JP2008039322A - Heat exchanger and heat exchange apparatus having the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce the size and weight of a heat exchanger and improve the assembly property of the heat exchanger. <P>SOLUTION: A stainless sheet of a thickness of 0.1 mm is bent or otherwise to form a heat exchanger tube 30 in which a middle portion 32 is a flat tube of a thickness of 0.5 mm and both ends are open flared portions 34a and 34b about twice to four times as thick as the middle portion 132. A plurality of such heat exchanger tubes 30 arranged such that the flared portions 34a and 34b of each heat exchanger tube 30 are in contact with the flared portions 34a and 34b of adjacent heat exchanger tubes 30 are brazed at both ends, where headers 40 and 50 are mounted to hold them on holding portions 44 and 54, to form the heat exchanger 20. This can reduce the size and weight of the heat exchanger, improve the heat exchange efficiency thereof and improve the assembly property of the heat exchanger. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a heat exchanger and a heat exchange apparatus including the heat exchanger, and more specifically, includes a plurality of heat exchange tubes that are formed of a metal material as a hollow tube having a flat cross section at the center and arranged in parallel. A heat exchanger for cooling or heating the heat exchange medium by heat exchange between the heat exchange medium flowing in the plurality of heat exchange tubes and the heat exchange medium flowing outside the plurality of heat exchange tubes, and such a heat exchanger The present invention relates to a shell-and-tube heat exchange device.

  Conventionally, a heat exchanger of this type has been proposed that includes a plurality of tubes that circulate refrigerant between an inlet tank and an outlet tank of the refrigerant and exchange heat with the outside air (see, for example, Patent Document 1). In this heat exchanger, the refrigerant flowing into the inlet tank is cooled by exchanging heat between the plurality of tubes and the outside air passing between the tubes substantially vertically while passing through the plurality of tubes and reaching the outlet tank. And in order to improve heat exchange efficiency, the cooling fin is attached between several tubes.

In addition, there is also proposed one having a plurality of tubes with a reduced diameter for circulating the refrigerant through two headers forming an inlet and an outlet of the refrigerant to exchange heat with the outside air (for example, see Patent Document 2). In this heat exchanger, the refrigerant is circulated through a plurality of tubes having a reduced diameter, and the refrigerant is cooled by exchanging heat between the plurality of tubes and the outside air.
Japanese Patent Laid-Open No. 2001-167782 JP 2004-218969 A

  In general, heat exchangers used for computers, home appliances, and the like are desired to have high heat exchange efficiency, small size, light weight, and good assembly. In the former heat exchanger described above, extrusion molding or pressure welding is performed in order to maintain the pressure resistance of the tube, making it difficult to reduce the size and weight.

  Further, in the latter heat exchanger described above, since the pipe is reduced in diameter, the strength of the pipe decreases, and the pipe may be bent or crushed during assembly. In addition, since a large number of tubes need to be attached to the header, the assemblability is deteriorated.

  Furthermore, depending on the use conditions of the heat exchanger such as when exchanging heat with high-temperature and high-humidity outside air, condensed water may adhere to the surface of the tube, and the ventilation resistance in the outside air flow path may increase.

  The downsizing of the heat exchanger has a problem that the distance between the high temperature part and the low temperature part may be close, heat loss due to heat conduction such as a heat exchange tube increases, and the amount of exchange heat decreases.

  The heat exchanger of the present invention and the heat exchange device including the heat exchanger are one of the objects for reducing the size and weight of the heat exchanger and the heat exchange device. Another object of the heat exchanger of the present invention and the heat exchange apparatus including the heat exchanger is to improve heat exchange efficiency. Furthermore, the heat exchanger of this invention and a heat exchange apparatus provided with the same make it one of the objectives to improve the assembly property of a heat exchanger or a heat exchange apparatus. Or the heat exchanger of this invention makes it one of the objectives aiming at the improvement of the drainage of condensed water.

  The heat exchanger of the present invention and the heat exchange apparatus including the same employ the following means in order to achieve at least a part of the above object.

The heat exchanger of the present invention is
A heat exchange medium and a plurality of heat exchange tubes flowing in the plurality of heat exchange tubes, each having a plurality of heat exchange tubes arranged in parallel and formed as a hollow tube having a flat cross-section at the center portion by a metal material. A heat exchanger that cools or heats the heat exchange medium by heat exchange with the heat exchange medium flowing outside the exchange tube,
The plurality of heat exchange tubes are formed with an end portion or a widened portion having a larger cross-sectional thickness than the central portion in the vicinity of the end portion,
The heat exchange medium is formed by joining the plurality of heat exchange tubes at the widened portion so that a flow path of the heat exchange medium is formed between adjacent heat exchange tubes.
This is the gist.

  In this heat exchanger of the present invention, the cross section of the central portion is formed in the vicinity of or near the ends of a plurality of heat exchange tubes that are formed in parallel as a hollow tube having a flat cross section in the central portion made of a metal material. Forming a widened portion having a large thickness and joining a plurality of heat exchange tubes at the widened portion so that a flow path of the heat exchange medium is formed between adjacent heat exchange tubes. The replacement tubes can be accurately arranged at the same interval, and the heat exchange medium can be easily sealed, so that the heat exchanger can be easily assembled. Further, by forming the heat exchange tube as a flat hollow tube, the contact area with the outside air can be increased, and the heat exchange efficiency can be improved. Here, the heat exchange medium may include outside air.

  In such a heat exchanger according to the present invention, the plurality of heat exchange tubes may be formed by bending a plate material. If it carries out like this, the tube for heat exchange can be formed with sufficient precision. In this case, the plurality of heat exchange tubes may be formed by bending the plate material into a B shape or a C shape.

  Further, in the heat exchanger according to the present invention, the plurality of heat exchange tubes are formed as two widened portions opened at both ends, and are formed in a box shape having one surface as an opening as a whole. A holding portion for holding an end portion of the heat exchange tube on an inner side surface of the portion and a supply / discharge passage for supplying and discharging a heat exchange medium to a portion different from the opening, A pair of headers that hold both ends of the plurality of heat exchange tubes with the holding portion in a state where the tubes are arranged in parallel may be provided. If it carries out like this, supply / exhaust of the heat exchange medium to the tube for heat exchange can be performed favorably.

  In the heat exchanger according to the present invention, the plurality of heat exchange tubes may be formed by forming the two widened portions in the vicinity of both end portions and sealing both ends using crushing processing. The plurality of heat exchange tubes may be formed by forming the two widened portions in the vicinity of both end portions and sealing both end portions using a bending process. By doing so, it is possible to easily seal the end of the heat exchange tube. In these cases, a flow path of a heat exchange medium that penetrates the plurality of heat exchange tubes may be formed in the widened portion of the plurality of heat exchange tubes. By doing so, it can be made smaller and lighter than those provided with a header or the like for flowing in and out of the heat exchange medium.

  In the heat exchanger according to the present invention, the plurality of heat exchange tubes may be formed with positioning portions for positioning with respect to the heat exchange tubes adjacent to the central portion. If it carries out like this, arrangement | positioning of the several heat exchange tube can be performed easily with sufficient precision.

  In the heat exchanger according to the present invention, the plurality of heat exchange tubes may be formed as a plurality of flow paths in at least one section of the central portion. If it carries out like this, the pressure | voltage resistance of the tube for heat exchange can be improved. In this case, the plurality of flow paths may be formed as parallel flow paths for flowing the heat exchange medium in parallel in the same direction, and the plurality of flow paths are formed in a zigzag shape of the heat exchange medium. It can also be formed as a single flow path that flows through. Thus, by forming a plurality of flow paths, it is possible to reduce heat loss from the high temperature part to the low temperature part due to heat conduction such as a heat exchange tube. Furthermore, in these cases, the plurality of heat exchange tubes may be formed such that the plurality of flow paths are separated by a space. If it rubs, the heat loss from the high temperature part to the low temperature part by heat conduction, such as a heat exchange tube, can be further reduced.

  In the heat exchanger of the present invention, a drainage promotion member that promotes the elimination of water that may be generated by condensation on the outer surface of the plurality of heat exchange tubes may be attached. If it carries out like this, the drainage property of the condensed water which can adhere to the outer surface of the tube for heat exchange can be made favorable, and the passage resistance of the heat exchange medium by condensed water can be made small. That is, the performance of the heat exchanger can be maintained high. In this case, the drainage promotion member may be a string-like or belt-like member formed of a porous material.

  In the heat exchanger according to the present invention, the plurality of heat exchange tubes may have outer surfaces formed as rough surfaces. If it carries out like this, the contact surface of the condensed water which can adhere to the outer surface of the tube for heat exchange can be made small, and discharge | emission of condensed water can be made easy.

  In the heat exchanger of the present invention, the plurality of heat exchange tubes may be attached so that the flow path of the heat exchange medium flowing through the central portion is inclined at a predetermined angle from the vertical. If it carries out like this, the discharge property of the condensed water adhering to the outer surface of the tube for heat exchange can be improved.

  In the heat exchanger of the present invention, the heat exchange medium may be attached to the plurality of heat exchange tubes so that the heat exchange medium flows in from the vertically lower side and the heat exchange medium flows out from the vertically upper side. In this way, it is possible to prevent the condensed water from adhering to the vicinity of the ends located on the vertical upper side of the plurality of heat exchange tubes, and to dry the condensate. Therefore, it is possible to suppress the drainage of the condensed water in the lower part.

  In the heat exchanger of the present invention, the plurality of heat exchange tubes may be arranged in a plurality of tube rows and the plurality of tube rows in series with the flow of the heat exchange medium. it can. In this way, the temperature difference before and after heat exchange of the heat exchange medium and the heat exchange medium can be increased as compared with the case of a single row. In this case, as the plurality of tube rows, heat exchange tubes are arranged in parallel at the first interval, and first tube rows and heat exchange tubes are arranged in parallel at intervals larger than the first interval. The second tube row may be arranged such that the first tube row is on the upstream side of the heat exchange medium and the downstream side of the heat exchange medium from the second tube row. In this way, the temperature difference before and after heat exchange between the heat exchange medium and the heat exchange medium can be further increased. Further, in this case, the heat exchange tube constituting the first tube row is formed so that the cross-sectional area of the central portion is smaller than that of the heat exchange tube constituting the second tube row. It can also be.

  In the heat exchanger according to the present invention, the heat exchange medium and the heat exchange medium may be attached so as to flow substantially opposite to each other. If it carries out like this, the temperature difference before and behind heat exchange of a heat exchange medium can be enlarged.

The heat exchange device of the present invention is
A shell-and-tube heat exchange device,
The heat exchanger according to any one of the above-described aspects, i.e., a plurality of heat exchange tubes that are basically formed of a metal material as a hollow tube having a flat cross section at the center and arranged in parallel, A heat exchanger that cools or heats the heat exchange medium by heat exchange between a heat exchange medium flowing in the plurality of heat exchange tubes and a heat exchange medium flowing outside the plurality of heat exchange tubes, The plurality of heat exchange tubes have end portions or widened portions having a cross-sectional thickness larger than that of the central portion in the vicinity of the end portions, and a flow path of a heat exchange medium is provided between adjacent heat exchange tubes. A heat exchanger formed by joining the plurality of heat exchange tubes at the widened portion to be formed; and
A container member in which a central portion of at least a plurality of heat exchange tubes of the heat exchanger is housed and a supply / discharge port for supplying and discharging the heat exchange medium is formed in a flow path of the heat exchange medium;
It is a summary to provide.

  Since the heat exchanger of the present invention includes the heat exchanger of the present invention according to any one of the above-described aspects, the effects of the heat exchanger of the present invention, for example, a plurality of heat exchange tubes can be accurately measured at the same interval. The effect of being able to arrange well, the effect of being able to easily obtain the seal of the heat exchange medium, the effect of being able to improve the assembly of the heat exchanger, the effect of being able to improve the heat exchange efficiency The same effect as the above can be achieved. Of course, since it is a shell-and-tube heat exchange device, liquid-liquid heat exchange can be performed. The container member can be a hollow member having a circular or rectangular cross section.

  In such a heat exchange device of the present invention, the container member may be formed with a flow wall through which the heat exchange medium flows from the inlet to the outlet. In this way, the heat exchange efficiency can be further improved.

  Next, the best mode for carrying out the present invention will be described using examples.

  FIG. 1 is a block diagram showing an outline of the configuration of a heat exchanger 20 as a first embodiment of the present invention, and FIG. 2 is for cooling the high-temperature and high-humidity outside air of the heat exchanger 20 of the first embodiment. It is explanatory drawing explaining a mode at the time of attaching to a duct. As shown in the figure, the heat exchanger 20 of the first embodiment includes a plurality of heat exchange tubes 30 that are formed as flat hollow tubes and arranged in parallel, and ends of the plurality of heat exchange tubes 30. A pair of headers 40 and 50 that are attached so as to cover and flow the refrigerant into and out of the plurality of heat exchange tubes 30, and exclusion facilitators 62 a and 62 b for removing condensed water adhering to the plurality of heat exchange tubes 30. It is comprised by.

  The heat exchanging tube 30 is formed by bending a plate made of a stainless steel material having a thickness of 0.1 mm, the center portion 32 is formed into a flat tube having a thickness of 0.5 mm, and both end portions are in the center. It is formed as widened portions 34a and 34b opened at a thickness of about 2 to 4 times that of the portion 132, and is joined to form a hollow tube on the flat side (C-shaped cut). The plurality of heat exchanging tubes 30 are joined to the adjacent heat exchanging tubes 30 at the widened portions 34 a and 34 b at both ends, thereby providing an outside air flow path 60 as a heat exchange medium between the heat exchanging tubes 30. Forming. The outer surface of the heat exchange tube 30 is processed to be a rough surface. This process can be performed, for example, by spraying sand.

  The headers 40 and 50 are formed in a substantially rectangular box shape with one surface having openings 42 and 52 as a whole by a stainless material, and the end portions of the plurality of heat exchange tubes 30 are formed on the inner side surfaces of the openings 42 and 52. The holding portions 44 and 54 for holding are formed. Supply / exhaust passages 46 and 56 for supplying and exhausting refrigerant are attached to portions of the headers 40 and 50 different from the openings 42 and 52 (center of the left front surface in FIG. 1).

  The exclusion accelerating portions 62a and 62b are long enough to reach the bottom of the duct in a string shape or a belt shape with a porous material having a diameter smaller than the interval between the central portions of the plurality of heat exchange tubes 30, for example, porous ceramics, cloth, paper, or the like. Is formed.

  In the heat exchanger 20 of the first embodiment, a plurality of heat exchange tubes 30 are arranged in such a manner that the widened portions 34a, 34b are in contact with the widened portions 34a, 34b of the adjacent heat exchange tubes 30. The headers 40 and 50 are attached so that both ends of the heat exchange tube 30 are held by the holding portions 44 and 54 of the headers 40 and 50, and are completed by brazing in this state, and are excluded when attached to a duct or the like. The promotion parts 62a and 62b are attached and completed. By brazing, the plurality of heat exchange tubes 30 and the headers 40 and 50 can be easily joined to the plurality of heat exchange tubes 30 and the entire seal can be easily secured.

  As shown in FIG. 2, the heat exchanger 20 of the first embodiment configured as described above is arranged such that the header 40 is positioned vertically upward and the header 50 is positioned vertically downward and inclined from the vertical. The refrigerant is supplied from the exhaust passage 56 and used so that the refrigerant flows out from the supply / exhaust passage 46 of the header 40. By arranging and mounting in this manner, the refrigerant flows from the supply / discharge passage 56 of the header 50 vertically below, passes through the plurality of heat exchange tubes 30, and flows out from the supply / discharge passage 46 of the header 40. To do. On the other hand, the outside air, which is a heat exchange medium that exchanges heat with the refrigerant, is cooled by passing through the flow path 60 in the gap between the central portions 32 of the plurality of heat exchange tubes 30.

  Consider a case where high temperature and high humidity outside air is cooled by the heat exchanger 20. At this time, moisture in the outside air is condensed as condensed water on the outer surface of the heat exchange tube 30, but the heat exchange is performed so that the outer surface of the tube 30 for heat exchange becomes a rough surface. The contact surface of the condensed water adhering to the outer surface of the tube 30 for use becomes smaller, and the condensed water flows downward. At this time, in the heat exchanger 20 of the first embodiment, since the exclusion promoting portions 62a and 62b are attached, the condensed water is drained to the duct bottom by the exclusion promoting portions 62a and 62b. In addition, since the upper ends of the plurality of heat exchange tubes 30 are downstream of the refrigerant, the temperature of the refrigerant is higher than the lower ends of the heat exchange tubes 30. For this reason, adhesion of condensed water is suppressed on the upper side of the heat exchanging tube 30, and it becomes a dry state. As a result, it is possible to suppress the condensed water from adhering to the outer surface of the lower portion of the widened portion 34a on the upper side of the heat exchanging tube 30, and the surface tension of the condensed water attached to the lower portion of the widened portion 34a can thereby suppress the above. It is possible to prevent the drainage of the lower condensed water from being suppressed. As described above, by increasing the drainage of the condensed water adhering to the outer surface of the heat exchange tube 30, it is possible to suppress an increase in the ventilation resistance of the flow path 60.

  According to the heat exchanger 20 of the first embodiment described above, a plurality of heat exchange tubes 30 are joined by the widened portions 34 a and 34 b so that the outside air flow path 60 is formed between the adjacent heat exchange tubes 30. Therefore, the plurality of heat exchange tubes 30 can be accurately arranged at the same interval, and the refrigerant seal can be easily obtained, so that the heat exchanger can be easily assembled. Can do. Further, by forming the heat exchange tube 30 as a flat hollow tube, the contact area with the outside air can be increased, and the heat exchange efficiency can be improved. As a result, the heat exchanger can be reduced in size and weight. Further, by using the headers 40 and 50, it is possible to satisfactorily supply and discharge the refrigerant to and from the plurality of heat exchange tubes 30.

  Moreover, according to the heat exchanger 20 of 1st Example, drainage of the condensed water adhering to the outer surface of the tube 30 for heat exchange by processing so that the outer surface of the tube 30 for heat exchange may become a rough surface. Therefore, it is possible to suppress an increase in ventilation resistance due to the condensed water in the flow path 60 of the outside air. Moreover, according to the heat exchanger 20 of 1st Example, drainage of the condensed water adhering to the outer surface of the tube 30 for heat exchange can be accelerated | stimulated by attaching the exclusion promotion parts 62a and 62b, It can suppress that the ventilation resistance by the condensed water of the flow path 60 increases. As a result, it can suppress that the efficiency of a heat exchanger falls. Furthermore, according to the heat exchanger 20 of the first embodiment, the upper side of the heat exchange tube 30 is obtained by flowing the refrigerant so that the upper ends of the plurality of heat exchange tubes 30 are on the downstream side of the refrigerant. Adhesion of condensed water can be suppressed. As a result, it is possible to suppress the condensed water from adhering to the outer surface of the lower portion of the widened portion 34a on the upper side of the heat exchanging tube 30, and the surface tension of the condensed water attached to the lower portion of the widened portion 34a can thereby suppress the above. It is possible to prevent the drainage of the lower condensed water from being suppressed.

  In the heat exchanger 20 of the first embodiment, the header 40 is arranged on the vertically upper side so that the header 50 is positioned on the vertically lower side and is inclined from the vertical, and the refrigerant flows in from the supply / discharge passage 56 of the header 50. However, the header 40 is arranged so that the header 50 is positioned on the vertical upper side, and the header 50 is not tilted from the vertical. Alternatively, the refrigerant may be attached so that the refrigerant flows in from the supply / discharge passage 46 of the header 40 and flows out of the supply / discharge passage 56 of the header 50.

  In the heat exchanger 20 of the first embodiment, the exclusion promoting parts 62a and 62b are attached, but the exclusion promoting parts 62a and 62b may not be attached. Further, in the heat exchanger 20 of the first embodiment, the exclusion promoting portions 62a and 62b are formed in a string shape or a belt shape with porous ceramics, cloth, paper, or the like, but the exclusion promoting portions 62a and 62b are made of a metal mesh, It may be formed by punching metal or the like. In this case, it is good also as what does not form in a string shape or a strip | belt shape.

  In the heat exchanger 20 of the first embodiment, the heat exchanging tube 30 is joined so as to form a hollow tube on the flat side (C-shaped cut), but the heat exchanging of the modified example of FIG. As shown in the tube 30B, it is good also as what joins so that it may become B shape in which two flat flow paths of a refrigerant | coolant are formed.

  In the heat exchanger 20 of the first embodiment, the heat exchange tube 30 is formed by using a bending process or the like for a plate material formed of a stainless material having a thickness of 0.1 mm. The replacement tube 30 may be formed.

  In the heat exchanger 20 of the first embodiment, the processing is performed so that the outer surface of the heat exchanging tube 30 becomes a rough surface, but such processing may not be performed. Further, the outer surface of the heat exchange tube 30 may be subjected to water repellent treatment or hydrophilic treatment. If it carries out like this, the drainage property of the condensed water adhering to the outer surface of the tube 30 for heat exchange can be made more favorable.

  In the heat exchanger 20 of the first embodiment, a plate for heat exchange is formed into a flat tube having a thickness of 0.5 mm at the center portion 32 by bending a plate material formed of a stainless steel material having a thickness of 0.1 mm. However, the thickness of the plate material is not limited to 0.1 mm, and plate materials having various thicknesses may be used depending on the usage mode of the heat exchanger 20. In this case, the thickness of the central portion 32 is not limited to 0.5 mm, and may be any thickness. For example, when the heat exchanger 20 is used for heat recovery from waste heat, the heat exchanging tube 30 is formed so that the thickness of the central portion 32 is about 2 mm using a plate material of 0.3 mm to 0.5 mm. It can also be formed. Further, the plate material forming the heat exchange tube 30 is not limited to the stainless steel material, and various metal materials can be used depending on the type and form of the refrigerant and the heat exchange medium.

  FIG. 4 is a configuration diagram showing an outline of the configuration of the heat exchanger 120 of the second embodiment, and FIG. 5 is an example of a cross section of the central portion 132 of the heat exchange tube 130 of the heat exchanger 120 of the second embodiment. It is sectional drawing shown. As shown in the figure, the heat exchanger 120 of the second embodiment is configured by joining a plurality of heat exchange tubes 130 having four flat flow paths 132a to 132d in parallel.

  The heat exchanging tube 130 has a thickness of 0.5 mm due to the refrigerant channels 132a to 132d in which the central portion 132 is formed in parallel by bending a plate material formed of a stainless steel material having a thickness of 0.1 mm. Is formed as a flat flow path, and both ends are sealed by crushing. In the vicinity of both ends of the heat exchanging tube 130, widened portions 134a and 134b having a thickness about 2 to 4 times that of the central portion 132 are formed, and in the approximate center of the widened portions 134a and 134b, there is a heat exchanging portion. Circular through holes 136a and 136b penetrating the tube 130 are formed. Note that the through holes 136a and 136b are not formed on the right side of the widened portions 134a and 134b of the heat exchange tube 130 located on the rightmost side in FIG. In addition, the heat exchange tube 130 of the second embodiment is also processed so that the outer surface becomes rough.

  In the heat exchanger 120 of the second embodiment, the plurality of heat exchange tubes 130 described above are joined so that the through holes 136a and 136b of the widened portions 134a and 134b of the adjacent heat exchange tubes 130 are aligned with each other in FIG. It is configured by attaching supply / exhaust passages 146 and 156 to the left through holes 136a and 136b of the heat exchange tube 130 located on the leftmost side. By joining the heat exchange tubes 130, a flow path 160 of the outside air that is a heat exchange medium is formed between the heat exchange tubes 130.

  In the heat exchanger 120 of the second embodiment configured as described above, the refrigerant flows from one of the supply / discharge passages 146 and 156 and passes through the widened portions 134a and 134b of the heat exchange tube 130 communicated by the through holes 136a and 136b. The heat exchange tubes 130 are supplied as flow paths, reach the other widened portions 134a and 134b through the refrigerant flow paths 132a to 132d, and pass through the other supply / discharge passages 146 and 156 using the through holes 136a and 136b as flow paths. leak. On the other hand, the outside air, which is a heat exchange medium that exchanges heat with the refrigerant, is cooled by passing through the flow path 160 in the gap between the central portions 132 of the plurality of heat exchange tubes 130.

  Also in the heat exchanger 120 of the second embodiment, like the heat exchanger 20 of the first embodiment, the heat exchanging tube 130 is arranged so as to be inclined from the vertical, and the refrigerant flows in from the supply / discharge passage 156 below the vertical, It is attached so that the refrigerant flows out from the supply / exhaust passage 146 in the upper vertical direction, and further, the exclusion promoting portions 62a and 62b can be attached and used.

  In the heat exchanger 120 of the second embodiment described above, as in the heat exchanger 20 of the first embodiment, a plurality of heat exchanges are performed so that an outside air flow path 160 is formed between the adjacent heat exchange tubes 130. Since the tubes 130 are joined by the widened portions 134a and 134b, the plurality of heat exchange tubes 130 can be arranged with high accuracy at the same interval, and a refrigerant seal can be easily obtained, so that heat exchange can be performed. The assembly property of the vessel can be made good. Further, by forming the heat exchange tube 130 as a flat hollow tube, it is possible to increase the contact area with the outside air and improve the heat exchange efficiency. In addition, through holes 136a and 136b are formed in the widened portions 134a and 134b of the heat exchanging tube 130, and the widened portions 134a and 134b are joined so that the through holes 136a and 136b of the adjacent heat exchanging tubes 130 are aligned. Therefore, it is not necessary to attach a header used for supplying and discharging the refrigerant, the number of parts can be reduced, high sealing performance can be ensured, and the heat exchanger can be reduced in size and weight.

  Further, in the heat exchanger 120 of the second embodiment, similarly to the heat exchanger 20 of the first embodiment, the heat exchange tube 130 is processed so that the outer surface of the heat exchange tube 130 becomes a rough surface. The drainage of the condensed water adhering to the outer surface of 130 can be improved, and an increase in the ventilation resistance due to the condensed water in the flow path 160 of the outside air can be suppressed. Further, by attaching the exclusion promoting parts 62a and 62b, drainage of the condensed water adhering to the outer surface of the heat exchange tube 130 can be promoted, and the ventilation resistance due to the condensed water in the outside air flow path 160 is increased. Can be suppressed. As a result, it can suppress that the efficiency of a heat exchanger falls. Furthermore, by allowing the refrigerant to flow so that the upper ends of the plurality of heat exchange tubes 130 are on the downstream side of the refrigerant, it is possible to suppress the attachment of condensed water on the upper side of the heat exchange tubes 130. As a result, it is possible to suppress the condensed water from adhering to the outer surface of the lower portion of the widened portion 134a on the upper side of the heat exchanging tube 130, and by the surface tension of the condensed water adhered to the lower portion of the widened portion 134a. It is possible to prevent the drainage of the lower condensed water from being suppressed.

  In the heat exchanging tube 130 of the heat exchanger 120 of the second embodiment, both ends are sealed by crushing, but the heat exchanging tube 130B of the heat exchanger 120B of the modified example illustrated in FIG. 6 is shown. Thus, both ends may be sealed by bending.

  In the heat exchanging tube 130 of the heat exchanger 120 of the second embodiment, as shown in FIG. 5, the end portions of the plate members when forming the four refrigerant flow paths 132 a to 132 d are bent and joined inside. However, it is also possible to form a protruding portion that protrudes outward and to join the protruding portion.

  In the heat exchanger 120 of the second embodiment, a plurality of heat exchanging tubes 130 are joined so that the through holes 136a and 136b are aligned, but this is shown in a heat exchanging tube 130C of a modified example illustrated in FIG. As described above, the positioning portions 133a to 133d may be formed in the refrigerant flow paths 132a to 132d of the heat exchange tube 130C, respectively. If it carries out like this, the positioning at the time of joining the some tube 130C for heat exchange can be performed easily, and the yield of a heat exchanger can be made high. Moreover, since the positioning parts 133a to 133d are formed in the central part 132 (refrigerant flow paths 132a to 132d), the pressure resistance of the central part 132 can be improved. Such positioning parts 133a to 133d can be formed by embossing. The positioning portions 133a to 133d do not need to be formed in all of the refrigerant flow paths 132a to 132d, and may be formed in a part thereof, and the positions to be formed are not limited to the central portion 132.

  In the heat exchange tube 130 of the heat exchanger 120 of the second embodiment, the four refrigerant flow paths 132a to 132d parallel to the central portion 132 are formed, but three or less refrigerant flow paths are formed in parallel. It may be a thing, and it does not matter as what forms five or more refrigerant flow paths in parallel.

  In the heat exchange tube 130 of the heat exchanger 120 of the second embodiment, the four refrigerant flow paths 132a to 132d are formed in parallel with the central portion 132. However, the heat exchange tube of the modified example illustrated in FIG. As shown in the tube 130D, a zigzag refrigerant channel 132D that connects the widened portions 134a and 134b in the vicinity of both ends of the heat exchange tube 130D may be formed. In this case, as shown in the drawing, the heat exchanger is preferably arranged so that the upstream side of the refrigerant flow path 132D is the downstream side of the outside air that is the heat exchange medium. The refrigerant in the refrigerant flow path 132D meanders in a zigzag manner and flows as a whole from the right side to the left side in FIG. 8, so that the refrigerant and the outside air flow as opposed to each other. Thereby, the performance of a heat exchanger can be improved. Here, the zigzag-shaped refrigerant flow path 132D is not limited to the three rows that are bent twice as shown in FIG. 8, but is formed as five rows that are bent four times, seven rows that are bent six times, and the like. It is good also as what to do.

  In the heat exchange tube 130 of the heat exchanger 120 of the second embodiment, the four refrigerant flow paths 132a to 132d are formed in the central portion 132 by bending, but the four refrigerant flow paths 132a to 132d are separated by a space. You may form so. For example, if the fan-shaped refrigerant flow path 132D of the heat exchange tube 130D of the modification example illustrated in FIG. 8 is separated by a space, the heat exchange tube 130E of the modification example illustrated in FIG. 9 is obtained. A cross section of the center portion of the heat exchange tube 130E is shown in FIG. Thus, by separating the zigzag refrigerant passage 132E with the spaces 137a and 137b, heat loss from the high temperature portion to the low temperature portion due to heat conduction of the heat exchange tube can be reduced. As a result, the performance of the heat exchanger can be improved. It should be noted that the refrigerant flow path need not be formed in a zigzag shape as a space separating the refrigerant flow paths, but may be formed as parallel refrigerant flow paths as in the second embodiment.

  In the heat exchange tube 130 of the heat exchanger 120 of the second embodiment, the four refrigerant flow paths 132a to 132d are formed in the central portion 132 by bending, but the refrigerant flow paths 132a to 132d may not be formed. I do not care.

  In the heat exchanger 120 of the second embodiment, similarly to the heat exchanger 20 of the first embodiment, the heat exchanging tube 130 is disposed so as to be inclined from the vertical, and the refrigerant flows in from the supply / discharge passage 156, and the supply / discharge passage However, the heat exchanging tube 130 may not be disposed so as to be inclined from the vertical, or the refrigerant is introduced from the supply / exhaust passage 146 and is supplied from the supply / exhaust passage 156. It is good also as what is attached and used so that a refrigerant may flow out. In addition, although the heat exchange tube 130 is formed by using a bending process or the like for a plate material made of a stainless material having a thickness of 0.1 mm, the heat exchange tube 130 is formed by using a method other than the bending process. It doesn't matter. Further, although the treatment is performed so that the outer surface of the heat exchanging tube 130 becomes a rough surface, such treatment may not be performed, or the outer surface of the heat exchanging tube 130 may be subjected to a water repellent treatment. It is good also as what performs a hydrophilic treatment.

  FIG. 11 is a configuration diagram showing an outline of the configuration of the heat exchanger 220 of the third embodiment of the present invention. As shown in the figure, the heat exchanger 220 of the third embodiment is a micro heat exchange train in which both ends are sealed by bending and a heat exchanging tube 330 not having a plurality of refrigerant channels is arranged in parallel in the central portion 332. 320 and a heat exchanging tube 430 in which the thickness (cross-sectional area) of the central portion 432 and the thickness (cross-sectional area) of the widened portions 434a and 434b are smaller than the heat exchanging tube 330 of the micro heat exchanging column 320 are arranged in parallel. The micro heat exchange train 420 is arranged in series in a flow of outside air that is a heat exchange medium.

  Similar to the heat exchange tube 130 of the second embodiment, the micro heat exchange row 320 and the micro heat exchange row 420 have circular through holes 336a, 336b, Widened portions 334a, 334b, 434a, 434b in which 436a, 436b are formed are formed, and the widened portions 334a, 334b, 434a, 342 of the adjacent heat exchanging tubes 330, 430 are formed in the plural heat exchanging tubes 330, 430. The through holes 336a, 336b, 436a, 436b of 434b are joined so as to be aligned, and the supply / discharge passage 346 is inserted into the through holes 336a, 336b, 435a, 436b on the left side of the heat exchange tubes 330, 430 located on the leftmost side in FIG. , 356, 436, 456 are attached. In the micro heat exchange train 320, the thickness of the heat exchange tube 330 is larger than the thickness of the heat exchange tube 430 in the micro heat exchange train 420, so that the pitch of the heat exchange tubes 330 is increased and the heat exchange tubes 330 are joined. By doing so, the width of the outside air flow path 360 is also larger than that of the outside air flow path 460 formed by joining the heat exchange tubes 430. In the example, the heat exchanger 220 is configured in such a ratio that four heat exchange tubes 430 of the micro heat exchange train 420 are arranged while three heat exchange tubes 330 of the micro heat exchange train 320 are arranged. The heat exchanging tube 330 and the heat exchanging tube 430 are formed by bending a plate material made of a stainless material having a thickness of 0.1 mm, similar to the heat exchanging tube 130 of the heat exchanger 120 of the second embodiment. Etc., the central portions 332 and 432 are formed as a flat flow channel having a thickness of 0.5 mm as a whole, both end portions are sealed by bending, and the outer surface is processed to be a rough surface. ing. In addition, the through-holes 336a, 336b, 436a, 436b are not formed on the right side of the widened portions 334a, 334b, 434a, 434b of the heat exchange tubes 330, 430 located on the rightmost side in FIG.

  In the heat exchanger 220 of the third embodiment, as shown in FIG. 11, the supply / discharge passages 346, 446 are arranged to be above the supply / discharge passages 356, 456, and the refrigerant of the micro heat exchange train 420 is arranged. After flowing into the micro heat exchange train 420 from the supply / discharge passage 456 and exchanging heat with the outside air through the plurality of heat exchange tubes 430, the heat flows out from the supply / discharge passage 446, and the refrigerant flowing out of the supply / discharge passage 446 is micro heat exchanged. About the outside air (heat exchange medium) so that it flows from the supply / discharge passage 356 of the row 320 into the micro heat exchange row 320 and flows out from the supply / discharge passage 456 after exchanging heat with the outside air through the plurality of heat exchange tubes 330. Are attached so that they exchange heat with the micro heat exchange train 320 and then exchange heat with the micro heat exchange train 420 (so as to flow from the upper left rear to the lower right in FIG. 11).

  In the heat exchanger 220 of the third embodiment configured as described above, the outside air is first cooled by exchanging heat with the refrigerant flowing in the heat exchange tubes 330 of the micro heat exchange train 320, and then the micro heat exchange train 420. It is further cooled by exchanging heat with the refrigerant flowing through the heat exchange tube 430. As described above, since the refrigerant flows in the order of the micro heat exchange train 420 and the micro heat exchange train 320, the coolant and the outside air flow as opposed to each other. Compared with the heat exchange tube 330 of the micro heat exchange train 320, the heat exchange tube 430 of the micro heat exchange train 420 has a cross-sectional area of the central portion 432 and a distance (pitch width) between adjacent heat exchange tubes 430. Is formed so that the diameter of the tube on the upstream side of the refrigerant is smaller than the diameter of the tube on the downstream side of the refrigerant, which tends to be higher temperature. While maintaining high performance in the low temperature part, the diameter of the high temperature part can be increased while the scale is deposited to reduce the influence of the scale.

  According to the heat exchanger 220 of the third embodiment described above, the micro heat exchange train 320 and the micro heat exchange train 420 are arranged in series with the flow of the heat exchange medium (outside air). Compared to a heat exchanger having a row of heat exchange tubes, it can have a high heat exchange function. In addition, the heat exchange tube 430 of the micro heat exchange train 420 is compared to the heat exchange tube 330 of the micro heat exchange train 320, and the cross-sectional area of the central portion 432 and the distance (pitch width) between adjacent heat exchange tubes 430. Therefore, the influence of the scale can be reduced by increasing the diameter of the high temperature portion while the scale is deposited while maintaining the high performance of the low temperature portion of the heat exchanger. Of course, since the refrigerant and the outside air are attached so as to flow opposite to each other, the performance of the heat exchanger can be improved.

  In the heat exchanger 220 of the third embodiment, as in the heat exchanger 20 of the first embodiment, a plurality of heats are formed so that the flow paths 360, 460 of the outside air are formed between the adjacent heat exchange tubes 330, 430. Since the replacement tubes 330 and 430 are configured to be joined by the widened portions 334a, 334b, 434a, and 434b, the plurality of heat exchange tubes 330 and 430 can be accurately arranged at the same interval and a refrigerant seal can be provided. It can be easily obtained, and the assembly property of the heat exchanger can be improved. Moreover, by forming the heat exchange tubes 330 and 430 as flat hollow tubes, the contact area with the outside air can be increased, and the heat exchange efficiency can be improved. Moreover, through holes 336a, 336b, 436a, 436b are formed in the widened portions 334a, 334b, 434a, 434b of the heat exchange tubes 330, 430, and the through holes 336a, 336b, 436a of the adjacent heat exchange tubes 330, 430 are formed. , 436b are joined so that the widened portions 334a, 334b, 434a, and 434b are joined, so that it is not necessary to attach a header used for supplying and discharging refrigerant, the number of parts can be reduced, and high sealing performance can be ensured. This makes it possible to reduce the size and weight of the heat exchanger. Further, by performing the treatment so that the outer surfaces of the heat exchange tubes 330 and 430 become rough, the drainage of condensed water adhering to the outer surfaces of the heat exchange tubes 330 and 430 can be improved, and the outside air It is possible to suppress an increase in ventilation resistance due to the condensed water in the flow paths 360 and 460.

  Further, in the heat exchanger 220 of the third embodiment, as in the heat exchanger 20 of the first embodiment, the heat exchanging tubes 330 and 430 are disposed so as to be inclined from the vertical, or the exclusion promoting portions 62a and 62b. Can also be used. Therefore, by attaching the exclusion promoting portions 62a and 62b, drainage of the condensed water adhering to the outer surfaces of the heat exchange tubes 330 and 430 can be promoted, and the ventilation resistance due to the condensed water in the flow paths 360 and 460 of the outside air can be promoted. Can be prevented from increasing. As a result, it can suppress that the efficiency of a heat exchanger falls. Further, by flowing the refrigerant so that the upper ends of the plurality of heat exchange tubes 330 and 430 are on the downstream side of the refrigerant, adhesion of condensed water on the upper side of the heat exchange tubes 330 and 430 is suppressed. Can do. As a result, it is possible to prevent the condensed water from adhering to the outer surface of the lower portion of the widened portions 334a and 434a on the upper side of the heat exchange tubes 330 and 430, and the condensed water attached to the lower portion of the widened portions 334a and 434b. It is possible to prevent the drainage of the condensed water below it from being suppressed due to the surface tension.

  In the heat exchanger 220 of the third embodiment, the central portions 332 and 432 of the heat exchange tube 330 and the heat exchange tube 430 are formed as a single refrigerant flow path, but the heat exchange tube 130 of the second embodiment A plurality of refrigerant flow paths may be formed as described above, or a folded refrigerant flow path may be formed like the heat exchange tubes 130D and 130E of the modified example. In this case, as shown in the heat exchanging tube 430B of the modified example illustrated in FIG. 12, the cross-sectional area of the refrigerant flow path on the upstream side of the refrigerant may be formed so as to be larger than that on the downstream side.

  In the heat exchange tubes 330 and 430 of the heat exchanger 220 of the third embodiment, both ends are sealed by bending, but both ends are crushed like the heat exchange tube 130 of the second embodiment. It does not matter as a seal. Moreover, it is good also as what attaches a pair of headers as an open end similarly to the heat exchanger 20 of 1st Example.

  In the heat exchanger 220 of the third embodiment, the two tube rows of the micro heat exchange row 320 and the micro heat exchange row 420 are arranged in series with the flow of the heat exchange medium (outside air). However, three or more tube rows may be arranged in series with the flow of the heat exchange medium (outside air).

  In the heat exchanger 20 of the first embodiment, the heat exchanger 120 of the second embodiment, the heat exchanger 220 of the third embodiment, or a modification thereof, a plate formed of a stainless material having a thickness of 0.1 mm is used. The heat exchange tubes 30, 130, 330, and 430 are formed using bending or the like, but the thickness of the plate is not limited to 0.1 mm, and the heat exchangers 20, 120, and 220 are used. Depending on the embodiment, plate materials having various thicknesses may be used. In this case, the thickness of the central portions 32, 132, 332, and 432 is not limited to 0.5 mm, and may be any thickness. For example, when the heat exchangers 20, 120, and 220 are used for heat recovery from waste heat, the center portions 32, 132, 332, and 432 have a thickness of 2 mm using a plate material of 0.3 mm to 0.5 mm. It is also possible to form the heat exchange tubes 30, 130, 330, and 430 so as to have a degree. Further, the plate material forming the heat exchange tubes 30, 130, 330, 430 is not limited to the stainless steel material, and various metal materials are used depending on the type and form of the heat exchange medium and the heat exchange medium flowing inside. be able to.

  In the heat exchanger 20 of the first embodiment, the heat exchanger 120 of the second embodiment, the heat exchanger 220 of the third embodiment, or modifications thereof, the case where outside air is used as the heat exchange medium has been described. The heat exchange medium is not limited to the outside air, and a liquid can also be used. In this case, the heat exchanger 20 of the first embodiment, the heat exchanger 120 of the second embodiment, the heat exchanger 220 of the third embodiment, or a modified example thereof may be a shell and tube type. An example of a shell and tube heat exchanger 70 in which the heat exchanger 20 of the first embodiment is a shell and tube type is shown in FIG. In the case of the shell-and-tube heat exchanger 70, as shown in the drawing, the heat exchanger 20 of the first embodiment is inserted into a container 80 having a circular or rectangular cross section, and the supply / discharge passage of the heat exchanger 20 is inserted. The heat exchange medium is supplied to and discharged from 46, and the liquid as the heat exchange medium is supplied to and discharged from the supply and discharge passages 82 and 84 attached to the container 80. Thus, by using the shell-and-tube heat exchange 70, the heat exchanger 20 of the first embodiment, the heat exchanger 120 of the second embodiment, the heat exchanger 220 of the third embodiment, or modifications thereof. It can be used as a liquid-liquid heat exchanger. In the case of the shell and tube type, as shown in the shell and tube heat exchanger 70B of the modified example of FIG. 14, the flow walls 86a and 86b through which the heat exchange medium in the container 80 flows. It is good also as what provides.

  In the first embodiment, the second embodiment, and the third embodiment described above, the outside heat is assumed as the heat exchange medium. However, the heat exchange medium is not limited to the outside air, and any fluid can be used. It may be used as a heat exchange medium.

  The best mode for carrying out the present invention has been described with reference to the embodiments. However, the present invention is not limited to these embodiments, and various modifications can be made without departing from the gist of the present invention. Of course, it can be implemented in the form.

  The present invention can be used in the manufacturing industry of heat exchangers and heat exchange devices.

It is a block diagram which shows the outline of a structure of the heat exchanger 20 as 1st Example of this invention. It is explanatory drawing explaining a mode at the time of attaching the heat exchanger 20 of 1st Example to a duct in order to cool high temperature high humidity external air. It is a block diagram which shows the outline of a structure of the tube 30B for heat exchange of a modification. It is a block diagram which shows the outline of a structure of the heat exchanger 120 of 2nd Example of this invention. It is sectional drawing which shows an example of the cross section of the center part 132 of the tube 130 for heat exchange of the heat exchanger 120 of 2nd Example. It is a block diagram which shows the outline of a structure of the tube 130B for heat exchange of the heat exchanger 120B of a modification. It is a block diagram which shows the outline of a structure of the tube 130C for heat exchange of a modification. It is a block diagram which shows the outline of a structure of the tube 130D for heat exchange of a modification. It is a block diagram which shows the outline of a structure of the tube 130E for heat exchange of a modification. It is sectional drawing which illustrates the cross section of the center part of the tube 130E for heat exchange of a modification. It is a block diagram which shows the outline of a structure of the heat exchanger 220 of 3rd Example of this invention. It is a block diagram which shows the outline of a structure of the tube 430B for heat exchange of a modification. It is a block diagram which shows the outline of a structure of the shell and tube type heat exchanger 70 using the heat exchanger 20 of 1st Example. It is a block diagram which shows the outline of a structure of the shell and tube type heat exchanger 70B of a modification.

Explanation of symbols

20, 120, 120B, 220 heat exchanger, 30, 30B, 130, 130B to 130E, 330, 430, 430B heat exchange tube, 32, 132, 132D, 132E, 332, 432 central part, 34a, 34b, 134a , 134b, 334a, 334b, 434a, 434b Widened portion, 40, 50 Header, 42, 52 Opening portion, 44, 54 Holding portion, 46, 56, 146, 156, 346, 356, 446, 456 Supply / exhaust passageway, 60 , 160, 360, 460 flow path, 70, 70B shell and tube heat exchanger, 80 container, 82, 84 supply / discharge passage, 86a, 86b flow wall, 132a-132d refrigerant flow path, 133a-133d positioning part, 136a, 136b, 336a, 336b, 436a, 436b Through hole, 137a, 137 b Space, 320, 420 Micro heat exchange train.

Claims (23)

A heat exchange medium and a plurality of heat exchange tubes, which are formed as a hollow tube having a flat cross section at the center by a metal material and arranged in parallel, and which flow in the plurality of heat exchange tubes A heat exchanger that cools or heats the heat exchange medium by heat exchange with the heat exchange medium flowing outside the exchange tube,
The plurality of heat exchange tubes are formed with an end portion or a widened portion having a larger cross-sectional thickness than the central portion in the vicinity of the end portion,
The heat exchange medium is formed by joining the plurality of heat exchange tubes at the widened portion so that a flow path of the heat exchange medium is formed between adjacent heat exchange tubes.
Heat exchanger.   The heat exchanger according to claim 1, wherein the plurality of heat exchange tubes are formed by bending a plate material.   The heat exchanger according to claim 2, wherein the plurality of heat exchange tubes are formed by bending the plate material into a B shape or a C shape. The heat exchanger according to any one of claims 1 to 3,
The plurality of heat exchange tubes are formed as two widened portions having both ends opened,
It is formed in a box shape having an opening on one side as a whole, and the heat exchange medium is supplied to and discharged from a portion different from the opening and the holding portion that holds the end of the heat exchange tube on the inner side surface of the opening. A heat exchanger having a pair of headers that hold both ends of the plurality of heat exchange tubes with the holding portion in a state where the plurality of heat exchange tubes are arranged in parallel.   4. The heat exchanger according to claim 1, wherein the plurality of heat exchange tubes have two widened portions formed in the vicinity of both end portions, and the both end portions are sealed using a crushing process. 5.   4. The heat exchanger according to claim 1, wherein the plurality of heat exchange tubes have two widened portions formed in the vicinity of both ends, and both ends are sealed using a bending process.   The heat exchanger according to claim 5 or 6, wherein a flow path of a heat exchange medium penetrating the plurality of heat exchange tubes is formed in the widened portion of the plurality of heat exchange tubes.   The heat exchanger according to any one of claims 1 to 7, wherein the plurality of heat exchange tubes are formed with positioning portions for positioning with respect to the heat exchange tubes adjacent to the central portion.   The heat exchanger according to any one of claims 1 to 8, wherein the plurality of heat exchange tubes are formed as a plurality of flow paths in at least one section of the central portion.   The heat exchanger according to claim 9, wherein the plurality of flow paths are formed as parallel flow paths for flowing the heat exchange medium in parallel in the same direction.   The heat exchanger according to claim 9, wherein the plurality of flow paths are formed as a single flow path that allows the heat exchange medium to flow in a folded manner.   The heat exchanger according to any one of claims 9 to 11, wherein the plurality of heat exchange tubes are formed such that the plurality of flow paths are separated by a space.   The heat exchanger according to any one of claims 1 to 12, further comprising a drainage promotion member that promotes removal of water generated by condensation on the outer surfaces of the plurality of heat exchange tubes.   The heat exchanger according to claim 13, wherein the drainage promotion member is a string-like or belt-like member formed of a porous material.   The heat exchanger according to any one of claims 1 to 12, wherein an outer surface of each of the plurality of heat exchange tubes is formed as a rough surface.   The heat exchanger according to any one of claims 1 to 15, wherein the plurality of heat exchange tubes are attached so that a flow path of a heat exchange medium flowing through the central portion is inclined at a predetermined angle from vertical.   The heat exchanger according to any one of claims 1 to 16, wherein the heat exchange medium is attached to the plurality of heat exchange tubes so that the heat exchange medium flows in from a vertically lower side and flows out from the vertical upper side.   The heat exchanger according to any one of claims 1 to 17, wherein the plurality of heat exchange tubes are arranged in a plurality of tube rows, and the plurality of tube rows are arranged in series with respect to a flow of the heat exchange medium.   As the plurality of tube rows, a first tube row in which heat exchange tubes are arranged in parallel at a first interval and a second tube in which heat exchange tubes are arranged in parallel at intervals larger than the first interval. The heat exchanger according to claim 18, wherein the first tube row is arranged upstream of the second tube row and downstream of the heat exchange medium.   20. The heat exchange according to claim 19, wherein the heat exchange tubes constituting the first tube row are formed such that a cross-sectional area of a central portion is smaller than that of the heat exchange tubes constituting the second tube row. vessel.   The heat exchanger according to any one of claims 1 to 20, wherein the heat exchange medium and the heat exchange medium are attached so as to flow substantially opposite to each other as a whole. A shell-and-tube heat exchange device,
A heat exchanger according to any one of claims 1 to 21,
A container member in which a central portion of at least a plurality of heat exchange tubes of the heat exchanger is housed and an inlet and an outlet for supplying and discharging the heat exchange medium are formed in a flow path of the heat exchange medium. When,
A heat exchange device comprising: The heat exchange apparatus according to claim 22, wherein the container member is formed with a flow wall through which the heat exchange medium flows from the inflow port toward the outflow port.