WO2017037772A1

WO2017037772A1 - Heat exchanger and method for manufacturing same

Info

Publication number: WO2017037772A1
Application number: PCT/JP2015/074366
Authority: WO
Inventors: 良太赤岩; 寿守務吉村; 松本　崇; 山田　彰二; 皓亮宮脇; 石橋　晃; 智嗣上山; 綾河島
Original assignee: 三菱電機株式会社
Priority date: 2015-08-28
Filing date: 2015-08-28
Publication date: 2017-03-09
Also published as: JPWO2017037772A1; JP6537615B2

Abstract

To provide a heat exchanger and a method for manufacturing a heat exchanger, with which it is possible to improve defrosting efficiency and suppress frost formation to a greater extent than in the prior art. A heat exchanger for exchanging heat between internally flowing coolant and peripherally flowing air, wherein: the heat exchanger is provided with a plurality of heat transfer tubes 12 extending in a straight line, and hollow headers 10, 11 into which both ends of each of the plurality of transfer tubes are inserted to constitute a part of a coolant flow route; each of the plurality of transfer tubes has openings 15A–15F at both ends, and internally has a plurality of coolant flow paths 15a–15f through which the coolant flows; and in at least at one end connected to the header in the long direction of the plurality of the heat transfer tubes, the openings 15A–15C provided at some locations including the location positioned farthest to the upstream side of the flow of air are orientated differently inside the header relative to the openings 15D–15F at the remaining locations provided at the one end.

Description

HEAT EXCHANGER AND HEAT EXCHANGER MANUFACTURING METHOD

The present invention relates to a heat exchanger, a refrigeration cycle apparatus, and a heat exchanger manufacturing method, for example, a heat exchanger used in an air conditioner capable of defrosting operation and heating operation, and a heat exchanger manufacturing method.

Conventionally, for example, as a heat exchanger for a car air conditioner, a pair of headers that are horizontally opposed to each other, a plurality of flat heat transfer tubes that are connected in parallel to the pair of headers at a constant interval, and between flat heat transfer tubes There is a corrugated fin that intervenes closely in a gap and supplies a refrigerant as a heat exchange medium to a plurality of flat heat transfer tubes.

However, when the heating operation is performed using the above-described heat exchanger in, for example, a heat pump type cooling / heating air conditioning outdoor unit, the above-described heat exchanger functions as an evaporator. For this reason, when heating operation is performed during cold weather, the surface temperature of the fins and heat transfer tubes in the evaporator decreases to below the freezing point, and moisture in the air may form frost on the fins and heat transfer tube surfaces.

When such frost formation occurs, the resistance to air passing between the fins of the evaporator is significantly increased, and the heat resistance in the heat exchange between the fins and the air is increased, resulting in a decrease in heat exchange efficiency. In fact, the heat exchanger described above has not been put to practical use in the outdoor unit for air conditioning.

Here, in order to prevent the above-described frost formation, heat exchange configured such that a part of the windward side of the louver on the surface of the corrugated fin provided for promoting heat transfer becomes a heat conduction suppressing portion. A device has been proposed (see, for example, Patent Document 1). In order to prevent the above-described frost formation, a heat exchanger for air conditioning in which the refrigerant flow path on the windward side of the flat heat transfer tube is closed has been proposed (see, for example, Patent Document 2).

JP 2012-72955 A Japanese Patent No. 3738404

However, since the heat exchanger described in Patent Document 1 is provided with a heat conduction suppression unit for the fin located on the windward side of the heat transfer tube, when performing a defrosting operation, heat is not easily transmitted, Fin surface temperature is unlikely to rise. For this reason, it takes time for the frost on the fins to melt, and the defrosting time becomes longer.

Further, in the air conditioner heat exchanger described in Patent Document 2, since the refrigerant does not flow in the refrigerant flow path in the heat transfer tube located on the windward side of the heat transfer tube, when performing the defrosting operation, Patent Document 1 As in the heat exchanger described in 1., the fin surface temperature on the windward side of the heat transfer tube is unlikely to rise, and the defrosting time becomes long.

As described above, the techniques described in

Patent Documents

1 and 2 have a problem that the defrosting efficiency is poor and as a result, the heating efficiency is lowered. Moreover, when performing cooling operation, there also existed a subject that the effective windward side temperature difference area | region of an outdoor heat exchanger may reduce efficiency.

The present invention has been made against the background of the problems described above, and provides a heat exchanger and a heat exchanger manufacturing method that can improve the defrosting efficiency than before and suppress frosting than before. It is intended to provide.

The heat exchanger according to the present invention is a heat exchanger for exchanging heat between the refrigerant flowing inside and the air flowing around, and each of the plurality of heat transfer tubes extending linearly and each of both ends of the plurality of heat transfer tubes Each of the plurality of heat transfer tubes has openings at both ends and has a plurality of refrigerant flow paths through which the refrigerant flows, In at least one end connected to the header in the longitudinal direction of the plurality of heat transfer tubes, the opening provided in a part of the part including the part located on the most upstream side of the air flow is at the one end. The opening of the remaining part to be provided and the inside of the header have different orientations.

The manufacturing method of the heat exchanger according to the present invention includes a first step of inserting the plurality of heat transfer tubes into one arcuate member of two arcuate members having an arcuate cross section constituting the hollow tubular header, After the first step, a part of the plurality of heat transfer tubes including the heat transfer tube located on the most upstream side of the air flow is left with an opening provided at one end located on the one header side. The second step of bending so as to be located on the other end side of the opening provided on the one header side of the portion of the portion, and the bent portion of the plurality of heat transfer tubes after the second step And a third step of producing the header by combining the one arcuate member and the other arcuate member so as to be located inside the header.

According to the present invention, during the defrosting operation, the gas refrigerant flowing into the heat exchanger functioning as an evaporator flows through the inside of the heat transfer tube located on the windward side of the heat transfer tube, compared to the conventional heat transfer tube. In the heating operation, the gas refrigerant that has flowed into the heat exchanger that functions as an evaporator flows through the inside of the heat transfer tube located on the windward side of the heat transfer tube, compared with the conventional heat transfer tube. The heat exchange in can be suppressed. Therefore, the defrosting efficiency can be improved as compared with the conventional case, and frost formation can be suppressed as compared with the conventional case.

1 is a configuration diagram of a refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. It is an external view of the outdoor heat exchanger 5 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. It is a perspective view which shows the outline | summary of the outdoor heat exchanger 5 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. It is a figure which shows the header 10 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. It is a figure which shows the header 11 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. It is a figure which shows the mode of the frost on the fin 13 of the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. It is a figure which shows the relationship between the refrigerant | coolant flow path of the heat exchanger tube 12, and the temperature of the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. It is a figure which shows the relationship between the refrigerant | coolant flow path of the heat exchanger tube 12, and the heat exchange amount of the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. It is a figure which shows the relationship between the refrigerant flow path of the heat exchanger tube 12, and the refrigerant | coolant flow rate of the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. It is the perspective view and front sectional drawing explaining the assembly process of the header 10 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. It is the perspective view and front sectional drawing explaining the assembly process of the header 10 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. It is the perspective view and front sectional drawing explaining the assembly process of the header 10 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. It is a perspective view of the heat exchanger tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. It is a figure which shows the header 10 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 2 of this invention. It is a figure which shows the header 11 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 2 of this invention. It is a perspective view of the heat exchanger tube 12 of the refrigeration cycle apparatus 100 which concerns on Embodiment 2 of this invention. It is the front view and perspective view which show the shape of the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 3 of this invention. It is the front view and perspective view which show the shape of the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 3 of this invention. It is the front view and perspective view which show the shape of the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 4 of this invention. It is the front view and perspective view which show the shape of the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 4 of this invention. It is a figure which shows the header 10 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 5 of this invention. It is a perspective view which shows the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 5 of this invention. It is a perspective view which shows the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 5 of this invention. It is a figure which shows the 1st example of the shape of the heat exchanger tube 12 and the header 10 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 6 of this invention. It is a figure which shows the 2nd example of the shape of the heat exchanger tube 12 and the header 10 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 6 of this invention. It is an external view of the outdoor heat exchanger 5 of the refrigeration cycle apparatus 100 according to Embodiment 7 of the present invention. It is a figure which shows the header 10 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 7 of this invention. It is a figure which shows the header 11 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 7 of this invention. It is a figure which shows the header 110 and the heat exchanger tube 112 of the conventional refrigeration cycle apparatus. It is a figure which shows the header 111 and the heat exchanger tube 112 of the conventional refrigeration cycle apparatus. It is a figure which shows the mode of the frost on the fin 113 of the heat exchanger tube 112 of the conventional refrigeration cycle apparatus. It is a figure which shows the relationship between the refrigerant | coolant flow path of the heat exchanger tube 112 of the conventional refrigeration cycle apparatus, and the temperature of the heat exchanger tube 112. FIG. It is a figure which shows the relationship between the refrigerant | coolant flow path of the heat exchanger tube 112 and the heat exchange amount of the heat exchanger tube 112 of the conventional refrigeration cycle apparatus. It is a figure which shows the relationship between the refrigerant | coolant flow path of the heat exchanger tube 112 of the conventional refrigeration cycle apparatus, and the refrigerant | coolant flow volume of the heat exchanger tube 112. FIG.

Hereinafter, modes for carrying out the present invention will be described with reference to the drawings. Here, in the following drawings including FIG. 1, the same reference numerals denote the same or corresponding parts, and are common to all the embodiments described below. And the form of the component represented by the whole specification is an illustration to the last, Comprising: It does not limit to the form described in the specification.

Embodiment 1 FIG.
FIG. 1 is a configuration diagram of a refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. As shown in FIG. 1, the refrigeration cycle apparatus 100 includes a compressor 1, a four-way valve 2, an indoor heat exchanger 3, an expansion valve 4, and an outdoor heat exchanger 5.

The compressor 1 is a variable capacity compressor that compresses sucked refrigerant and discharges it as a high-temperature and high-pressure refrigerant. The four-way valve 2 is for switching the refrigerant flow path provided on the discharge side of the compressor 1. In FIG. 1, the refrigerant flow in a state where the four-way valve 2 is switched so as to perform the heating operation is indicated by a solid line. Moreover, in FIG. 1, the refrigerant | coolant flow in the state in which the four-way valve 2 was switched so that a defrost operation may be performed is shown with the dotted line.

The indoor heat exchanger 3 is a heat exchanger that functions as an evaporator during cooling operation and functions as a condenser during heating operation. The expansion valve 4 is for decompressing and expanding the refrigerant flowing out of the outdoor heat exchanger 5 during the cooling operation and decompressing and expanding the refrigerant flowing out of the indoor heat exchanger 3 during the heating operation. The outdoor heat exchanger 5 is a heat exchanger that functions as a condenser during cooling operation and functions as an evaporator during heating operation.

Hereinafter, the refrigerant flow when the heating operation is performed in the refrigeration cycle apparatus 100 will be described. When performing the heating operation, the four-way valve 2 is switched to the heating side, the indoor heat exchanger 3 functions as a condenser, and the outdoor heat exchanger 5 functions as an evaporator.

First, the refrigerant supplied to the compressor 1 is compressed to become a high-temperature and high-pressure gas refrigerant, passes through the four-way valve 2, and flows into the indoor heat exchanger 3. The refrigerant that has flowed into the indoor heat exchanger 3 is cooled and liquefied by heat exchange with the indoor air introduced into the indoor heat exchanger 3. The liquefied refrigerant passes through the expansion valve 4 to become a two-phase refrigerant state in which low-temperature and low-pressure gas refrigerant and liquid refrigerant are mixed, and flows into the outdoor heat exchanger 5. The refrigerant flowing into the outdoor heat exchanger 5 returns to the compressor 1 in a state where it is heated and gasified by exchanging heat with outdoor air introduced into the outdoor heat exchanger 5. When the heating operation is executed and the cumulative amount of frost in the outdoor heat exchanger 5 increases, the defrosting operation is started.

Hereinafter, the refrigerant flow when the defrosting operation is performed in the refrigeration cycle apparatus 100 will be described. When performing the defrosting operation, the four-way valve 2 is switched to the cooling side, the indoor heat exchanger 3 functions as an evaporator, and the outdoor heat exchanger 5 functions as a condenser. The refrigerant flow during the defrosting operation is in the opposite direction to the refrigerant flow during the heating operation.

First, the refrigerant supplied to the compressor 1 is compressed to become a high-temperature and high-pressure gas refrigerant, passes through the four-way valve 2, and flows into the outdoor heat exchanger 5. The refrigerant that has flowed into the outdoor heat exchanger 5 is cooled and liquefied by exchanging heat with the indoor air introduced into the outdoor heat exchanger 5. The liquefied refrigerant passes through the expansion valve 4 to become a two-phase refrigerant state in which low-temperature and low-pressure gas refrigerant and liquid refrigerant are mixed, and flows into the indoor heat exchanger 3. The refrigerant flowing into the indoor heat exchanger 3 returns to the compressor 1 in a state of being heated and gasified by exchanging heat with outdoor air introduced into the indoor heat exchanger 3.

FIG. 2 is an external view of the outdoor heat exchanger 5 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. FIG. 3 is a perspective view showing an outline of the outdoor heat exchanger 5 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. The arrows in FIGS. 2 and 3 indicate the flow of air. The air passes through the gaps between the fins by driving the blowing means (not shown).

As shown in FIG. 2, the outdoor heat exchanger 5 includes

headers

10 and 11, heat transfer tubes 12, and fins 13. The header 10 is provided below the outdoor heat exchanger 5, and the header 11 is provided below the outdoor heat exchanger 5. The

headers

10 and 11 are configured in, for example, a hollow cylindrical shape. The heat transfer tube 12 has a plurality of flow paths through which the refrigerant flows and has a flat shape extending linearly and is inserted into the

headers

10 and 11. In addition, the fin 13 is a corrugated fin, for example, and is closely intervened in the gap between the adjacent heat transfer tubes 12.

As shown in FIG. 2, the header 10 is connected to the refrigerant pipe 101. The refrigerant pipe 101 is connected to the expansion valve 4. The header 11 is connected to the refrigerant pipe 102. The refrigerant pipe 102 is connected to the four-way valve 2.

In addition, the heat transfer tube 12 is not limited to the example configured to have a plurality of refrigerant flow paths, and each of the plurality of heat transfer tubes may be configured to have a single refrigerant flow path. Moreover, the fin 13 is not limited to the above-mentioned example, A plate type fin may be used and the finless type which does not use a fin may be employ | adopted.

Here, during the heating operation, the gas-liquid two-phase refrigerant flows into the header 10 through the refrigerant pipe 101, and the refrigerant that has flowed into the header 10 is distributed to the heat transfer pipe 12. The gas-liquid two-phase refrigerant flowing in the heat transfer tube 12 exchanges heat with air and becomes a gas refrigerant and flows out to the header 11. The gas refrigerant that has flowed out to the header 11 is guided to the refrigerant pipe 102.

On the other hand, during the cooling operation or the defrosting operation, the gas refrigerant flows into the header 11 through the refrigerant pipe 102, and the refrigerant that has flowed into the header 11 is distributed to the plurality of heat transfer tubes 12. Then, the gas refrigerant flowing in the heat transfer tube 12 exchanges heat with air and becomes liquid refrigerant and flows out to the header 10. The liquid refrigerant that has flowed out to the header 10 is guided to the refrigerant pipe 101. Thus, the refrigerant flow during the cooling operation or the defrosting operation is in the opposite direction to the refrigerant flow during the heating operation.

As shown in FIG. 3, openings 15A to 15F are provided at the end of the heat transfer tube 12 in order from the windward side. Although FIG. 3 illustrates an example in which an opening is provided on one end side of the heat transfer tube 12, the opening is similarly provided on the other end side of the heat transfer tube 12. Further, as shown in FIG. 3, a plurality of refrigerant flow paths 15 are provided inside the heat transfer tube 12. Among the plurality of refrigerant channels 15, the

refrigerant channels

15a, 15b, 15c, 15d, 15e, and 15f are sequentially called from the windward side. In the following description, the

refrigerant channels

15a, 15b, and 15c may be referred to as refrigerant channels 15a to 15c. In the following description, the

refrigerant channels

15d, 15e, and 15f may be referred to as refrigerant channels 15d to 15f.

The portion on the windward side of the heat transfer tube 12 is referred to as the windward heat transfer tube 12a. A portion on the windward side of the fin 13 is referred to as a windward fin 13a. A louver 14 is provided on the surface of the fin 13. The louver 14 has a shape cut and raised so as to promote heat transfer.

Since the two-phase refrigerant mixed with the gas refrigerant and the liquid refrigerant flows into the outdoor heat exchanger 5 during the heating operation as described above, the refrigerant is distributed from the header 10 to the plurality of refrigerant flow paths 15 of the heat transfer pipe 12. Depending on the relationship between the header 10 and the refrigerant flow path 15, there are flows in which the flow rate ratio of the refrigerant flowing in each refrigerant flow path 15 and the ratio of the gas refrigerant and the liquid refrigerant are different.

FIG. 4 is a diagram showing the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. FIG. 5 is a diagram showing the header 11 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. FIG. 6 is a diagram showing a state of frost on the fins 13 of the heat transfer tubes 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. In the first embodiment, among the gas refrigerant and liquid refrigerant supplied to the header 10, there is a flow such as a laminar flow, a wavy flow, a bubble flow, and a plug flow in which the gas refrigerant is likely to collect on the upper portion of the header 10. It is assumed that it will occur.

As shown in FIG. 4, liquid refrigerant is accumulated in the lower part of the header 10, and gas refrigerant is accumulated in the upper part of the header 10. For example, in the portion having the refrigerant flow paths 15a to 15c in the heat transfer tube 12, the opening provided at the lower end is located above the liquid level of the liquid refrigerant and is opposite to the traveling direction of the gas refrigerant inside the header 10. It is bent to face the direction. For example, the portion having the refrigerant flow paths 15d to 15f in the heat transfer tube 12 is configured such that the opening provided at the lower end is positioned below the liquid level of the liquid refrigerant.

In addition, in the above description, although the example in which the site | part which has the refrigerant flow paths 15a-15c among the heat exchanger tubes 12 was bent was demonstrated, it is not limited to this. For example, only the heat transfer tube having the refrigerant flow path 15a among the heat transfer tubes 12 may be bent. What is necessary is just to be the structure which bends the site | part which has 1 or 2 or more continuous refrigerant | coolant flow paths 15 including the refrigerant flow path 15 located in the most upstream side of the air flow among the heat exchanger tubes 12. FIG.

By configuring the heat transfer tube 12 as shown in FIG. 4, the gas refrigerant flowing inside the header 10 is likely to flow into the refrigerant flow paths 15a to 15c due to inertial force. On the other hand, the liquid refrigerant flowing under the header 10 is sucked into the refrigerant flow paths 15d to 15f. That is, the two-phase refrigerant flowing through the refrigerant flow paths 15d to 15f has a smaller gas refrigerant ratio than the two-phase refrigerant flowing through the refrigerant flow paths 15a to 15c. The two-phase refrigerant that has passed through the refrigerant flow paths 15a to 15f exchanges heat with air, changes to a gas single-phase refrigerant, and is supplied to the header 11.

As shown in FIG. 5, a gas refrigerant is stored inside the header 11. For example, portions of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c are configured to extend linearly. For example, a portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f is bent so as to face the direction opposite to the traveling direction of the gas refrigerant inside the header 11. As a result, the in-tube pressure loss of the refrigerant channels 15a to 15c and the refrigerant channels 15d to 15f are equal, or the in-tube pressure loss of the refrigerant channels 15d to 15f is made larger than that of the refrigerant channels 15a to 15c. The flow rate of the gas refrigerant flowing to ˜15c can be increased. This is because, when comparing two-phase refrigerants of the same flow rate, the pressure loss in the pipe increases as the proportion of the gas refrigerant increases, and the part of the heat transfer pipe 12 having the refrigerant flow paths 15a to 15c is bent. This is to prevent the flow rate of the refrigerant flow paths 15a to 15c in the heat transfer tube 12 from being reduced due to an increase in pressure loss.

By configuring the heat transfer tube 12 as shown in FIG. 4, during the heating operation, the two-phase refrigerant flowing through the refrigerant flow paths 15a to 15c is more gas than the two-phase refrigerant flowing through the refrigerant flow paths 15d to 15f. The two-phase refrigerant flowing through the refrigerant flow paths 15d to 15f has a smaller ratio of the gas refrigerant than the two-phase refrigerant flowing through the refrigerant flow paths 15a to 15c. For this reason, the heat exchange amount in which the refrigerant flowing through the refrigerant flow path provided on the windward side of the heat transfer tube 12 exchanges heat with air can be suppressed, and as shown in FIG. It becomes uniform from the upper side toward the leeward side.

By configuring the heat transfer tube 12 as shown in FIG. 5, when the gas single-phase refrigerant inside the header 11 is supplied to the refrigerant channel 15 during the cooling operation or the defrosting operation, the refrigerant channel 15 a Since the refrigerant flowing through the refrigerant channels 15-15c is larger than the refrigerant flowing through the refrigerant channels 15d-15f, the amount of heat exchange in the refrigerant channels 15a-15c can be increased.

FIG. 7 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 12 and the temperature of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. FIG. 8 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 12 and the heat exchange amount of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. FIG. 9 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 12 and the refrigerant flow rate of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.

7, the horizontal axis of the heat transfer tube 12 is defined on the horizontal axis, and the temperature of the heat transfer tube 12 is defined on the vertical axis of FIG. 7. The horizontal axis in FIG. 8 defines the refrigerant flow path of the heat transfer tube 12, and the vertical axis in FIG. 8 defines the heat exchange amount of the heat transfer tube 12. The horizontal axis of FIG. 9 defines the refrigerant flow path of the heat transfer tube 12, and the vertical axis of FIG. 9 defines the refrigerant flow rate of the heat transfer tube 12.

As shown in FIG. 7, the temperature of the refrigerant is constant from the windward side of the refrigerant channel to the leeward side of the refrigerant channel. As shown in FIG. 7, the temperature of the air decreases as it goes from the windward side of the refrigerant flow path to the leeward side of the refrigerant flow path. As shown in FIG. 8, the heat exchange amount of the outdoor heat exchanger 5 is increased from the windward side of the refrigerant flow path toward the leeward side of the refrigerant flow path.

As shown in FIG. 9, the flow rate of the gas refrigerant flowing inside the heat transfer tube 12 decreases from the windward side of the refrigerant flow path toward the leeward side of the refrigerant flow path. As shown in FIG. 9, the flow rate of the liquid refrigerant flowing inside the heat transfer tube 12 increases from the windward side of the refrigerant flow path to the leeward side of the refrigerant flow path.

In the first embodiment, as shown in FIG. 7, even if the temperature difference between the refrigerant temperature on the windward side and the air temperature is large, the amount of heat exchange on the windward side is suppressed and the heat exchange on the leeward side is suppressed as shown in FIG. To promote the amount. Therefore, in the first embodiment, as shown in FIG. 9, the two-phase refrigerant having a high ratio of gas refrigerant flows through the refrigerant channel on the leeward side, and the two-phase refrigerant having a high ratio of liquid refrigerant is the refrigerant on the leeward side. By flowing through the flow path, heat exchange on the leeward side that can obtain more latent heat of the refrigerant is promoted. Further, as the air flowing on the fins 13 flows from the upstream side to the downstream side, the amount of water vapor that the air has decreases.

FIG. 10 is a perspective view and a front sectional view for explaining an assembly process of the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. FIG. 11 is a perspective view and a front sectional view for explaining an assembly process of the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. FIG. 12 is a perspective view and a front sectional view for explaining an assembly process of the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.

As shown in FIG. 10, the header 10 includes, for example, an arc member 10a and an arc member 10b. The arc-shaped member 10a and the arc-shaped member 10b are configured by, for example, members having a cross-sectional arc shape. Below, the process of assembling the header 10 and the heat transfer tube 12 will be described.

First, the heat transfer tube 12 is inserted into the arc-shaped member 10a as shown in FIG. 10, for example, in a state where there is a cut in the longitudinal direction of the heat transfer tube 12 between the refrigerant flow channel 15c and the refrigerant flow channel 15d. Is done. Among the inserted heat transfer tubes 12, one of the end portions of the heat transfer tubes 12 corresponding to the refrigerant flow paths 15a to 15c is bent in the longitudinal direction of the header by a bending machine, for example, as shown in FIG. It becomes a state.

Next, as shown in FIG. 11, in a state where the heat transfer tube 12 is inserted into the arcuate member 10a and a part of the heat transfer tube 12 is bent, the arcuate member 10a and the arcuate member 10b are fitted to each other to fit the header 10. Is formed. Specifically, for example, the fitting of the arc-shaped member 10a and the arc-shaped member 10b is performed by, for example, a belt conveyor type integrated brazing process or the like. As a result, the state shown in FIG. 12 is obtained.

The above-described assembly process is not limited to the case of the circular pipe header as shown in FIG. 12, but also in the case of a header constituted by a plurality of members, the obstacle in the process of bending the heat transfer tube 12 by the bending machine. As long as it is not, it can be applied. By bending the heat transfer tube 12 as described above, the heat transfer tube 12 inserted into the header 10 is thermally expanded in the course of the belt conveyor type integrated brazing process so that the heat transfer tube 12 is thermally expanded. Has the effect of solving the problem of missing from the header 10.

FIG. 13 is a perspective view of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. As shown in FIG. 13, portions of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c are bent, and portions of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f are not bent and extend in a straight line. Yes. As described above, the direction of the opening provided in the end portion on the header 10 side of the portion having the refrigerant flow paths 15a to 15c in the heat transfer tube 12 is the same as that of the heat transfer tube having the refrigerant flow paths 15d to 15f in the heat transfer tube 12. This is different from the direction of the opening provided at the end on the header 10 side.

FIG. 29 is a diagram showing a header 110 and a heat transfer tube 112 of a conventional refrigeration cycle apparatus. FIG. 30 is a diagram showing a header 111 and a heat transfer tube 112 of a conventional refrigeration cycle apparatus. FIG. 31 is a diagram showing a state of frost on the fin 113 of the heat transfer tube 112 of the conventional refrigeration cycle apparatus.

As shown in FIG. 29, the conventional heat transfer tube 112 corresponds to all the refrigerant flow paths 115, and the lower end portion located inside the header 110 extends in a straight line without being bent. In addition, as shown in FIG. 30, the conventional heat transfer tube 112 extends in a straight line without being bent at the upper end portion located inside the header 111.

FIG. 32 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 112 and the temperature of the heat transfer tube 112 of the conventional refrigeration cycle apparatus. FIG. 33 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 112 and the heat exchange amount of the heat transfer tube 112 of the conventional refrigeration cycle apparatus. FIG. 34 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 112 and the refrigerant flow rate of the heat transfer tube 112 of the conventional refrigeration cycle apparatus.

32, the horizontal axis of the heat transfer tube 12 is defined on the horizontal axis, and the temperature of the heat transfer tube 12 is defined on the vertical axis of FIG. 32. The horizontal axis of FIG. 33 defines the refrigerant flow path of the heat transfer tube 12, and the vertical axis of FIG. 33 defines the heat exchange amount of the heat transfer tube 12. The horizontal axis of FIG. 34 defines the refrigerant flow path of the heat transfer tube 12, and the vertical axis of FIG. 34 defines the refrigerant flow rate of the heat transfer tube 12.

32, the temperature of the refrigerant is constant from the windward side of the refrigerant channel to the leeward side of the refrigerant channel. As shown in FIG. 32, the temperature of the air decreases as it goes from the windward side of the refrigerant flow path to the leeward side of the refrigerant flow path. As shown in FIG. 33, the heat exchange amount of the outdoor heat exchanger 5 decreases from the windward side of the refrigerant flow path toward the leeward side of the refrigerant flow path.

As shown in FIG. 34, the flow rate of the gas refrigerant flowing inside the heat transfer tube 12 is constant from the windward side of the refrigerant flow path to the leeward side of the refrigerant flow path. As shown in FIG. 34, the flow rate of the liquid refrigerant flowing inside the heat transfer tube 12 is constant from the windward side of the refrigerant channel to the leeward side of the refrigerant channel.

When the heat transfer tube 112 is configured as shown in FIGS. 29 and 30, two-phase refrigerants having the same ratio of gas refrigerant to liquid refrigerant and the same amount are distributed from the header 110 as shown in FIG. Will be. Here, as shown in FIG. 33, the heat exchange amount of the outdoor heat exchanger 5 decreases from the windward side of the refrigerant flow path toward the leeward side of the refrigerant flow path. When the heat exchange with the refrigerant is performed while flowing through the gap, as shown in FIG. 32, the temperature difference between the air and the refrigerant is the largest in the portion located on the windward side of the heat transfer tube 112, and the windward side to the leeward side. The temperature difference between the air and the refrigerant becomes lower. For this reason, as shown in FIG. 31, the amount of heat exchange in which air and refrigerant exchange heat is the largest in the portion located on the windward side of the heat transfer tube 112, and frost is most likely to occur. And the frost accumulated on the windward side of the conventional heat transfer tube 112 eventually leads to a decrease in the air volume passing through the heat exchanger because it obstructs the air path, and the frost on the fin surface becomes a thermal resistance and the heat exchange efficiency with the air is increased. The problem of deteriorating occurs.

On the other hand, the outdoor heat exchanger 5 according to the first embodiment is a heat exchanger that exchanges heat between the refrigerant flowing inside and the air flowing around, and includes a plurality of heat transfer tubes 12 extending linearly. Each end of each of the plurality of heat transfer tubes 12 is inserted, and each of the plurality of heat transfer tubes 12 has an opening at each end so that the refrigerant flows. Provided in some parts including the part located at the most upstream side of the air flow at one end having a plurality of refrigerant flow paths inside and connected to the header 10 in the longitudinal direction of the plurality of heat transfer tubes 12 The opening to be formed has a different orientation in the inside of the header 10 and the opening of the remaining part located on the header 10 side. In particular, in one heat transfer tube 12, among a plurality of flow paths arranged in a direction intersecting with the longitudinal direction of the header 10, the openings of some of the flow paths are the openings of other flow paths and the refrigerant flow in the header 10. Try to have a different orientation to the direction. For this reason, a difference arises in the ease of a refrigerant | coolant entering into a some flow path and another flow path by the inertial force of a refrigerant | coolant flow. In the first embodiment, on the header side where the gas and the liquid are mixed, the difference in the height position in the header 10 is also used between the openings of some of the flow paths and the openings of the other flow paths. However, the distribution of the refrigerant gas and liquid inside the header may be various. In particular, when the distribution is not determined in the height direction, it is not always necessary to change the height of the opening between the flow paths. Moreover, it is not necessary to change the height position even in the header through which only the gas refrigerant flows. In those cases, the difference in the direction of the opening may be used to generate gas, liquid, and inflow distribution between the flow paths. Further, in the header 10, a bent portion is formed so that the openings of some of the flow paths are different from the openings of the other flow paths, and the flow of the refrigerant is made different by making the resistance of the flow paths different. It may be. Such a difference in bending may be used for a difference in refrigerant inflow. Moreover, you may make it the direction of such an opening part differ only in one header among the headers of the both ends of the heat exchanger tube 12. FIG. By using such a structure, during the defrosting operation, the gas refrigerant flowing into the outdoor heat exchanger 5 flows inside the heat transfer tube 12 located on the windward side of the heat transfer tube 12 as compared with the conventional case. Heat exchange in the heat transfer tube 12 is promoted, and during the heating operation, the gas refrigerant flowing into the outdoor heat exchanger 5 flows through the heat transfer tube 12 located on the windward side of the heat transfer tube 12 than before. Heat exchange in the heat transfer tube 12 can be suppressed. Therefore, the defrosting efficiency can be improved as compared with the conventional case, and frost formation can be suppressed as compared with the conventional case.

Embodiment 2. FIG.
In the second embodiment, the heat transfer tube 12 is configured differently from the first embodiment. In the second embodiment, items that are not particularly described are the same as those in the first embodiment, and the same functions and configurations are described using the same reference numerals.

FIG. 14 is a diagram showing the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 2 of the present invention. FIG. 15 is a diagram showing the header 11 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 2 of the present invention. FIG. 16 is a perspective view of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 2 of the present invention.

As shown in FIG. 14, the portion of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c is bent so that the lower end thereof faces in the direction opposite to the refrigerant flow direction in the header 10. Further, as shown in FIG. 14, the portion having the refrigerant flow paths 15 d to 15 f in the heat transfer tube 12 is bent so that the lower end thereof faces the same direction as the refrigerant flow direction in the header 10. As shown in FIG. 15, the upper end of the heat transfer tube 12 extends straight without being bent.

As shown in FIG. 16, the orientation of the opening provided at the lower end of the portion having the refrigerant flow paths 15a to 15c in the heat transfer tube 12 is the lower end of the portion having the refrigerant flow paths 15d to 15f in the heat transfer tube 12. The direction is opposite to the direction of the opening provided. As a result, the gas refrigerant inside the header 10 is supplied more to the refrigerant flow paths 15a to 15c than to the refrigerant flow paths 15d to 15f.

As described above, the outdoor heat exchanger 5 according to the second embodiment has a part of the heat transfer tube 12 including a part located at the most upstream side of the air flow at least at one end in the longitudinal direction. The opening provided is configured to be in the direction opposite to the refrigerant flow direction inside the header 10, and the opening of the remaining portion located on the header 10 side is the same as the refrigerant flow direction inside the header 10. It is comprised so that it may become a direction.
For this reason, it is only necessary to bend the lower end of the heat transfer tube 12, it is not necessary to bend the upper end of the heat transfer tube 12, and for example, a circular tube having an insertion port for the heat transfer tube 12 is used. The processing can be simplified as compared with the first one.

In the second embodiment, the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f is bent so that the lower end thereof is oriented in the same direction as the refrigerant flow direction in the header 10. Pressure loss on the flow paths 15d to 15f side increases. Therefore, in the second embodiment, the gas refrigerant is less likely to enter the refrigerant flow paths 15d to 15f than in the first embodiment, and a larger amount of gas refrigerant can be supplied to the refrigerant flow paths 15a to 15c.

Embodiment 3 FIG.
In the third embodiment, unlike the first embodiment, for example, the portion having the refrigerant flow paths 15a to 15c of the heat transfer tube 12 is inserted and bent to the center height of the header 10. In Embodiment 3, items that are not particularly described are the same as those in Embodiment 1, and the same functions and configurations are described using the same reference numerals.

FIG. 17 is a front view and a perspective view showing the shape of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 3 of the present invention. FIG. 18 is a front view and a perspective view showing the shape of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 3 of the present invention. In the third embodiment, unlike the first embodiment, the gas refrigerant out of the gas-liquid two-phase refrigerant flowing inside the header 10 flows like an annular flow that tends to gather at a position corresponding to the center height of the header 10. It is assumed that this occurs.

As shown in FIG. 17, the lower end of the portion of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c is the center of the header 10 in the radial direction than the lower end of the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f. It is bent so that it is located on the side. Also, as shown in FIG. 17, the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f is such that the position of the opening provided at the lower end thereof is shortened to the height near the side wall of the header 10. It is configured by cutting.

Thus, the orientation of the opening provided at the lower end of the portion having the refrigerant flow paths 15a to 15c in the heat transfer tube 12 is the opening provided at the lower end of the portion of the heat transfer pipe 12 having the refrigerant flow paths 15d to 15f. Unlike the above, the gas refrigerant inside the header 10 is supplied to the refrigerant flow paths 15a to 15c more than the refrigerant flow paths 15d to 15f.

As shown in FIG. 18, the lower end of the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f is smaller in diameter of the header 10 than the lower end of the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f. You may comprise so that it may extend linearly so that it may be located in the direction center side. At this time, as shown in FIG. 18, the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f is arranged such that the position of the opening provided at the lower end thereof is located at a height near the side wall of the header 10. It is bent.

As described above, in the outdoor heat exchanger 5 according to the third embodiment, the header 10 has a hollow cylindrical shape, and is connected to the header 10 in the longitudinal direction of the plurality of heat transfer tubes 12. The openings provided in some parts including the part located on the most upstream side of the air flow are located closer to the center side in the radial direction of the header 10 than the openings of the remaining parts located on the header 10 side. Yes. For this reason, in this Embodiment 3, it can be set as the header 10 with a small cross-sectional area where an annular flow tends to occur, and the cost of the header 10 can be reduced. In the third embodiment, as in the first embodiment, more gas refrigerant in the header 10 is supplied to the refrigerant flow paths 15a to 15c than to the refrigerant flow paths 15d to 15f.

Embodiment 4 FIG.
In the fourth embodiment, unlike the first embodiment, the flat surface of the heat transfer tube 12 is cut open, for example, to the half surface in the minor axis direction. In the fourth embodiment, items not particularly described are the same as those in the first embodiment, and the same functions and configurations are described using the same reference numerals.

FIG. 19 is a front view and a perspective view showing the shape of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 4 of the present invention. FIG. 20 is a front view and a perspective view showing the shape of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 4 of the present invention.

As shown in FIG. 19, for example, the portion of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c has a through portion 12A in which a portion located inside the header 10 penetrates from the outer surface to the inner surface. It is configured. With this configuration, the gas refrigerant inside the header 10 is supplied more to the refrigerant flow paths 15a to 15c than to the refrigerant flow paths 15d to 15f.

Note that, as shown in FIG. 20, the portion located on the upper end side by a predetermined distance from the lower end of the header 10 is not provided with the penetration portion 12A, and the location where the penetration portion 12A is provided more than in FIG. Good. Even if it does in this way, there can exist an effect similar to the case where it is set as a structure like FIG.

As described above, the outdoor heat exchanger 5 according to the fourth embodiment has a portion located on the most upstream side of the air flow at one end located on the header 10 side in the longitudinal direction of the plurality of heat transfer tubes 12. Some of the parts including the through-hole 12 </ b> A have a part located inside the header 10 cut out from the outer surface to the inner surface.
For this reason, in the fourth embodiment, unlike the first embodiment, the process of inserting the heat transfer tube 12 into the header 10 and bending the portion of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c is performed. Without it, the outdoor heat exchanger 5 can be manufactured. Therefore, this Embodiment 4 can manufacture the outdoor heat exchanger 5 by a simpler process than Embodiment 1. FIG. In the fourth embodiment, the same effect as in the first embodiment can be obtained.

Embodiment 5 FIG.
In the fifth embodiment, unlike the fourth embodiment, the lower end of the heat transfer tube 12 is bent in the same direction as the refrigerant inflow direction in the header 10. In the fifth embodiment, items that are not particularly described are the same as those in the fourth embodiment, and the same functions and configurations are described using the same reference numerals.

FIG. 21 is a diagram showing the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 5 of the present invention. FIG. 22 is a perspective view showing heat transfer tube 12 of refrigeration cycle apparatus 100 according to Embodiment 5 of the present invention. FIG. 23 is a perspective view showing heat transfer tube 12 of refrigeration cycle apparatus 100 according to Embodiment 5 of the present invention.

As shown in FIGS. 21 to 23, in the heat transfer tube 12, the opening provided at the lower end is positioned above the liquid level of the liquid refrigerant in the header 10, and the traveling direction of the gas refrigerant in the header 10 is as follows. It is bent to face the same direction. Further, the portions having the refrigerant flow paths 15a to 15c in the heat transfer tubes 12 shown in FIGS. 22 and 23 are the same as the portions having the refrigerant flow paths 15a to 15c in the heat transfer tubes 12 shown in FIGS. In addition, the structure has a through portion 12A.

At this time, since the opening provided at the lower end of the portion having the refrigerant flow paths 15d to 15f in the heat transfer tube 12 is located in the direction opposite to the direction of the refrigerant flowing through the header 10, the refrigerant loses pressure loss. The gas refrigerant becomes difficult to flow. On the other hand, since the opening provided at the lower end of the portion having the refrigerant flow paths 15a to 15c in the heat transfer tube 12 is located in the same direction as the direction of refrigerant flowing through the header 10, the structure in which gas refrigerant flows easily It has become.

As described above, the outdoor heat exchanger 5 according to the fifth embodiment is cut out in the heat transfer tube 12 and bent in the same direction as the refrigerant inflow direction in the header 10 as in the configuration of the fourth embodiment. It is a thing. Therefore, in the fifth embodiment, the height of the refrigerant inserted into the header 10 can be shortened while obtaining the same effect as in the first to third embodiments. Therefore, the total pressure loss of the refrigerant passing through the outdoor heat exchanger 5 can be reduced.

Embodiment 6 FIG.
In the sixth embodiment, unlike the first to fifth embodiments, the shape of the header 10 into which the heat transfer tube 12 is inserted has a shape that becomes narrower in the insertion direction of the heat transfer tube 12. In the sixth embodiment, items not particularly described are the same as those in the first to fifth embodiments, and the same functions and configurations are described using the same reference numerals.

FIG. 24 is a diagram showing a first example of the shape of the heat transfer tube 12 and the header 10 of the refrigeration cycle apparatus 100 according to Embodiment 6 of the present invention. FIG. 25 is a diagram showing a second example of the shape of the heat transfer tube 12 and the header 10 of the refrigeration cycle apparatus 100 according to Embodiment 6 of the present invention.

As shown in FIG. 24, the header 10 is configured to have a triangular cross section. Specifically, the header 10 may be provided such that one of the sides is located at the bottom and the top facing the above-described bottom is located at the top.

Note that, as shown in FIG. 25, the header 10 may have a hexagonal cross section. Specifically, the header 10 may be provided such that one of the sides is positioned at the lowest position as the bottom and the top portion facing the above-described bottom is positioned at the highest position.

As described above, the outdoor heat exchanger 5 according to the sixth embodiment configures the header 10 so that the horizontal internal cross-sectional area decreases from the lower end side of the heat transfer tube 12 toward the upper end side of the heat transfer tube 12. is doing. For this reason, it becomes easy to accumulate gas refrigerant above the inside of the header 10, and the effects of the first, second, and fourth embodiments can be further exhibited.

In the third to sixth embodiments described above, if necessary, the upper end of the heat transfer tube 12 is bent or the flow path length is shortened so as to correspond to a plurality of refrigerant flow paths so that the pressure losses are different. It is good also as a structure cut | disconnected.

Embodiment 7 FIG.
In the seventh embodiment, unlike the first to sixth embodiments, the shape of the outdoor heat exchanger 5 is changed. In the seventh embodiment, items not particularly described are the same as those in the first to sixth embodiments, and the same functions and configurations are described using the same reference numerals.

FIG. 26 is an external view of the outdoor heat exchanger 5 of the refrigeration cycle apparatus 100 according to Embodiment 7 of the present invention. As shown in FIG. 26, the

headers

10 and 11 are provided in the vertical direction, and the heat transfer tubes 12 are provided in the horizontal direction.

FIG. 27 is a diagram showing the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 7 of the present invention. FIG. 28 is a diagram showing the header 11 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 7 of the present invention. In FIG. 27, a case where liquid refrigerant is accumulated on the inner wall side of the header 10 in the header 10 and gas refrigerant is accumulated in the direction away from the inner wall of the header 10 inside the header 10 will be described as an example.

As shown in FIG. 27, the gas-liquid two-phase refrigerant flows in the header 10 from below to above. A portion of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c is bent so as to face the direction opposite to the refrigerant flow direction. Thereby, the gas refrigerant inside the header 10 is easily supplied to the refrigerant flow paths 15a to 15c.

As shown in FIG. 28, the gas refrigerant flows in the header 11 from below to above. Parts of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f are bent so as to face the same direction as the refrigerant flow direction.

As described above, in the refrigeration cycle apparatus 100 according to the seventh embodiment, one end located on the header 10 side among the longitudinal ends of the plurality of heat transfer tubes 12 is the interior of the header 10, as in the first embodiment. Of the plurality of heat transfer tubes 12, the openings provided in a part of the plurality of heat transfer tubes 12 including the part located on the most upstream side of the air flow are the openings of the remaining parts located on the header 10 side and the header 10. It has a different orientation inside. For this reason, also in this Embodiment 7, the same effect as Embodiment 1 can be show | played.

In the above description, the example in which the heat exchanger is the outdoor heat exchanger 5 has been described, but the present invention is not limited to this. The present invention can be similarly applied to the case where the heat exchanger is an indoor heat exchanger.

The refrigeration cycle apparatuses 100 of Embodiments 1 to 7 described above can be applied to, for example, a heat pump apparatus, a hot water supply apparatus, a refrigeration apparatus, and the like.

1 compressor, 2-way valve, 3 indoor heat exchanger, 4 expansion valve, 5 outdoor heat exchanger, 10 header, 10a, 10b arc member, 11 header, 12 heat transfer tube, 12A through section, 12a upwind heat transfer tube, 13 fin, 13a upwind fin, 14 louver, 15, 15a-15f refrigerant flow path, 15A-15F opening, 100 refrigeration cycle device, 101 refrigerant piping, 102 refrigerant piping, 110 header, 111 header, 112 heat transfer tube, 113 Fin, 115 refrigerant flow path.

Claims

A heat exchanger that exchanges heat between refrigerant flowing inside and air flowing around.
A plurality of heat transfer tubes extending in a straight line;
Each end of each of the plurality of heat transfer tubes is inserted, and each includes a hollow header that constitutes a flow path of the refrigerant,
Each of the plurality of heat transfer tubes has openings at both ends, and has a plurality of refrigerant flow paths through which the refrigerant flows,
In at least one end connected to the header in the longitudinal direction of the plurality of heat transfer tubes, the opening provided in a part of the part including the part located on the most upstream side of the air flow is at the one end. The heat exchanger which becomes a different direction in the inside of the said opening part and the said header of the remaining site | parts provided.
At least one end in the longitudinal direction of the plurality of heat transfer tubes, the opening provided in a part of the part including the part located at the most upstream side of the air flow is opposite to the refrigerant flow direction inside the header. The heat exchanger according to claim 1, wherein the heat exchanger is configured as follows.
At least one end in the longitudinal direction of the plurality of heat transfer tubes, the opening provided in a part of the part including the part located at the most upstream side of the air flow is the opening of the remaining part provided at the one end. The heat exchanger according to claim 1 or 2, wherein the heat exchanger is located on a radial center side of the header rather than a portion.
At least one end in the longitudinal direction of the plurality of heat transfer tubes, some of the parts including the part located at the most upstream side of the air flow are notched from the outer surface to the inner surface. The heat exchanger according to claim 1, wherein the heat exchanger is configured to have a penetrating portion.
The heat exchanger according to claim 4, wherein at least one end in the longitudinal direction of the plurality of heat transfer tubes is bent in the same direction as the refrigerant flow direction inside the header.
The heat exchanger according to any one of claims 1 to 5, wherein the header into which one end in the longitudinal direction of the plurality of heat transfer tubes is inserted is provided below the heat transfer tubes.
The header provided below the heat transfer tube is:
The heat exchanger according to claim 6, wherein a horizontal internal cross-sectional area is reduced from a lower end side of the heat transfer tube toward an upper end side of the heat transfer tube.
The said opening part of the remaining site | part provided in the said one end is comprised so that it may become the same direction as a refrigerant | coolant flow direction inside the said header. Claim 1, Claim 2, Claim 3, Claim 6, or The heat exchanger according to claim 7.
A method of manufacturing a heat exchanger according to any one of claims 1 to 8,
A first step of inserting the plurality of heat transfer tubes into one arcuate member of two arcuate members having an arcuate cross section constituting the hollow cylindrical header;
After the first step, an opening provided at one end of the plurality of heat transfer tubes including the heat transfer tube located on the most upstream side of the air flow is provided at one end located on the one header side. A second step of bending so as to be positioned on the other end side than the opening provided on the one header side of the remaining portion;
After the second step, the third step of producing the header by combining the one arcuate member and the other arcuate member so that the bent portion of the plurality of heat transfer tubes is located inside the header. And a method of manufacturing a heat exchanger.