WO2018002981A1

WO2018002981A1 - Heat exchanger, refrigerator using heat exchanger as cooler, and method for manufacturing heat exchanger

Info

Publication number: WO2018002981A1
Application number: PCT/JP2016/068952
Authority: WO
Inventors: 孔明仲島; 雄亮田代; 関根　加津典; 貴紀谷川
Original assignee: 三菱電機株式会社
Priority date: 2016-06-27
Filing date: 2016-06-27
Publication date: 2018-01-04
Also published as: JPWO2018002981A1; CN109416228A; JP6644143B2

Abstract

This heat exchanger is provided with a heat transfer tube, the heat transfer tube has a partition wall inside the tube, and the partition wall extends, in a twisted shape, in the longitudinal direction inside the tube, and divides the inside of the tube into two sections.

Description

Heat exchanger, refrigerator using this heat exchanger as a cooler, and manufacturing method of heat exchanger

The present invention relates to a heat exchanger provided with a heat transfer tube as a component, a refrigerator using the heat exchanger as a cooler, and a method for manufacturing the heat exchanger.

As a heat transfer tube used as a component of a conventional heat exchanger, for example, in order to improve the heat transfer coefficient of fluid flowing in the tube as described in Patent Document 1, a plurality of ribs are connected inside the heat transfer tube, In addition, there was a heat transfer tube spirally wound in the axial direction.
This conventional heat transfer tube has a mechanism in which when the refrigerant flows through the tube in a gas-liquid two-phase state, the liquid part moves to the center through the gap between the ribs.

JP 2006-242529 A

The conventional heat transfer tube as described in Patent Document 1 can efficiently exchange heat when the refrigerant flowing in the tube is condensed from gas to liquid by the above mechanism and the air outside the tube is heated. .
However, when the conventional heat transfer tube as described in Patent Document 1 is used in a cooler that evaporates the refrigerant in the tube and cools the air outside the tube, it is more efficient that the liquid refrigerant is outside the tube. Since it can be heated, there is a problem in that the mechanism cannot cool the air efficiently.

Further, in a refrigerator equipped with a storage room and a refrigeration cycle configured by sequentially connecting a compressor, a radiator, a decompressor, and a cooler, the circulation flow rate of the refrigerant is small and the Reynolds number is about 100 to 3000. There is a laminar flow. For this reason, in the conventional heat transfer tube as described in Patent Document 1, since the liquid part of the gas-liquid two-phase refrigerant accumulates in the lower part of the heat transfer tube, when the inside of the heat transfer tube is divided by a plurality of ribs, the liquid refrigerant is evenly distributed. Is not divided, and the entire heat transfer tube cannot be uniformly cooled.

The present invention has been made in order to solve the above-described problems, and includes a heat exchanger including a heat transfer tube that can equally divide a liquid part of a gas-liquid two-phase refrigerant as a component, and this heat. It aims at providing the manufacturing method of the refrigerator which used the exchanger as a cooler, and a heat exchanger.

A heat exchanger according to the present invention is a heat exchanger provided with a heat transfer tube, and the heat transfer tube has a partition wall inside the tube, and the partition wall has a twisted shape and the tube interior in the longitudinal direction. The tube interior is divided into two.

The refrigerator according to the present invention includes a compressor, a radiator, a decompressor, the above heat exchanger, and a blower, and the compressor, the radiator, the decompressor, and the heat exchanger are connected to each other. Provided with a refrigerating cycle.

A method of manufacturing a heat exchanger according to the present invention is a method of manufacturing a heat exchanger provided with a heat transfer tube, and the heat transfer tube has a twisted partition wall inside the tube that divides the inside of the tube into two. The first heat transfer tube and a second heat transfer tube that does not have the partition inside the tube, and after passing the first heat transfer tube through the opening of the fin, the fluid is supplied to the first heat transfer tube. The heat transfer tube is sealed and compressed, and the first heat transfer tube is expanded.

According to the heat exchanger of the present invention, since the heat transfer tube having a twisted partition wall that divides the inside of the tube into two in the axial direction is configured, the gas-liquid two-phase refrigerant is divided equally. However, the liquid part of the gas-liquid two-phase refrigerant can be agitated, and the heat transfer rate is improved.

According to the refrigerator according to the present invention, since the above heat exchanger is used as a cooler which is one component of the refrigeration cycle, the heat transfer coefficient in the cooler is improved.

According to the method for manufacturing a heat exchanger according to the present invention, since the first heat transfer tube is expanded by the fluid, the degree of adhesion between the first heat transfer tube and the fin is improved in the same manner as in a normal heat exchanger. .

It is a refrigerant circuit block diagram which shows roughly the refrigerant circuit structure of the refrigerator which concerns on embodiment of this invention. It is the schematic diagram which showed typically an example of the structure of the heat exchanger which concerns on embodiment of this invention. It is the schematic diagram which showed typically an example of the internal structure of the heat exchanger tube which comprises some heat exchangers concerning embodiment of this invention. It is explanatory drawing for demonstrating the effect which the heat exchanger tube which comprises some heat exchangers concerning embodiment of this invention has. It is the schematic diagram which showed typically the state inside the heat exchanger tube which comprises some heat exchangers concerning embodiment of this invention. It is explanatory drawing for demonstrating the rotation position of the partition of the heat exchanger tube which comprises some heat exchangers concerning embodiment of this invention. It is explanatory drawing for demonstrating the state of the refrigerant | coolant which flows through the heat exchanger tube which comprises some heat exchangers concerning embodiment of this invention. It is explanatory drawing for demonstrating the state of the refrigerant | coolant which flows through the heat exchanger tube which comprises some heat exchangers concerning embodiment of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one. Further, in the following drawings including FIG. 1, the same reference numerals denote the same or equivalent parts, and this is common throughout the entire specification. Furthermore, the forms of the constituent elements shown in the entire specification are merely examples, and are not limited to these descriptions.

FIG. 1 is a refrigerant circuit configuration diagram schematically showing a refrigerant circuit configuration of a refrigerator 100 according to an embodiment of the present invention. Hereinafter, the refrigerator 100 will be described with reference to FIG. This refrigerator 100 can cool the inside of the refrigerator 100 to a target temperature using a refrigeration cycle. Moreover, the refrigerator 100 is provided with 4 A of heat exchangers which concern on embodiment of this invention as the cooler 4. FIG. The heat exchanger 4A will be described in detail with reference to FIG.

As shown in FIG. 1, the refrigerator 100 includes a compressor 1, a radiator 2, a decompressor 3, a cooler 4, and a blower 5. And the compressor 1, the heat radiator 2, the decompressor 3, and the cooler 4 are connected, and a refrigerating cycle is comprised.
The radiator 2 includes an air heat exchanger 2a and a heat radiating pipe 2b. The blower 5 includes a blower 5 a that supplies air to the radiator 2 and a blower 5 b that supplies air to the cooler 4.

The compressor 1 is not particularly limited as long as the compressor 1 sucks the refrigerant and compresses the refrigerant to be in a high temperature and high pressure state. For example, the compressor 1 can be configured using various types such as reciprocating, rotary, scroll, or screw. The compressor 1 may be configured of a type that can be variably controlled by an inverter. The compressor 1 is installed in a machine room 7 formed at the bottom of the refrigerator 100.

The radiator 2 radiates the heat of the refrigerant discharged from the compressor 1 to the air. As shown in FIG. 1, the air heat exchanger 2a is provided on the upstream side of the refrigerant flow with respect to the heat radiating pipe 2b.
The air heat exchanger 2a exchanges heat between the refrigerant discharged from the compressor 1 and the air supplied from the blower 5a. The air heat exchanger 2 a is installed in the machine room 7.
The heat radiating pipe 2 b is made of, for example, a copper pipe and is provided along the wall surface of the refrigerator 100.
The blower 5a is provided at a position where air can be supplied to the air heat exchanger 2a of the machine room 7, and supplies air to the air heat exchanger 2a.

The decompressor 3 is provided between the heat radiating pipe 2b and the cooler 4, and decompresses the refrigerant to expand it. The decompressor 3 may be configured by a device whose opening degree can be variably controlled, for example, a precise flow rate control means using an electronic expansion valve, an inexpensive refrigerant flow rate control means such as a capillary.

The cooler 4 is installed in the cooling chamber 8 of the refrigerator 100, absorbs the heat of the air from the refrigerant flowing out of the decompressor 3, and generates cool air to be supplied to the storage chamber 6 of the refrigerator 100. The configuration of the cooler 4 will be described in detail later.
The blower 5 b is provided at a position where air can be supplied to the cooler 4 in the cooling chamber 8, and supplies air to the cooler 4 by circulating the air in the storage chamber 6.

Next, the operation of the refrigerator 100 will be described.
The high-temperature and high-pressure gas refrigerant discharged from the compressor 1 passes through the air heat exchanger 2a and the heat radiating pipe 2b. The high-temperature and high-pressure gas refrigerant exchanges heat with the outside air around the refrigerator 100 in the air heat exchanger 2a and the heat radiating pipe 2b, and condenses by heat radiation. The condensed high-pressure liquid refrigerant is decompressed and decompressed by the decompressor 3, and becomes a gas-liquid two-phase refrigerant. Thereafter, the gas-liquid two-phase refrigerant flows into the cooler 4 installed in the cooling chamber 8 formed inside the refrigerator 100.

In the cooler 4, the air in the storage chamber 6 of the refrigerator 100 and the gas-liquid two-phase refrigerant exchange heat. The air in the storage chamber 6 of the refrigerator 100 is circulated in the cabinet by the blower 5b. The air is cooled by the gas-liquid two-phase refrigerant and sent to the storage chamber 6, and the refrigerant becomes a low-pressure gas refrigerant and flows out of the cooler 4. Thereafter, the refrigerant that has become low-pressure gas flows into the compressor 1, is pressurized again and discharged, and circulates in the refrigeration cycle.

Next, the flow of cooling air in the refrigerator 100 will be described.
The air cooled by the cooler 4 in the cooling chamber 8 is conveyed by the blower 5b, flows into each storage chamber 6, and cools each storage chamber 6. The cooling air that has cooled each storage chamber 6 is conveyed by the blower 5 b, passes through a return air passage formed inside the refrigerator 100, flows into the cooling chamber 8 again, and is cooled again by the cooler 4. .

Further, a portion surrounded by a one-dot chain line in FIG. When the heat exchanger 20 is provided and the refrigerant is decompressed by the decompressor 3, heat exchange with the outlet pipe of the cooler 4 may be performed. As the heat exchange unit 20, for example, a shell and tube heat exchanger, a double tube heat exchanger, a plate heat exchanger, or the like can be used. Since the refrigerant temperature at the inlet of the decompressor 3 is larger than the inlet temperature of the suction pipe of the compressor 1, when the heat exchange unit 20 is provided, the refrigerant in the decompressor 3 is cooled by the refrigerant flowing through the suction pipe. . For this reason, since the inlet dryness of the refrigerant on the inlet side of the cooler 4 takes a value close to 0, the liquid phase part increases and the cooler 4 can be used effectively. In addition, the heat exchange part 20 is not an essential structure.

FIG. 2 is a schematic diagram schematically showing an example of the configuration of the heat exchanger 4A according to the embodiment of the present invention. FIG. 3 is a schematic view schematically showing an example of the internal structure of the heat transfer tube 61 constituting a part of the heat exchanger 4A. FIG. 4 is an explanatory diagram for explaining the effect exerted by the heat transfer tube 61 constituting a part of the heat exchanger 4A. Hereinafter, based on FIGS. 2 to 4, the configuration of the heat exchanger 4A, in particular, the heat transfer tube 61 constituting a part of the heat exchanger 4A will be described. In FIG. 2, the air flow is indicated by an arrow A, the direction of gravity is indicated by an arrow B, and the refrigerant flow is indicated by an arrow C. In FIG. 4, the air flow is represented by arrow A, the swirl flow generation state is represented by arrow E, and the refrigerant flow in the pipe is represented by arrow F.

As shown in FIG. 2, the heat exchanger 4 </ b> A includes a plurality of plate-like fins 15 and heat transfer tubes 60. The heat transfer tube 60 is configured to be bent a plurality of times from the refrigerant inlet portion 60A to the refrigerant outlet portion 60B. That is, the heat transfer tube 60 includes a straight portion 51 that is inserted into the plurality of fins 15 and through which the refrigerant flows linearly, and a bent portion 52 that connects the ends of the straight portions 51 and bends the flow of the refrigerant. Has been. The refrigerant flowing through the heat exchanger 4A flows in from the refrigerant inlet portion 60A, flows out of the refrigerant outlet portion 60B after passing through the straight portion 51 and the bending portion 52. In FIG. 2, the heat transfer tube 60 has four straight portions 51 and four bent portions 52.

The heat transfer tube 60 is inserted into the opening 15 </ b> A formed in the fin 15. The heat transfer tube 60 includes a heat transfer tube 61 having a partition wall 65 inside the tube and a heat transfer tube 62 having no partition wall 65 inside the tube. In the use state of the heat exchanger 4A, the refrigerant inlet portion 60A of the heat transfer tube 60 is provided on the lower side in the gravity direction, and the refrigerant outlet portion 60B of the heat transfer tube 60 is provided on the upper side in the gravity direction. Therefore, the refrigerant flows from the lower side in the gravitational direction toward the upper side in the gravitational direction.

As shown in FIG. 3, the heat transfer tube 61 has a partition wall 65 that divides the inside of the tube into two equal parts. The partition wall 65 has a structure twisted toward the fluid flow direction (longitudinal direction of the heat transfer tube 61). The partition wall 65 has a shape that is twisted at least once by the end of the straight portion 51. For example, the partition 65 can be formed into a twisted shape by making the partition 65 spiral. This heat transfer tube 61 corresponds to the “first heat transfer tube” of the present invention.
The heat transfer tube 62 does not have the partition wall 65, and is configured by, for example, a U-shaped heat transfer tube, and the end of the heat transfer tube 61 may be connected. The heat transfer tube 62 corresponds to the “second heat transfer tube” of the present invention.

In the heat transfer tube 60, the straight portion 51 is configured by a heat transfer tube 61, and the bent portion 52 is configured by a heat transfer tube 62. That is, the heat exchanger 4 </ b> A has a structure in which at least a part of the straight portion 51 is configured by the heat transfer tube 61 and the heat transfer tube 60 in which the bending portion 52 is configured by the heat transfer tube 62 is inserted into the plurality of fins 15. ing.

Generally, in a refrigerator, the flow rate of the refrigerant is small, and the Reynolds number of the refrigerant near the cooler is as small as 100 to 3000. For this reason, the gas-liquid two-phase refrigerant inside the cooler is a laminar flow in which the liquid refrigerant accumulates in the direction of gravity. In the cooler, the liquid refrigerant evaporates to cool the air around the heat transfer tube. Therefore, in a state where the liquid refrigerant is accumulated in the lower part of the cooler, only the liquid refrigerant in contact with the lower part of the heat transfer tube exchanges heat with the air, resulting in a poor heat exchange performance.

Therefore, assuming that the heat exchanger 4A is used as the cooler 4, in the heat exchanger 4A, the heat transfer tube 61 provided with the partition wall 65 twisted inside the tube is used, so that the heat exchanger 4A is accumulated in the lower portion of the heat transfer tube 61. The liquid refrigerant is agitated. As a result, as shown in FIG. 4, the entire liquid refrigerant can be evaporated evenly. Therefore, the entire heat transfer tube 61 can be effectively contributed to heat exchange, and the heat exchange performance of the heat transfer tube 60 is improved.

FIG. 5 is a schematic diagram schematically showing an internal state of the heat transfer tube 61 constituting a part of the heat exchanger 4A. FIG. 6 is an explanatory diagram for explaining the rotational position of the partition wall 65 of the heat transfer tube 61 constituting a part of the heat exchanger 4A. FIG. 7 is an explanatory diagram for explaining the state of the refrigerant flowing through the heat transfer tubes 61 constituting a part of the heat exchanger 4A. FIG. 8 is an explanatory diagram for explaining the state of the refrigerant flowing through the heat transfer tubes 61 constituting a part of the heat exchanger 4A. The heat transfer tubes 61 constituting the heat exchanger 4A will be described in more detail based on FIGS.

FIG. 5 illustrates four states depending on the rotation position of the partition wall 65 with the partition wall 65 in a vertical state being set to 0 ° as a reference. That is, in FIG. 5, (a) shows a state when the partition wall 65 is 0 °, (b) shows a state when the partition wall 65 rotates 45 °, and (c) shows a state when the partition wall 65 rotates 90 °. The state (d) shows the state when the partition wall 65 is rotated by 135 °. Further, in FIGS. 6 to 8, in addition to the configuration of FIG.

As shown in FIGS. 5A to 5D, since the partition wall 65 has a twisted shape, the heat transfer tube 61 is viewed in the cross section of the flow path (the cross section in the direction perpendicular to the fluid flow). The inclination angle is different between two points in the longitudinal direction. For example, when the vertical direction is a reference direction, the inclination angle of the partition wall 65 shown in FIG. 5A with respect to the vertical direction is 0 °, and the inclination angle of the partition wall 65 shown in FIG. The inclination angle of the partition wall 65 shown in FIG. 5C with respect to the vertical direction is 90 °, and the inclination angle of the partition wall 65 shown in FIG. 5A is 135 ° with respect to the vertical direction. The reference direction may be not only the vertical direction but also the horizontal direction, for example.

As shown in FIGS. 5A to 5D, the inside of the heat transfer tube 61 is in a gas-liquid two-phase state of the gas part and the liquid part, and the ratio occupied by the liquid part is larger.
As shown in FIG. 5A, the gas-liquid two-phase refrigerant is equally divided by the partition wall 65 provided inside the heat transfer tube 61.
As shown in FIGS. 5B to 5D, the gas-liquid two-phase refrigerant moves upward and downward while generating a swirling flow by the torsion of the partition wall 65. The state of the refrigerant at this time is as schematically shown in FIG.
Since the refrigerant is laminar as described above, the liquid refrigerant accumulates in the direction of gravity.

Therefore, as described above, the liquid refrigerant accumulated in the lower portion of the heat transfer tube 61 can be agitated by the action of the partition wall 65, and the entire liquid refrigerant can be evaporated.
In the above description, the partition wall 65 has been described as having a shape that is twisted at least once by the end of the straight portion 51. However, the partition wall 65 does not have to be twisted by exactly one turn, as shown in FIG. If the shape is twisted by 3/4 of a turn until the end of the straight part 51, the effect is exhibited.

The heat exchanger 4A includes a heat transfer tube 61 having a partition wall 65 that is twisted. The heat transfer tube 61 is provided in the straight portion 51 of the heat exchanger 4A, and a bent portion 52 that joins the heat transfer tubes 60 is provided with a heat transfer tube 62 that does not have a twisted partition wall 65. As shown in FIG. 6, the partition wall 65 of the refrigerant inlet 60A is vertical. For this reason, the refrigerant that has flowed into the heat exchanger 4A is uniformly divided within the heat transfer tube 61 by the partition wall 65 that is vertical at the refrigerant inlet portion 60A.

Further, by adopting such a structure for the heat transfer tube 60, even if the distribution of the liquid refrigerant becomes non-uniform as shown in FIG. 7 at a certain position inside the heat exchanger 4A, the bent portion 52 is provided. Then, since there is no partition wall 65, the liquid refrigerant merges at the bent portion 52, and when entering the next heat transfer tube 61, the liquid refrigerant can be uniformly divided again by the action of the partition wall 65.

In the heat exchanger 4A, when the liquid refrigerant flows through the bent portion 52 and then flows into the heat transfer tube 61 of the straight portion 51, the partition wall 65 is vertical. That is, as shown in FIG. 6, the partition wall 65 of the heat transfer tube 61 connected to the connection portion located on the downstream side in the refrigerant flow direction in each of the connection portions of the heat transfer tube 61 and the heat transfer tube 62 is made vertical. . By doing in this way, the liquid refrigerant accumulated in the lower part can be divided into two, and the liquid refrigerant can be made to flow evenly through the flow path divided into two by the partition wall 65. That is, as shown in FIG. 6, the partition wall 65 positioned at a portion into which the refrigerant flowing without being divided flows is made vertical (arrow D).

In the actual manufacture of the heat exchanger 4A, as shown in FIG. 5 (a), the rotation position of the partition wall 65 located at the portion into which the refrigerant flowing without being divided flows is +45. It was found that when the angle was in the range of -45 °, the performance was sufficiently exhibited, but the highest performance was obtained when the partition wall 65 was 0 °, that is, vertical.

Further, the heat transfer tube 61 may be arranged immediately after the bent portion 52, or after the smooth tube 63 is provided immediately after the bent portion 52 and the smooth tube 63 is interposed. When the smooth tube 63 is installed, the smooth tube 63 may be installed at least on the downstream side of the refrigerant flow of the heat transfer tube 62 as shown in FIG. By installing the smooth tube 63, the flow disturbed by the bending portion 52 is adjusted by the smooth tube 63, and the liquid portion as shown in FIG. 4 becomes a flow accumulated in the lower part of the heat transfer tube 60. By connecting the heat transfer tube 61 after this flow, the refrigerant can be divided into two by the partition wall 65, and the liquid refrigerant can be stably divided.

In addition, the inside of the partition wall 65 and the heat transfer tube 60 may be grooved. By performing the groove processing, the liquid refrigerant rises along the groove due to the viscosity of the liquid refrigerant accumulated in the lower part of the heat transfer tube 60. For this reason, the area in a pipe | tube which heat-exchanges with the air which passes the outer periphery of the heat exchanger tube 60 will increase, and the performance of a heat exchanger can be improved.

Note that the heat transfer tube 61 is formed by extruding and rotating a metal material by extrusion molding. A normal heat transfer tube uses copper or the like having a high thermal conductivity. However, in the case of extrusion molding with a complicated shape such as the heat transfer tube 61, the metal material constituting the heat transfer tube 61 is precision using aluminum. Can be molded well. For this reason, it is good to make the heat exchanger tube 60 of this heat exchanger 4A with aluminum. However, any metal material can be used as long as the heat transfer tube 61 can be formed by extrusion molding, and the material is not limited to aluminum.

In addition, in the case of a normal heat exchanger including the heat exchanger 4A, fins are provided in addition to the heat transfer tubes. By increasing the adhesion between the fins and the heat transfer tubes, the original performance of the heat exchanger can be raised. Therefore, in general, in order to increase the adhesion between the fin and the heat transfer tube, after passing the heat transfer tube through the hole (opening) of the fin, a rod (tube expansion machine) slightly larger than the inner diameter of the heat transfer tube is used. The system is inserted into the tube and expanded. Since a partition wall 65 as in the heat transfer tube 61 is not formed in a general heat transfer tube, there is no problem with the tube expansion method using such a tube expander.

However, since the heat transfer tube 61 has the partition wall 65 in the tube, a tube expansion method using such a tube expander cannot be employed. For this reason, when manufacturing the heat exchanger 4A, after passing the heat transfer tube 61 through the openings 15A of the fins 15, the fluid (for example, liquid or gas) is enclosed in the heat transfer tube 61 and compressed to heat the heat transfer tube 60. The method of expanding the pipe is adopted. Therefore, also in the heat exchanger 4A, it is possible to increase the degree of adhesion between the heat transfer tubes 61 and the fins 15 as in the case of a normal heat exchanger.

Furthermore, as shown in FIG. 1, the refrigerator 100 uses a heat exchanger 4 </ b> A including a heat transfer tube 60 as a component as the cooler 4. In general, a refrigerator is designed to have a small air path in order to provide a space for placing food and stored items as much as possible. Therefore, in the refrigerator 100, as shown in FIG. 2, the air to be cooled flows in the same direction as the direction of gravity (arrow B) (from bottom to top in FIG. 2 (arrow A)). In the case of such a wind flow, heat exchange can be performed when the refrigerant and the air accumulated in the lower part of the heat transfer tube 60 come into contact with each other. Therefore, it is sufficient to provide the refrigerator 100 with the heat transfer tube 61 having a mechanism for stirring the refrigerant. The performance of the cooler 4 can be improved.

1 compressor, 2 radiator, 2a air heat exchanger, 2b heat radiation pipe, 3 decompressor, 4 cooler, 4A heat exchanger, 5 blower, 5a blower, 5b blower, 6 storage room, 7 machine room, 8 cooling Chamber, 15 fin, 15A opening, 20 heat exchanging part, 51 straight part, 52 bending part, 60 heat transfer pipe, 60A refrigerant inlet part, 60B refrigerant outlet part, 61 heat transfer pipe, 62 heat transfer pipe, 63 smooth pipe, 65 partition , 100 refrigerator.

Claims

A heat exchanger with a heat transfer tube,
The heat transfer tube is
Has a partition inside the tube,
The partition is
A heat exchanger with a twisted shape that extends in the longitudinal direction inside the tube and divides the inside of the tube into two parts.
The partition is
The heat exchanger according to claim 1, wherein when viewed in the cross section of the flow path, the inclination angle with respect to a reference direction is different between two points in the longitudinal direction.
The heat transfer tube is
It has a straight part and a bent part,
The heat exchanger according to claim 1 or 2, wherein the partition is provided in at least a part of the linear portion.
The partition is
The heat exchanger according to claim 3, wherein the heat exchanger has a shape twisted at least once by the end of the straight portion.
The partition is
The heat exchanger according to any one of claims 1 to 4, wherein the heat exchanger is vertical at a refrigerant inlet.
The heat exchanger according to any one of claims 1 to 5, wherein the partition wall, which is a connecting portion between the straight portion and the bent portion and is downstream of the connecting portion located downstream in the refrigerant flow direction, is vertical. .
The heat transfer tube is
The heat exchanger according to any one of claims 1 to 6, further comprising a smooth tube connecting the straight portion and the bent portion.
The heat exchanger according to any one of claims 3 to 7, wherein a groove is provided in the partition wall and the linear portion.
A compressor, a radiator, a decompressor, a heat exchanger according to claims 1 to 8, and a blower;
The refrigerator provided with the refrigerating cycle comprised by the said compressor, the said heat radiator, the said pressure reduction device, and the said heat exchanger communicating.
Air flows in the same direction as the direction of gravity through the heat exchanger,
The heat exchanger is
The refrigerator according to claim 9, wherein the linear portion is arranged to be perpendicular to the air flow direction.
A method of manufacturing a heat exchanger having a heat transfer tube,
The heat transfer tube is
A first heat transfer tube having a twisted partition wall dividing the inside of the tube in two;
A second heat transfer tube that does not have the partition wall inside the tube, and
A method of manufacturing a heat exchanger, wherein after passing the first heat transfer tube through the opening of the fin, a fluid is sealed in the first heat transfer tube and compressed, and the first heat transfer tube is expanded.
The first heat transfer tube is
The method for manufacturing a heat exchanger according to claim 11, wherein the heat exchanger is produced by extruding a metal material.
The method for manufacturing a heat exchanger according to claim 12, wherein the metal material is aluminum.