JPH1054683A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger, high in a fin efficiency, capable of intercepting heat transfer generated from neighboring heat transfer tubes through fins, high in actual density and the degree of freedom and reduced in pressure loss. SOLUTION: In a heat exchanger, a plurality of heat transfer tubes, having individually independent fins fixed thereto with a given pitch, are arranged horizontally so as to be arrayed in a multitude of stages, and a pipeline, reciprocating alternately across an initial stage and a final stage, is formed while air stream is supplied so as to intersect with a plurality of heat transfer tubes respectively. In this case, a plurality of heat transfer tubes 2 are arrayed in zigzag with respect to the air stream from the initial stage to the final stage while a fin 1 is provided with a hexagonal configuration and is attached to the heat transfer tube 1 so that one set of opposing angles are faces upward and downward. Further, the hexagonal fins 1, fixed to neighboring heat transfer tubes, are in contact with each other through one side of the hexagonal configuration while the fore rim and rear rim of one series of hexagonal fins 1, contacted across the initial stage and the final stage, are constituted so as to show the recessed and projected configurations.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger used for refrigerators and air conditioners.

[0002]

2. Description of the Related Art As a conventional heat exchanger of a refrigerator or an air conditioner, a cross fin tube type heat exchanger as shown in FIG. 25 has been used. Since the cross fins are continuous over the plurality of arranged heat transfer tubes, there is a disadvantage that the arrangement of the heat transfer tubes is determined by the type of the fins.

As a heat exchanger provided with fins for each heat transfer tube, a heat exchanger in which fins are wound around heat transfer tubes, such as a spine fin tube heat exchanger, has been proposed (Japanese Patent Publication No. 38-8442). No., No. 51-114751,
JP-A-51-25258, etc.). In this case,
Since the fin height from the outer surface of the heat transfer tube is constant, it becomes a circular fin, the space factor with respect to the heat transfer area is poor, and the cooling air flow is faster at a place far from the heat transfer tube, and the heat exchange between the air and the fin Was not good.

A heat exchanger with a spiral fin wound around a non-circular fin is disclosed in Japanese Patent Application Laid-Open No. Sho 62-153688.
Is disclosed in Japanese Patent Application Laid-Open Publication No. HEI 9-203 (1995). This is because the manufacturing method is difficult, and it is considered impossible to align the end faces of each fin.

In a heat exchanger in which the leading edge of the fin facing upstream and the trailing edge of the fin facing downstream are not straight lines with respect to the cooling air flow, the leading edge of the fin and the trailing edge of the fin are each substantially away from the heat transfer tube. A cross fin tube type heat exchanger formed in a wave shape so as to have a uniform distance has been proposed (JP-A-8-61875). In this known example, the plurality of heat transfer tubes arranged in the upper and lower stages are linearly arranged vertically when viewed from the tube cross-sectional direction, so that the distance between adjacent heat transfer tubes is shortened. There is a disadvantage that the resistance increases.

[0006]

As a heat exchanger used in conventional refrigerators and air conditioners, a cross-fin tube type heat exchanger as shown in FIG. 25 is mainly used. Usually, a plurality of heat transfer tubes 5
Are inserted in the plate direction, and are arranged in a zigzag (or staggered) shape vertically when viewed from the tube cross-sectional direction. The surface of the fin 4 is provided with a large number of cut-and-raised portions usually called louvers 6. In this heat exchanger, a local portion of the fin area that is far from the heat transfer tube (for example, a left corner portion in FIG. 25, a leading edge portion farthest from two heat transfer tubes near the leading edge)
As a result, the fin surface temperature approaches the air temperature, the amount of heat exchange decreases, and this is one of the factors that hinder improvement in heat transfer performance. Further, in a case where the refrigerant in the heat transfer tube changes from a superheated region to a supercooled region as in a condenser in which a high-temperature gas refrigerant flows in and a low-temperature liquid refrigerant flows out, as shown in FIG. 26, When the high-temperature heat transfer tube and the low-temperature heat transfer tube are adjacent to each other, heat transfer occurs due to heat conduction of the fins, heat loss occurs as a heat exchanger, and the performance of the heat exchanger deteriorates.

For example, in a heat exchanger of an indoor unit of a room air conditioner, as shown in FIG. 27, in order to secure a heat transfer area as much as possible in a limited space, long fins 7 are multistage. It is bent. The plurality of heat transfer tubes 8 inserted into the bending fins 7 are arranged in a staggered manner, and the fans 9
It is arranged so that it surrounds. This multi-stage bending heat exchanger is manufactured by forming a cut in a linear heat exchanger and then bending the heat exchanger, so that the bending resistance of the fin or the louver at the bent portion 10 is increased and the heat transfer is increased. Performance degradation is a problem.

On the other hand, a fin tube type heat exchanger having independent fins for each heat transfer tube has a high fin efficiency,
Since they can be arranged freely, there is an advantage that the degree of freedom of mounting as a heat exchanger is large. However, since these stand-alone fin tube heat exchangers are usually manufactured by winding fins around heat transfer tubes, the fin shape is basically circular. An air gap is formed between the heat exchangers, and as a result, the volume ratio of the heat exchanger to the same volume is reduced. Further, if there is a gap between the fins, there is a problem that air flows between the fins and the heat transfer performance is reduced.

Furthermore, in the conventional cross fin tube type heat exchanger, the heat transfer tube arrangement and the fin leading edge are arranged linearly. However, such an arrangement has the disadvantage that the air flow is accelerated between the heat transfer tubes, resulting in increased pressure loss due to fin friction.

Accordingly, an object of the present invention is to provide a fin having a high fin efficiency, a heat conduction generated through the fins even when there is a temperature difference between adjacent heat transfer tubes, a high mounting density and a high degree of freedom, and a pressure loss. To provide an independent fin type heat exchanger having a small size.

[0011]

In order to achieve the above object, a heat exchanger of the present invention comprises a plurality of independent fins (hereinafter referred to as independent fins) fixed at a constant pitch in the tube axis direction. Heat transfer tubes each extend in the horizontal direction and are arranged in multiple stages, forming a single line that alternately reciprocates from the first stage to the last stage, and is formed in a horizontal direction so as to intersect with each of the heat transfer tubes. A heat exchanger to which an air flow is supplied, wherein a plurality of heat transfer tubes are arranged in a staggered manner with respect to the air flow from the first stage to the last stage, and the independent fins of each heat transfer tube form a polygonal shape. The independent fins fixed to the matching heat transfer tubes contact each other on one side or a part of this polygon, and the leading and trailing edges of a series of independent fins that contact from the first stage to the last stage correspond to the staggered arrangement of the heat transfer tubes. And have an uneven shape The features.

As described above, since the independent fins are provided for each heat transfer tube and the fins of the adjacent heat transfer tubes are arranged so as to be in contact with each other, heat is prevented from being conducted from the adjacent heat transfer tubes via the fins. In addition, a heat exchanger having a high spatial density of fins and a high degree of freedom with respect to the arrangement of heat transfer tubes can be obtained. In addition, since the leading edge and the trailing edge of the series of independent fins are uneven in correspondence with the staggered arrangement of the heat transfer tubes, the air flow path formed between the fins does not become long in the air flow direction. Further, since the heat transfer tubes are arranged in a staggered manner, the interval between the heat transfer tubes can be widened, the air flow is not accelerated, and the pressure loss of the air flow can be reduced.

In the case where hexagonal fins are used as independent fins of the heat exchanger, the hexagonal fins of each heat transfer tube are mounted so that a pair of opposing corners are directed vertically, and two adjacent fins are connected to each other. The hexagonal fins fixed to the heat tubes are in contact with each other on one side of the hexagon, and the leading and trailing edges of a series of hexagonal fins that contact from the first stage to the last stage have trapezoidal irregularities corresponding to the staggered arrangement of the heat transfer tubes. The heat exchanger may be assembled to have a shape. If one corner of the polygonal fin (here, hexagonal) is oriented in the direction of gravity as described above, drainage performance can be improved.

In the case of a heat exchanger in which a plurality of heat transfer tubes having independent fins are arranged around a cylindrical fan, polygonal or hexagonal fins are used as the independent fins and a plurality of heat transfer tubes are used. Are horizontally arranged from the cylindrical fan installed in the horizontal direction, and arranged around the fan so as to oppose an air flow to be sent out within a certain arc angle range, and the plurality of heat transfer tubes alternately reciprocate. Connected to form one pipe, adjacent heat transfer tubes are arranged in a zigzag pattern so that one of them is located forward in the airflow and the other is located behind one, and fixed to adjacent heat transfer tubes. The polygonal or hexagonal fins are in contact with one side of the polygon or hexagon, and the leading and trailing edges of the series of polygonal or hexagonal fins that contact each other correspond to the staggered arrangement of the heat transfer tubes. As an uneven shape, it may assemble the heat exchanger.

In the heat exchanger of the present invention, the provision of a slit or a turbulence promoting element consisting of point-like or linear protrusions on the surface of the independent fin is effective in increasing the fin surface heat transfer coefficient. is there. Further, a vertical vortex generator composed of a triangular wing formed by cutting and raising a part of this surface may be provided on the surface of the independent fin. Further, the independent fins may be constituted by corrugated plates.

[0016]

FIG. 1 is a block diagram showing an embodiment of the present invention.
This will be described with reference to FIG. FIG. 1 shows a heat exchanger including a heat transfer tube 2 provided with hexagonal fins 1 as independent fins. The plurality of heat transfer tubes 2 extend in the horizontal direction and are arranged in upper and lower stages, and alternately reciprocate from above to form a single refrigerant passage. Hexagonal fin 1 made of thin plate
The (plural) are arranged at a pitch with their plate faces facing each other, penetrate the heat transfer tube 2 through a hole formed in the center of each fin 1, and fix by crossing the axis of the heat transfer tube 2 by expanding or fitting. Have been. The air for cooling the refrigerant flows from the horizontal direction through the gap between the fins 1. In the present heat exchanger, the heat transfer tubes 2 arranged in multiple stages in the vertical direction are alternately arranged at two positions in front and rear with respect to the air flow direction and are arranged in a staggered manner. Is characterized in that the hexagonal fins 1 arranged in a row contact each other at one edge of the hexagon. For this purpose, the leading edge and the trailing edge of a series of hexagonal fins 1 connected vertically are
It has a trapezoidal concave and convex shape that goes back and forth in the flow direction of the air 3.

According to the heat exchanger shown in FIG. 1, the fins 1 are polygonal (hexagonal) but have a shape close to a circle, so that the fin efficiency is improved and
Are in contact with each other but are separated, so that heat conduction between the heat transfer tubes can be cut off. Further, since the adjacent fins 1 are arranged so as to be in contact with each other with a line, the mounting density is improved.

It is also possible to construct a heat exchanger in which circular fins are used in place of hexagonal fins and the fins of each stage are in point contact.

FIG. 2 shows a modification of the heat exchanger having the hexagonal fins 1 shown in FIG. 1, and shows a heat exchanger used for an indoor unit of a room air conditioner. This heat exchanger is opposed to the airflow blown out in the radial direction at a certain arc angle from the cylindrical fan,
A plurality of heat transfer tubes parallel to the cylindrical axis of the fan are arranged and configured. The plurality of heat transfer tubes are generally arranged in an inverted J shape when viewed from the tube cross-sectional direction, and have a staggered arrangement alternately arranged on each side of a line forming a J-shape. It should be noted that the cylindrical fan sends out the air in accordance with the arrangement of the inverted J shape instead of the entire circumference. Since this heat exchanger uses hexagonal fins, by aligning one side of the hexagonal fins of adjacent heat transfer tubes, the heat transfer tubes are arranged in a zigzag pattern, and before the series of fins facing the air flow. The edges and trailing edges of the series of fins from which the air flow separates may be zigzag.

The independent fin tube type heat exchanger is shown in FIG.
In the arrangement shown in FIG. 1, it is possible to arrange in a complicated form, and the degree of freedom in mounting is dramatically improved. By the way, the conventional cross fin tube type heat exchanger is shown in FIG.
Since the leading and trailing edges of the fins are straight as shown in Fig. 5, the air path formed between the adjacent fins from the leading edge to the trailing edge is long. Since the flow is accelerated, pressure loss due to friction at the fin surface increases. In order to solve this problem, it is effective to arrange the heat transfer tubes so as to be shifted back and forth as shown in FIG. 1 to increase the heat transfer tube distance. At this time, the fin ends are also formed in an uneven shape corresponding to the unevenness of the heat transfer tube, so that a decrease in the fin efficiency can be prevented. A heat exchanger having such a shape can of course be realized by a cross fin tube type heat exchanger in which a plurality of heat transfer tubes are inserted into one fin,
For example, it is easier to manufacture the fin tube type heat exchanger having a large degree of freedom in mounting as in the heat exchanger shown in FIG.

Each of the heat exchangers shown in FIGS. 1 and 2 uses hexagonal independent fins. However, not only hexagonal shapes but also various polygonal shapes can be considered. For example, a triangular fin 14 as shown in FIG. 3, a square fin 1 as shown in FIG.
5, a rectangular fin 16 shown in FIG. 5, a trapezoidal fin 17 shown in FIG. 6, a rhombus fin 18 shown in FIG. 7, an arrow-shaped fin 19 shown in FIG.

In the heat exchanger shown in FIG. 4, each of the square fins 1 fixed to the heat transfer tubes 2 arranged in a staggered manner has one corner facing downward and one side contacting one side of the adjacent square fin 1. Are combined. In the heat exchanger shown in FIG. 5, the rectangular fins 16 fixed to the staggered heat transfer tubes 2 are arranged such that a pair of long sides are in the same direction as the air flow, and the rectangular fins 16 adjacent to each other are arranged. Are in contact with each other on the long side, and are displaced in the airflow direction by the staggered arrangement. Thus, the leading edge and the trailing edge of the series of rectangular fins 16 have a rectangular uneven shape. Of course, the same is true even if the short sides touch each other. The heat exchanger shown in FIG. 6 is similar to that shown in FIG. 5. In FIG. 5, the long sides of the rectangular fins 16 are adjacent to each other, whereas in FIG. And the shape of the leading edge and the trailing edge of the series of fins also becomes trapezoidal irregularities.
The heat exchanger shown in FIG. 7 is similar to that shown in FIG.
The square fin 1 in FIG. 4 and the diamond fin 18 in FIG.
Due to the difference in the shapes of the heat transfer tubes, the ratio between the pitch of the heat transfer tubes arranged in a staggered arrangement and the staggered width can be changed. The arrow-shaped fin 19 provided in the heat exchanger shown in FIG. 8 has a set of two parallel sides,
It has two oblique sides connecting one end of the two parallel sides in a mountain shape, and two oblique sides connecting the other end of the two parallel sides in a valley shape, and is arranged in front of a series of arrow-shaped fins 19 that are vertically contacted. Both the edge and the trailing edge have a zigzag shape combining peaks and valleys.

If one of the four corners is oriented in the direction of gravity, such as the square fin 15 shown in FIG. 4 or the rhombus fin 18 shown in FIG. However, since water droplets easily collect on sharp corners and easily fall, it is effective in improving the drainage performance of the fins.

Each of the heat exchangers shown in FIGS. 3 to 8 has one arrangement of the heat transfer tubes arranged in a staggered manner, but the same effect can be obtained by providing a plurality of arrangements.

As one of means for improving the fin efficiency, as shown in FIG. 9, the heat transfer tubes are arranged not at the center of the square fins but at the windward side where the heat transfer coefficient is high and the fin surface temperature approaches the air temperature. The method is also effective. Incidentally, in FIG. 4, the heat transfer tube 2 is located at the center of the square fin 1.

In order to further improve the fin efficiency,
As shown in FIG. 10, a part of the fin end may be curved. The fin is an irregular octagon in which one pair of two opposing sides is a convex arc, and one of the arcs is arranged so as to face the air flow. The end face where the fins are in contact is the straight part 2
By setting it to 0, the fins can be brought into close contact with each other,
It is possible to prevent blow-through of an air flow in which a part of the air flow passes without contacting the fin surface, and it is possible to further improve the space mounting density. As another example, as shown in FIG. 11, if the upper and lower ends of the fins are straight portions and the left and right ends are curved in the same direction, a heat exchanger always having the same depth is provided. Note that the upper and lower linear portions need not necessarily be parallel, and as shown in FIG.
The fan shape can be further improved by providing a fan shape.

In order to further improve the mounting density and the degree of freedom, it is also effective to combine two or more types of fins 22 as shown in FIG.

Next, an embodiment in which the fin surface shape is devised in order to improve the heat transfer coefficient on the fin surface will be described below. In the following, a case where the fin shape is a quadrangle is shown, but the fin shape may of course be other than a quadrangle as shown in FIGS. FIG. 14 shows a fin in which a plurality of louvers 23 are provided in parallel. If the louvers are provided in parallel, the fin efficiency is reduced.
2 shows a fin provided with. In this case, the fin efficiency does not decrease due to the provision of the louvers. 16 and 17 show examples in which the vertical vortex generator 25 is provided. Vertical vortex generator 25
Is a winglet in which a part of a fin is raised in a triangular shape, and heat transfer is promoted by a vertical vortex generated by the winglet. FIG. 18 shows a case where an independent projection 26, which is one of the turbulence promoters, is provided. As a turbulence promoter, other than the independent protrusion, a means for separating the flow by a two-dimensional convex part 27 and promoting heat transfer at a reattachment point as shown in FIG. 19 is also effective. 20 and 21 show examples in which the fin surface is processed into a waveform. A case where a waveform 28 orthogonal to the flow is provided as shown in FIG. 20 or a case where a waveform 29 inclined with respect to the flow is provided as shown in FIG. 21 are conceivable. When a waveform inclined with respect to the flow is provided, a pseudo-vertical vortex is generated in the wave portion, and heat transfer is promoted.

FIG. 22 shows the results of evaluating the condensation performance of the rectangular fin heat exchanger according to the present invention shown in FIG. 5 and a conventional cross fin tube heat exchanger. However, 1 heat transfer tube
In the rectangular fin heat exchanger according to the present invention, the heat transfer tubes are vertically arranged in a staggered manner, whereas in the cross fin tube heat exchanger, the heat transfer tubes are vertically arranged in a straight line. The equipment specifications such as the dimensions of the heat exchanger and the sizes of the pipes and fins are as shown in FIG. As an evaluation method, the number of heat exchanged, the noise level, the fin efficiency, and the front wind speed were compared while keeping the fan rotation speed constant. In the rectangular fin heat exchanger of the present invention, the heat exchange capacity is increased by about 20% and the noise is reduced by 0.5 dB as compared with the conventional cross fin tube type heat exchanger. This is because the staggered arrangement of the heat transfer tubes reduced the pressure loss of the heat exchanger, increased the air volume by 10% or more, and improved the fin efficiency. Thus, it can be seen that the heat exchanger of the present invention has significantly improved heat transfer performance as compared with the conventional cross fin tube type heat exchanger.

Finally, the result of applying the heat exchanger according to the present invention to an air conditioner will be described. FIG. 23 is a diagram showing a heat pump refrigeration cycle. Indoor heat exchanger 34
Works as an evaporator during cooling and as a condenser during heating. The outdoor heat exchanger 32 functions as a condenser during cooling, and functions as an evaporator during heating. Indoor heat exchanger 3
4. The performance when the heat exchanger of the present invention is used for both the outdoor heat exchanger 32 is shown in FIG. Here, the operation coefficient (C
OP) is defined as a value obtained by dividing the cooling capacity or the heating capacity by the total electric input. The ratio of the operating coefficient on the vertical axis is based on the value of the operating coefficient when a conventional heat exchanger is used,
It is a ratio (%) of the operation coefficient when the heat exchanger of the present invention is used. It is understood that the use of the heat exchanger of the present invention improves the operation coefficient.

[0031]

According to the present invention, since each of the heat transfer tubes is provided with a polygon-shaped independent fin around each heat transfer tube, the fin efficiency can be increased more than the ordinary cross fin tube heat exchanger. And heat loss due to heat conduction between the heat transfer tubes can be cut off.

In addition, since polygon-shaped independent fins are provided for each heat transfer tube, and the fins of adjacent heat transfer tubes can be arranged so as to be in contact with each other, the space mounting density and the degree of freedom in heat transfer tube arrangement are improved. be able to.

Further, since a plurality of heat transfer tubes arranged in multiple stages with respect to the air flow are arranged in a staggered manner, a heat exchanger having a small pressure loss is provided.

When the shape of each fin is convex in the direction of gravity, the drainage performance can be improved.

[Brief description of the drawings]

FIG. 1 is a perspective view of a heat exchanger including hexagonal fins according to the present invention.

FIG. 2 is a perspective view when the heat exchanger of the present invention is used for a room air conditioner indoor unit.

FIG. 3 is a diagram showing a triangular independent fin.

FIG. 4 is a view showing a square independent fin.

FIG. 5 is a view showing a rectangular independent fin.

FIG. 6 is a view showing a trapezoidal independent fin.

FIG. 7 is a view showing a diamond-shaped independent fin.

FIG. 8 is a view showing an independent fin having an arrow shape.

FIG. 9 is a view showing a heat exchanger in which heat transfer tubes are arranged on the windward side.

FIG. 10 is a view showing a heat exchanger in which two or more types of independent fins are combined.

FIG. 11 is a diagram showing an independent fin in which the leading edge and the trailing edge of the fin are curved.

FIG. 12 is a diagram showing a fan-shaped independent fin with curved front and rear edges.

FIG. 13 is a diagram showing independent fins in which straight portions at upper and lower ends of the fin are non-parallel.

FIG. 14 is a diagram illustrating an independent fin having a plurality of louvers provided in parallel on a surface thereof.

FIG. 15 is a view showing an independent fin having a radial louver provided on a surface thereof.

FIG. 16 is a diagram showing an independent fin provided with a vertical vortex generator (winglet).

FIG. 17 is a view showing an independent fin having another vertical vortex generator.

FIG. 18 is a view showing an independent fin having an independent projection.

FIG. 19 is a diagram illustrating an independent fin having a two-dimensional projection.

FIG. 20 is a diagram showing independent fins having a waveform shape orthogonal to the air flow.

FIG. 21 is a diagram showing a wave-shaped independent fin oblique to the air flow.

FIG. 22 is a diagram showing the results of evaluating the condensation performance of the heat exchanger of the present invention.

FIG. 23 is a system diagram of a heat pump refrigeration cycle.

FIG. 24 is a performance comparison diagram of the air conditioner of the present invention and a conventional air conditioner.

FIG. 25 is a perspective view of a conventional cross fin tube type heat exchanger.

FIG. 26 is a diagram showing a conventional heat exchanger used as a condenser.

FIG. 27 is a perspective view of a heat exchanger of a conventional room air conditioner indoor unit.

[Explanation of symbols]

 Reference Signs List 1 independent fin 2 heat transfer tube 3 air flow 9 fan 14 triangle independent fin 15 square independent fin 16 rectangular independent fin 17 trapezoidal independent fin 18 diamond shaped independent fin 19 arrow shaped independent fin 20 2 Independent fins of different shapes or more 21 Parallel straight portions at fin ends 22 Non-parallel straight portions at fin ends 23 Parallel louvers on independent fin surfaces 24 Radial louvers on independent fin surfaces 25 Vertical vortex generators on independent fin surfaces 26 Independent projections on the independent fin surface 27 Two-dimensional projections on the independent fin surface 28 Waveform orthogonal to the flow on the independent fin surface 29 Waveform oblique to the flow on the independent fin surface 30 Compressor 31 Four-way valve 32 Outdoor heat exchanger 33 expansion valve 34 indoor heat exchanger

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Hideyuki Kimura 502, Kandachicho, Tsuchiura-shi, Ibaraki Pref. Machinery Research Laboratory, Hitachi, Ltd. (72) Inventor Sumiyoshi Takeda 390, Muramatsu, Shimizu-shi, Shizuoka Prefecture Within the System Division (72) Inventor Kensaku Oguni 390 Muramatsu, Shimizu-shi, Shizuoka Prefecture Inside the Air Conditioning System Division, Hitachi, Ltd. (72) Inventor Minato Toshimi 390 Muramatsu, Shimizu, Shizuoka Prefecture Inside the Air Conditioning System Division, Hitachi, Ltd. Inventor Hiroshi Yasuda 390 Muramatsu, Shimizu-shi, Shizuoka Prefecture Inside Air Conditioning Systems Division, Hitachi, Ltd.

Claims (10)

[Claims] 1. A plurality of heat transfer tubes each having independent fins fixed at a constant pitch in the tube axis direction, each of which extends horizontally and is arranged in multiple stages, and alternately reciprocates from the first stage to the last stage. In a heat exchanger in which a horizontal air flow is sent so as to intersect with each of the plurality of heat transfer tubes, the plurality of heat transfer tubes are
From the first stage to the last stage, the fins of each heat transfer tube are arranged in a zigzag shape with respect to the air flow, and the fins fixed to the adjacent heat transfer tubes are one side of a polygon or a part of the one side. A heat exchanger, wherein a front edge and a rear edge of a series of fins in contact with each other from the first stage to the last stage have an uneven shape corresponding to the staggered arrangement of the heat transfer tubes. 2. A plurality of heat transfer tubes each having independent fins fixed at a constant pitch in the tube axis direction, each of which extends horizontally and is arranged in multiple stages, and alternately reciprocates from the first stage to the last stage. In a heat exchanger in which an air flow is fed in a lateral direction so as to intersect with each of the plurality of heat transfer tubes, the plurality of heat transfer tubes are
From the first stage to the last stage, the fins of each heat transfer tube are arranged in a staggered manner with respect to the air flow, and the fins of the heat transfer tubes have a hexagonal shape, and a pair of opposed corners are oriented in the vertical direction, and are fixed to adjacent heat transfer tubes. The shape fins are in contact with each other on one side of the hexagon, and the leading edge and the trailing edge of a series of hexagonal fins contacting from the first stage to the last stage have an uneven shape corresponding to the staggered arrangement of the heat transfer tubes. And heat exchanger. 3. A plurality of heat transfer tubes, each having independent fins fixed at a constant pitch in the tube axis direction and extending in the horizontal direction, respectively, are provided by a cylindrical fan installed in the horizontal direction at a certain arc angle. In the heat exchanger, which is arranged around the fan so as to face the airflow sent out to the area and forms one pipe in which the plurality of heat transfer tubes alternately reciprocate, the plurality of heat transfer tubes are adjacent to each other. One of the heat pipes is arranged in a staggered manner so that one of the heat pipes is located forward toward the air flow and the other is located behind the one, and the fins of each heat transfer pipe are polygonally shaped and fixed to adjacent heat transfer pipes. The polygonal fins are in contact with each other at one side of the polygon, and the leading edge and the trailing edge of the series of polygonal fins that are in contact with each other have an uneven shape corresponding to the staggered arrangement of the heat transfer tubes. Heat exchanger. 4. A plurality of heat transfer tubes, each having independent fins fixed at a constant pitch in the tube axis direction and extending in the horizontal direction, respectively, from a cylindrical fan installed in the horizontal direction, having a certain arc angle. In the heat exchanger, which is arranged around the fan so as to face the airflow sent out to the area and forms one pipe in which the plurality of heat transfer tubes alternately reciprocate, the plurality of heat transfer tubes are adjacent to each other. One of the heat pipes is arranged in a staggered manner so that one of the heat pipes is located forward with respect to the air flow and the other is located behind the one, and the fins of each heat transfer tube have a hexagonal shape and are fixed to adjacent heat transfer tubes. The hexagonal fins are in contact with each other on one side of the hexagon, and the leading edge and the trailing edge of the series of hexagonal fins that are in contact with each other are irregularly shaped corresponding to the staggered arrangement of the heat transfer tubes. Heat exchanger. 5. The heat exchanger according to claim 1, wherein a slit is provided on a surface of the fin. 6. The heat exchanger according to claim 1, wherein the fin is made of a corrugated plate. 7. A turbulence promoting body comprising point-like or linear protrusions is provided on a surface of the fin.
5. The heat exchanger according to any one of items 1 to 4. 8. The heat exchange according to claim 1, wherein a longitudinal vortex generator formed of a triangular wing formed by cutting and raising a part of the surface is provided on the surface of the fin. vessel. 9. A refrigerator comprising the heat exchanger according to claim 1. 10. An air conditioner comprising the heat exchanger according to claim 1.