating bodies 200 and 200 ′ are all unified in the same shape. Further, the interval x ₁ in the radiator 200 and the interval y in the radiator 200 ′ are the same length.

  If comprised in this way, while heat-dissipating fins 210 used for the heat exchanger 1 are all unified in the same shape, the heat-radiating body 200 having only a narrow portion as the space between the heat-radiating plates 211 and the space between the heat-radiating bodies 11 A heat dissipating body 200 ′ having a wide portion and a narrow portion can be formed. And with respect to the heat flow, air radiator 200 'is arranged on the upstream side with respect to the air flow, and heat radiator 200 is arranged on the downstream side with respect to the air flow. It is possible to suppress frost that is likely to occur on the upstream side.

  [Outline of Twelfth Embodiment] In a heat exchanger, when two radiators are arranged next to each other, they are arranged at the time of defrosting by arranging them so that all the expansion plates included in both radiators do not overlap. Ensure that the water drops flow down efficiently.

  [Twelfth Embodiment] As shown in FIG. 25, the heat exchanger 1 according to this embodiment includes a refrigerant pipe 20 in which a plurality of stages are formed by being bent in a meandering manner, and a refrigerant pipe 20. And a heat dissipating body 300 through which air generated by a blower fan passes. Note that each of the radiators 300 has the same configuration. In FIG. 25, the air generated by the blower fan flows from the near side toward the far side.

  The radiators 300 arranged in the respective stages of the refrigerant pipes 20 are arranged so that the expansion plates 312a and 312b are parallel to each other. Thereby, with respect to the adjacent surface S (indicated by the alternate long and short dash line in FIG. 25) between the heat dissipating bodies 300 arranged in the adjacent steps, the one step (the lower step in FIG. 25). An expansion plate 312a of each radiation fin 310a of the radiator 300 disposed, and an expansion plate 312b of each radiation fin 310b of the radiator 300 disposed on the other side (the upper side in FIG. 25) , Will be in a face-to-face state. And each expansion board 312a and each expansion board 312b which face the adjacent surface S are arrange | positioned so that it may not mutually overlap.

  According to such a configuration, even if the heat radiators are brought into close contact with each other in order to make the heat exchanger compact, the expansion plates of the heat radiators arranged in adjacent stages do not overlap with each other on the adjacent surfaces. Water drops generated on the expansion plate at the time of defrosting easily flow down. In addition, the heat transfer area of the radiator is increased by the expansion plate, and the heat dissipation performance is also improved.

  In this embodiment, the expansion plates of the heat dissipating members arranged in adjacent steps are arranged so as not to overlap each other on adjacent surfaces, but are arranged so as to partially overlap within an allowable range. May be.

  In addition, you may apply the color in the said 1st Embodiment with respect to each heat radiator in the said 8th-12th embodiment. Specifically, a collar may be installed in an insertion hole through which a refrigerant pipe is inserted in a heat radiating plate provided in each radiator.

DESCRIPTION OF SYMBOLS 1 ... Heat exchanger 10, 70, 80, 90 ... Corrugated fin, 11, 71, 81 ... Orthogonal surface (enlarged heat transfer surface), 111, 112, 711, 811 ... Insertion hole, 113, 114 ... Collar, 12 , 72, 82 ... mountain surface (connection surface), 13, 73, 83 ... orthogonal surface (enlarged heat transfer surface), 131, 132, 731, 831 ... insertion hole, 133, 134 ... collar, 14, 74, 84 ... Valley face (connecting face), 20 ... refrigerant pipe, 30, 40 ... end plate, 721, 741 ... substantially M-shaped part, 821, 841 ... louver, 200, 200 ', 300 ... radiator, 210, 310 ... heat dissipation Fins, 211, 311 ... heat sink, 212, 312 ... expansion plate

Claims (29)

A refrigerant pipe having a plurality of steps formed by being bent in a meandering manner;
A heat exchanger comprising: a plurality of radiators arranged in the plurality of stages formed in the refrigerant pipe, wherein the refrigerant pipes are inserted through the stages of the plurality of stages, respectively. The radiator is a corrugated fin,
Each corrugated fin of the plurality of corrugated fins is a member provided in an insertion hole through which the refrigerant pipe of each corrugated fin is inserted, and is a member for bringing the refrigerant pipe into surface contact with each corrugated fin. The heat exchanger according to claim 1, further comprising a contact member.   The heat exchanger according to claim 2, wherein the contact member is integrally formed in the insertion hole.   The refrigerant pipe is in surface contact with the contact member by being expanded after being inserted into the insertion hole in a state having a diameter smaller than the diameter of the insertion hole of each corrugated fin of the plurality of corrugated fins. The heat exchanger according to claim 2, wherein:   3. The heat exchanger according to claim 2, wherein the refrigerant pipe has a larger outer diameter at a portion not in contact with the contact member than an outer diameter at a portion in contact with the contact member.   The ratio of the cross-sectional area of the plurality of corrugated fins after the expansion of the refrigerant pipe to the area of the portion of the plane substantially orthogonal to the refrigerant pipe of the corrugated fin that is subjected to heat exchange by one of the refrigerant pipes The heat exchanger according to claim 4, wherein is 0.02 or more and less than 0.1. The plurality of corrugated fins are:
A first corrugated fin having a first inter-fin distance;
The heat exchanger according to claim 1, further comprising a second corrugated fin having a second inter-fin distance that is longer than the first inter-fin distance. The first corrugated fin is disposed in a downstream stage of the air flow generated by the blower fan among the plurality of stages formed in the refrigerant pipe,
6. The heat exchanger according to claim 5, wherein the second corrugated fin is disposed at a stage upstream of the air flow among the plurality of stages formed in the refrigerant pipe.   The heat exchanger according to claim 7, wherein the distance between the first fins and the distance between the second fins is 3 mm or more and 20 mm or less. Each corrugated fin of the plurality of corrugated fins is
A first plane substantially orthogonal to the refrigerant pipe;
A second plane adjacent to the first plane and substantially perpendicular to the refrigerant tube;
A third plane adjacent to the second plane on the opposite side of the first plane and substantially perpendicular to the refrigerant tube;
A first bridging portion that bridges between the first plane and the second plane and is substantially parallel to the air flow generated by the blower fan;
A bridge between the second plane and the third plane is bridged on the opposite side of the refrigerant tube from the first bridge and includes a second bridge that is substantially parallel to the air flow. The heat exchanger according to claim 1.   The heat exchanger according to claim 10, wherein at least one of the first bridging part and the second bridging part is recessed in the direction of the refrigerant pipe.   The at least one of the first bridging portion and the second bridging portion is cut and raised in the direction of the refrigerant pipe in the direction of the air flow. The described heat exchanger. The plurality of corrugated fins are:
A first corrugated fin disposed at a first position shifted in a depth direction of the plurality of corrugated fins from a central axis of an air flow path generated by the blower fan;
A second corrugated fin disposed at a second position shifted in a direction opposite to a depth direction of the plurality of corrugated fins from a central axis of the air flow path;
The heat exchanger according to claim 1, comprising: The first position is a position when the first corrugated fin contacts a wall surface in the depth direction of the duct forming the air flow path,
The heat exchanger according to claim 13, wherein the second position is a position when the second corrugated fin is in contact with a wall surface in a direction opposite to a depth direction of the duct. The difference between the length in the depth direction of the duct and the length in the depth direction of the plurality of corrugated fins is defined as t, and the length in the width direction of the bridging portion that bridges the fins in the plurality of corrugated fins is defined as W. When the heat transfer coefficient at the wall surface of h is h1, and the heat transfer coefficient at the position where the distance from the wall surface of the duct is t is h2,
t / W <(2 × h2−h1) / {2 × (h1 + h2)}
The heat exchanger according to claim 10, wherein the following condition is satisfied. Each corrugated fin of the plurality of corrugated fins has a notch on the downstream side of the air flow generated by the blower fan,
The heat exchanger according to claim 1, wherein the refrigerant pipe has a flat shape and is press-fitted into a notch portion of each corrugated fin of the plurality of corrugated fins. When the width of the cross section of the refrigerant pipe in the direction parallel to the air flow is A and the width of the cross section of the refrigerant pipe in the direction perpendicular to the air flow is B,
A / B> 1
The heat exchanger according to claim 16, wherein the following condition is satisfied.   The heat exchanger according to claim 13, wherein two or more of the plurality of corrugated fins are arranged in the depth direction.   When the area where the fins of the corrugated fins of the plurality of corrugated fins are in contact with the refrigerant pipe is S1, and the area of the refrigerant pipe between the fins of the corrugated fins of the plurality of corrugated fins is S2, S2 / The heat exchanger according to claim 2, wherein S1 is 0 or more and 40 or less. Production steps to produce multiple corrugated fins;
An insertion step of inserting a refrigerant pipe through the plurality of corrugated fins;
A plurality of stages are formed in the refrigerant pipe, the plurality of corrugated fins are respectively disposed in the plurality of stages, and the refrigerant pipe is inserted into each corrugated fin of the plurality of corrugated fins in each of the plurality of stages. Bending step of bending the refrigerant pipe in a meandering manner,
In the manufacturing step, a contact member for bringing the refrigerant pipe into surface contact with each corrugated fin of the plurality of corrugated fins is formed in an insertion hole through which the refrigerant pipe of each corrugated fin is inserted. Manufacturing method of heat exchanger. A radiator that dissipates heat generated from the refrigerant pipe of the heat exchanger,
The heat dissipating body includes a plurality of heat dissipating fins arranged side by side on the refrigerant pipe,
Each of the heat dissipating fins
A pair of heat sinks inserted through the refrigerant pipe;
And an expansion plate that spans the pair of heat dissipation plates.   The heat dissipating body according to claim 21, wherein the adjacent heat dissipating fins are arranged such that their extension plates are disposed on opposite sides of the refrigerant pipe.   The heat dissipating body according to claim 21, wherein the adjacent heat dissipating fins are disposed so as to partially face each other's expansion plates.   The heat dissipating body according to claim 21, wherein the adjacent heat dissipating fins are disposed so as not to face each other's expansion plates.   25. The radiator according to any one of claims 21 to 24, wherein the adjacent radiator fins are arranged with the same spacing between the radiator plates arranged on the other radiator fin side. . A radiator that dissipates heat generated from the refrigerant pipe of the heat exchanger,
The heat dissipating body includes a plurality of heat dissipating fins arranged side by side on the refrigerant pipe,
Each of the heat dissipating fins
A heat sink inserted through the refrigerant pipe;
And an expansion plate extending from the heat radiating plate along the refrigerant pipe.   27. The heat dissipation according to claim 26, wherein the adjacent heat dissipating fins extend the expansion plate in the same direction, and the expansion plates are arranged on opposite sides of the refrigerant pipe. body. A refrigerant pipe having a plurality of steps formed by being bent in a meandering manner;
A radiator that is arranged at each stage formed in the refrigerant pipe and through which air generated by the blower fan passes,
The radiator according to claim 22 is disposed at a downstream stage with respect to the air flow,
The heat exchanger according to claim 23, wherein the radiator according to claim 23 is arranged at a stage upstream of the air flow. A refrigerant pipe having a plurality of steps formed by being bent in a meandering manner;
A radiator disposed in each stage formed in the refrigerant pipe, and
The radiator is
A plurality of heat sinks inserted through the refrigerant pipe;
Extending along the surface adjacent to the radiator disposed in the adjacent step, and an extension plate connected to any one of the radiator plates,
A heat exchanger, wherein the heat dissipating members arranged in the adjacent stages are arranged so as not to overlap a part or all of the expansion plates arranged on the adjacent surfaces.