JP7050538B2 - Heat exchanger and air conditioner - Google Patents

Description

The present invention relates to heat exchangers and air conditioners.

Conventionally, in an air conditioner or the like, a heat exchanger having a plurality of fins and a heat transfer tube arranged in a flow of air supplied by a blower (fan) has been used. Multiple fins are stacked on top of each other. The heat transfer tube penetrates a plurality of fins. An air conditioner provided with this heat exchanger is described in, for example, Japanese Patent Application Laid-Open No. 2011-122819 (Patent Document 1). The air conditioner described in this publication is a four-way ceiling cassette type air conditioner capable of blowing out in four directions while being embedded in the ceiling.

Japanese Unexamined Patent Publication No. 2011-122819

In the air conditioner described in the above publication, the product width of the heat exchanger is long. This product width is the length of the heat exchanger in the direction in which a plurality of fins are stacked. When the product width of the heat exchanger is long, a temperature difference is likely to occur in the heat transfer tube between the inlet and the outlet of the liquid single-phase portion where the refrigerant becomes the liquid single-phase in the heat exchanger. When a temperature difference occurs in the heat transfer tube between the inlet and the outlet of the liquid single-phase portion, the amount of heat exchanged between the refrigerants flowing through the heat transfer tube between the inlet and the outlet of the liquid single-phase portion increases. Therefore, there is a problem that the performance of the heat exchanger cannot be fully exhibited.

The present invention has been made in view of the above problems, and an object thereof is a heat exchanger capable of suppressing heat transfer generated between refrigerants flowing through a heat transfer tube at an inlet and an outlet of a liquid single phase portion. It is to provide an air conditioner equipped with it.

The heat exchanger according to the present invention has a plurality of fins laminated to each other and a heat transfer tube penetrating the plurality of fins, and exchanges heat between the refrigerant flowing inside the heat transfer tube and the air flowing outside the heat transfer tube. By making it condense the refrigerant. The heat exchanger includes a first heat exchange unit and a second heat exchange unit that faces the first heat exchange unit and is arranged leeward of the first heat exchange unit in the air flow. The second heat exchange unit has a first end and a second end, and extends continuously from the first end to the second end. The first heat exchange unit has a first heat exchange region and a second heat exchange region arranged along the direction in which the second heat exchange unit extends. The second heat exchange region is separated from the first heat exchange region along the direction in which the second heat exchange portion extends. The heat transfer tubes of the first heat exchange region and the second heat exchange region are adjacent to each other in the step direction and are folded back along the direction in which the second heat exchange portion extends.

According to the heat exchanger of the present invention, in the first heat exchange section, the second heat exchange region is separated from the first heat exchange region along the direction in which the second heat exchange section extends. Therefore, it is possible to suppress heat transfer generated between the refrigerants flowing through the heat transfer tube at the inlet and outlet of the liquid single-phase portion. Therefore, the performance of the heat exchanger can be improved.

It is a figure which shows schematic the refrigerating cycle in the cooling operation of the air conditioner which concerns on Embodiment 1 of this invention. It is a figure which shows the refrigerating cycle in the heating operation of the air conditioner which concerns on Embodiment 1 of this invention. It is a top view which shows schematic structure of the heat exchanger which concerns on Embodiment 1 of this invention. It is a perspective view which shows schematic structure of the heat exchanger which concerns on Embodiment 1 of this invention. It is a figure which shows schematic the path of the heat exchanger which concerns on Embodiment 1 of this invention. It is a developed view schematically showing the 1st heat exchange part of the heat exchanger which concerns on Embodiment 1 of this invention. It is a top view which shows schematic structure of the heat exchanger which concerns on a comparative example. It is a perspective view which shows schematic structure of the heat exchanger which concerns on a comparative example. It is a figure which shows schematicly the path of the heat exchanger which concerns on a comparative example. It is a developed view schematically showing the 1st heat exchange part of the heat exchanger which concerns on a comparative example. It is a developed view schematically showing the 1st heat exchange part of the heat exchanger which concerns on Embodiment 1 of this invention. It is a top view which shows schematic structure of the heat exchanger which concerns on Embodiment 3 of this invention. It is a developed view schematically showing the 1st heat exchange part of the heat exchanger which concerns on Embodiment 3 of this invention. It is a developed view schematically showing the 1st heat exchange part of the heat exchanger which concerns on the modification of Embodiment 3 of this invention. It is a perspective view schematically showing the state which the indoor unit of the air conditioner which concerns on Embodiment 4 of this invention is installed in the ceiling. It is sectional drawing which follows the XVI-XVI line of FIG.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Embodiment 1.
The configuration of the air conditioner 100 according to the first embodiment of the present invention will be described with reference to FIG. 1. FIG. 1 is a schematic view showing the configuration of the air conditioner 100 according to the present embodiment. Further, FIG. 1 is a schematic diagram of a refrigeration cycle in the cooling operation of the air conditioner 100 according to the present embodiment.

As shown in FIG. 1, the air conditioner 100 includes a compressor 1, an outdoor unit heat exchanger 2, an expansion valve 3, an indoor unit heat exchanger 4, a four-way valve 5, an outdoor unit fan 6, and an indoor unit fan. It has a 7 and a pipe 8. The compressor 1, the outdoor unit heat exchanger 2, the expansion valve 3, the indoor unit heat exchanger 4, and the four-way valve 5 are communicated with each other via the pipe 8. This constitutes a refrigeration cycle in which the refrigerant circulates through the compressor 1, the outdoor unit heat exchanger 2, the expansion valve 3, the indoor unit heat exchanger 4, and the four-way valve 5.

The compressor 1, the outdoor unit heat exchanger 2, the expansion valve 3, the four-way valve 5, and the outdoor unit fan 6 are arranged in the outdoor unit 9. The indoor unit heat exchanger 4 and the indoor unit fan 7 are arranged in the indoor unit 10. A series of operations of the air conditioner 100 is controlled by a control device (not shown).

The compressor 1 is configured to compress and discharge the sucked refrigerant. The compressor 1 is configured so that the rotation speed can be variably controlled. Specifically, the compressor 1 may be an inverter compressor having a variable compression capacity. In this inverter compressor, the rotation speed is adjusted by changing the drive frequency based on the instruction from the control device. This changes the compression capacity. Further, the compressor 1 may be a constant speed compressor having a constant compression capacity.

The four-way valve 5 is connected to the compressor 1, the outdoor unit heat exchanger 2, and the indoor unit heat exchanger 4. The four-way valve 5 is configured to switch the refrigerant discharged from the compressor 1 to the outdoor unit heat exchanger 2 or the indoor unit heat exchanger 4 to flow.

The outdoor unit heat exchanger 2 is connected to the expansion valve 3 and the four-way valve 5. The outdoor unit heat exchanger 2 is for exchanging heat between the refrigerant and the outdoor air. The outdoor unit heat exchanger 2 is a condenser that condenses the refrigerant compressed by the compressor 1 during the cooling operation. The outdoor unit heat exchanger 2 is an evaporator that evaporates the refrigerant decompressed by the expansion valve 3 during the heating operation.

The expansion valve 3 is connected to the outdoor unit heat exchanger 2 and the indoor unit heat exchanger 4. The expansion valve 3 is a throttle device that reduces the pressure of the refrigerant condensed by the outdoor unit heat exchanger 2 during the cooling operation. The expansion valve 3 is a throttle device that reduces the pressure of the refrigerant condensed by the indoor unit heat exchanger 4 during the heating operation. The expansion valve 3 may be, for example, an electronic expansion valve, a capillary tube, or the like.

The indoor unit heat exchanger 4 is connected to the four-way valve 5 and the expansion valve 3. The indoor unit heat exchanger 4 is for exchanging heat between the refrigerant and the indoor air. The indoor unit heat exchanger 4 is an evaporator that evaporates the refrigerant decompressed by the expansion valve 3 during the cooling operation. The indoor unit heat exchanger 4 is a condenser that condenses the refrigerant compressed by the compressor 1 during the heating operation.

The outdoor unit fan 6 is for flowing air through the outdoor unit heat exchanger 2. The outdoor unit fan 6 has a blade for generating wind and a fan motor for rotating the blade. The indoor unit fan 7 is for flowing air through the indoor unit heat exchanger 4. It has a blade that generates wind and a fan motor that rotates the blade.

Each of the outdoor unit heat exchanger 2 and the indoor unit heat exchanger 4 has a plurality of fin FIs and transmissions for heat exchange between the air supplied from each of the outdoor unit fan 6 and the indoor unit fan 7 and the refrigerant. It has a heat tube PI (see FIGS. 3 and 3). The plurality of fins FI are attached to the outside of the straight portion of the heat transfer tube PI. The heat transfer tube PI is configured so that the refrigerant flows inside. The heat transfer tube PI penetrates a plurality of fins FI.

Next, the operation of the air conditioner 100 according to the present embodiment will be described with reference to FIGS. 1 and 2. The operation of the air conditioner 100 during the cooling operation will be described with reference to FIG. During the cooling operation, the air conditioner 100 has the refrigerant circuit shown in FIG. The high-temperature high-pressure gas refrigerant discharged from the compressor 1 passes through the four-way valve 5 and flows into the outdoor unit heat exchanger 2. The outdoor unit heat exchanger 2 functions as a condenser. The refrigerant in the outdoor unit heat exchanger 2 exchanges heat with the surrounding outdoor air (outside air) blown by the outdoor unit fan 6. At this time, the refrigerant is condensed by heat dissipation.

The condensed high-pressure liquid refrigerant flows into the expansion valve 3 and is depressurized by the expansion valve 3 to become a low-pressure two-phase refrigerant. The two-phase refrigerant decompressed by the expansion valve 3 flows into the indoor unit heat exchanger 4. The indoor unit heat exchanger 4 functions as an evaporator. The refrigerant in the indoor unit heat exchanger 4 exchanges heat with the indoor air blown by the indoor unit fan 7. The indoor air is cooled by the refrigerant, and the refrigerant becomes a low-pressure gas refrigerant. The refrigerant that has become a low-pressure gas in the indoor unit heat exchanger 4 passes through the four-way valve 5, flows into the compressor 1, is again pressurized, and is discharged.

During the heating operation, the air conditioner 100 has the refrigerant circuit shown in FIG. The high-temperature high-pressure gas refrigerant discharged from the compressor 1 passes through the four-way valve 5 and flows into the indoor unit heat exchanger 4. The indoor unit heat exchanger 4 functions as a condenser. The refrigerant in the indoor unit heat exchanger 4 exchanges heat with the surrounding indoor air (inside air) blown by the indoor unit fan 7. At this time, the heat radiation causes the refrigerant to condense and the air to be heated.

The condensed high-pressure liquid refrigerant flows into the expansion valve 3 and is depressurized by the expansion valve 3 to become a low-pressure two-phase refrigerant. The two-phase refrigerant decompressed by the expansion valve 3 flows into the outdoor unit heat exchanger 2. The outdoor unit heat exchanger 2 functions as an evaporator. The refrigerant in the outdoor unit heat exchanger 2 exchanges heat with the outdoor air blown by the outdoor unit fan 6. The refrigerant is a low pressure gas refrigerant. The refrigerant that has become a low-pressure gas in the outdoor unit heat exchanger 2 passes through the four-way valve 5, flows into the compressor 1, is pressurized again, and is discharged.

Next, the structure of the heat exchanger 20 according to the present embodiment will be described with reference to FIGS. 1 to 6. A case where the heat exchanger 20 according to the present embodiment is applied to the indoor unit heat exchanger 4 will be described as an example. Further, a case where the heat exchanger 20 according to the present embodiment is used for the indoor unit 10 of the commercial air conditioner will be described as an example. However, the heat exchanger 20 according to the present embodiment is not limited to this structure.

3 and 4 show a commercial 4-way ceiling cassette type indoor unit 10. As shown in FIGS. 3 and 4, the indoor unit 10 includes a heat exchanger 20 as an indoor unit heat exchanger 4, a blower 30 as an indoor unit fan 7, and a refrigerant inlet / outlet (gas side and liquid side). ) Consists of a gas pipe and a liquid pipe. The blower 30 is installed in the center of the indoor unit 10. The heat exchanger 20 is arranged so as to surround the blower 30. The blower 30 is configured to blow air to the heat exchanger 20. The blower 30 is configured to be able to blow air in all directions with respect to the heat exchanger 20. That is, the blower 30 is configured to be able to blow air in four directions as shown by the white arrows in FIG.

The heat exchanger 20 has a plurality of fin FIs laminated with each other and a heat transfer tube PI penetrating the plurality of fin FIs. The heat exchanger 20 condenses the refrigerant by exchanging heat between the refrigerant flowing inside the heat transfer tube PI and the air flowing outside the plurality of heat transfer tubes PI. The heat exchanger 20 has a first heat exchange unit 21, a second heat exchange unit 22, a third heat exchange unit 23, and a fourth heat exchange unit 24. Each of the first heat exchange unit 21, the second heat exchange unit 22, the third heat exchange unit 23, and the fourth heat exchange unit 24 has a plurality of fin FIs and heat transfer tube PIs. The plurality of fins FI may be integrated or separated in each of the first heat exchange unit 21, the second heat exchange unit 22, the third heat exchange unit 23, and the fourth heat exchange unit 24. ..

Each of the first heat exchange unit 21, the second heat exchange unit 22, the third heat exchange unit 23, and the fourth heat exchange unit 24 is arranged so as to surround the periphery of the blower 30. The first heat exchange unit 21 and the second heat exchange unit 22 are arranged on all sides of the blower 30. Further, each of the third heat exchange unit 23 and the fourth heat exchange unit 24 is arranged on four sides of the blower 30.

Each of the first heat exchange unit 21, the second heat exchange unit 22, the third heat exchange unit 23, and the fourth heat exchange unit 24 is a first heat exchange unit 21, a second heat exchange unit, from the windward direction to the leeward side. 22, the third heat exchange unit 23, and the fourth heat exchange unit 24 are arranged in this order. In other words, each of the first heat exchange unit 21, the second heat exchange unit 22, the third heat exchange unit 23, and the fourth heat exchange unit 24 is the first heat exchange unit 21, the second heat exchange unit 22, and the third. The heat exchange unit 23 and the fourth heat exchange unit 24 are arranged so as to be separated from the blower 30 in this order.

The second heat exchange unit 22 is arranged so as to face the first heat exchange unit 21. The second heat exchange unit 22 is arranged leeward of the first heat exchange unit 21 in the flow of air supplied from the blower 30. The second heat exchange unit 22 has a first end and a second end. The second heat exchange unit 22 extends continuously from the first end to the second end. The first heat exchange unit 21 has a first heat exchange region 21A and a second heat exchange region 21B arranged along the direction in which the second heat exchange unit 22 extends. The second heat exchange region 21B is separated from the first heat exchange region 21A along the direction in which the second heat exchange portion 22 extends.

The first heat exchange region 21A and the second heat exchange region 21B are branched from the second heat exchange unit 22. That is, the first heat exchange region 21A and the second heat exchange region 21B are connected in parallel to the second heat exchange unit 22. In the present embodiment, the first heat exchange region 21A and the second heat exchange region 21B are arranged so as to sandwich the blower 30. Each of the first heat exchange region 21A and the second heat exchange region 21B is configured in an L shape.

The third heat exchange unit 23 is arranged so as to face the second heat exchange unit 22. The third heat exchange unit 23 is arranged leeward of the second heat exchange unit 22 in the flow of air supplied from the blower 30. The fourth heat exchange unit 24 is arranged so as to face the third heat exchange unit 23. The fourth heat exchange unit 24 is arranged leeward of the third heat exchange unit 23 in the flow of air supplied from the blower 30.

With reference to FIGS. 4 and 5, the number of passes of the heat transfer tube PI in the first heat exchange unit 21 is smaller than the number of passes of the heat transfer tube PI in the second heat exchange unit 22. This number of passes is the number of refrigerant channels. That is, the number of paths is the number of a plurality of refrigerant channels through which the refrigerant flows in parallel with each other. In the present embodiment, the number of passes of the first heat exchange unit 21 is four, and the number of passes of the second heat exchange unit 22 is eight. That is, the eight heat transfer paths of the second heat exchange unit 22 join the four heat transfer paths of the first heat exchange unit 21.

Subsequently, the path arrangement of the heat exchanger 20 according to the present embodiment will be described in more detail by taking the heat transfer path of the upper four stages as an example. The heat transfer paths of the upper two stages of the upper four stages that have passed through the B side of the second heat exchange unit 22 in the second row merge with each other, and the B side (second heat) of the first heat exchange unit 21 in the first row. It flows into the heat transfer path of the exchange region 21B). When the refrigerant flows into the upper part on the B side of the first heat exchange section 21 in the first row, the first heat exchange section 21 is divided into the first heat exchange region 21A and the second heat exchange region 21B, so that the refrigerant Does not move to the A side (first heat exchange region 21A) of the first heat exchange unit 21, but is folded back at the divided C side. At this time, since the heat transfer tube PI is coupled in the step direction of the first heat exchange section 21 in the first row on the C side, the refrigerant is turned back from the C side to the B side and the first heat exchange section in the first row. It flows out from the next lower stage that has flowed into the B side of 21. By repeating this movement, the refrigerant flows out from the lowermost stage of the upper four stages on the B side of the first heat exchange unit 21 and joins the liquid pipe.

The heat transfer paths of the lower two stages of the upper four stages that have passed through the B side of the second heat exchange unit 22 in the second row merge with each other, and the first heat on the A side of the first heat exchange unit 21 in the first row It flows into the exchange area 21A. For example, when the refrigerant flows into the lowermost stage of the upper four stages on the A side of the first heat exchange unit 21 in the first row, the first heat exchange unit 21 enters the first heat exchange region 21A and the second heat exchange region 21B. Since it is divided into and, the refrigerant does not move to the B side and is folded back at the divided C side. At this time, since the heat transfer tube PI is coupled in the step direction of the first heat exchange section 21 in the first row on the C side, the refrigerant is turned back from the C side to the A side and the first heat exchange section in the first row. It flows out from the next higher stage that has flowed into the A side of 21. By repeating this movement, the refrigerant flows out from the lowermost stage of the upper four stages on the A side of the first heat exchange unit 21 and joins the liquid pipe.

With reference to FIG. 6, in the present embodiment, the first heat exchange portion 21 in the first row on the windward side is divided in the product width direction. That is, the first heat exchange unit 21 is divided into two, a first heat exchange region 21A on the A side and a second heat exchange region 21B on the B side. As a result, it is possible to suppress the temperature difference generated between the heat transfer tube PIs in the adjacent step directions in the first heat exchange unit 21.

Next, the action and effect of the present embodiment will be described in comparison with the comparative example.
The structure of the heat exchanger of the comparative example will be described with reference to FIGS. 7 to 10. In the heat exchanger 20 of the comparative example, the first heat exchange unit 21 is mainly configured integrally, and the heat exchanger 20 of the present embodiment is not separated into the first heat exchange region and the second heat exchange region. It is different from the exchanger 20.

The flow of the refrigerant in the heating operation will be described with reference to FIGS. 7 and 8. In the heating operation, the refrigerant flows into the fourth heat exchange section 24 from the gas pipe provided on the first end side (A side) of the heat exchanger 20. The refrigerant flows from the first end side (A side) to the second end side (B side) of the heat exchanger, moves to the windward row by the U-shaped pipe provided on the B side, and again on the A side. Return to. After that, the refrigerant moves to the windward row by the U-shaped pipe installed on the A side, and moves to the B side. The refrigerant repeatedly moves from the A side to the B side, and moves to the first heat exchange unit 21 in the first row installed on the windward side. During this time, the refrigerant changes from a gas phase to a liquid phase by exchanging heat with air. Most of the refrigerant is liquefied on the A side of the heat transfer tube in the first heat exchange section 21 in the first row. The refrigerants in each stage merge and move to the expansion valve 3. In the case of cooling operation, the flow of the refrigerant is reversed, the refrigerant flows into the heat exchanger 20 from the liquid side, and flows out from the heat exchanger 20 to the gas side.

With reference to FIGS. 8 and 9, when the refrigerant undergoes a phase change and changes from a gas phase to a liquid phase, the refrigerant density increases and the flow velocity of the refrigerant decreases. Since the heat transfer coefficient of the refrigerant correlates with the flow velocity, the heat transfer coefficient on the refrigerant side decreases when the flow velocity is low. As a result, when the number of paths in the flow path does not change between the first heat exchange unit 21 and the second heat exchange unit 22, as in the comparative example, the performance of the heat exchanger 20 deteriorates.

With reference to FIG. 10, in the comparative example, the first heat exchange portion 21 in the first row on the windward side is integrally configured, and is not divided in the product width direction. Therefore, it is not possible to suppress the temperature difference generated in each heat transfer path in the adjacent step direction in the first heat exchange unit 21. Therefore, the transfer of heat increases. This reduces the performance of the heat exchanger 20.

On the other hand, according to the heat exchanger 20 according to the present embodiment, in the first heat exchange unit 21, the second heat exchange region 21B has the first heat along the direction in which the second heat exchange unit 22 extends. It is separated from the exchange region 21A. Therefore, as shown in FIG. 6, it is possible to suppress heat transfer generated between the refrigerants flowing through the heat transfer tube PI at the inlet and outlet of the first heat exchange section 21, which is the liquid single-phase section. Therefore, the performance of the heat exchanger 20 can be improved.

According to the heat exchanger 20 according to the present embodiment, the number of passes of the heat transfer tube PI in the first heat exchange unit 21 is smaller than the number of passes of the heat transfer tube PI in the second heat exchange unit 22. Therefore, the plurality of heat transfer paths of the second heat exchange unit 22 join the heat transfer paths of the first heat exchange unit 21. Since the flow velocity of the liquid refrigerant increases due to the merging of a plurality of heat transfer paths, the heat transfer coefficient on the refrigerant side increases. Thereby, the performance of the heat exchanger 20 can be improved.

According to the heat exchanger 20 of the present embodiment, the temperature distribution of the heat transfer tube PI generated in the product width direction can be suppressed by dividing the first heat exchange unit 21. Therefore, it is possible to suppress heat transfer between heat transfer paths stacked in the step direction. Further, the heat transfer coefficient in the heat transfer tube PI can be increased by increasing the flow velocity of the refrigerant by merging the liquid phase refrigerants. Thereby, the performance of the heat exchanger 20 can be further effectively improved.

According to the air conditioner 100 according to the present embodiment, since the heat exchanger 20 and the blower 30 are provided, the air conditioner 100 capable of improving the performance of the heat exchanger 20 is provided. be able to.

According to the air conditioner 100 according to the present embodiment, the first heat exchange unit 21 and the second heat exchange unit 22 are arranged on four sides of the blower 30. Therefore, the air conditioner 100 can be applied to the 4-way ceiling cassette type.

Embodiment 2.
The heat exchanger 20 according to the second embodiment of the present invention will be described with reference to FIG. Unless otherwise specified, the following embodiments 2 to 4 have the same configuration and effect as the heat exchanger according to the first embodiment. Therefore, the same components as those of the heat exchanger according to the first embodiment are designated by the same reference numerals, and the description thereof will not be repeated.

The second embodiment is different from the first embodiment in the flow path of the first heat exchange unit 21 in the first row. In the first embodiment, as shown in FIG. 6, two flow paths flow in from both the first heat exchange region 21A and the second heat exchange region 21B. On the other hand, in the second embodiment, as shown in FIG. 11, two flow paths flow in from the second heat exchange region 21B.

In the heat exchanger 20 according to the present embodiment, in the first heat exchange section 21, the heat transfer tube PI has a first heat transfer tube section PI1 and a second heat transfer tube section PI2 adjacent to the first heat transfer tube section PI1. ing. Each of the first heat transfer tube portion PI1 and the second heat transfer tube portion PI2 passes through the first heat exchange section 21 a plurality of times so as to be folded back along the extending direction of the second heat exchange section 22. At the inlet and outlet of the first heat exchange section 21, the number of times of passing through either the first heat exchange region 21A or the second heat exchange region 21B of the first heat transfer tube section PI1 is the first of the second heat transfer tube section PI2. It is the same as the number of times of passing through either the heat exchange region 21A or the second heat exchange region 21B.

In the present embodiment, one flow path FL1 flows into the upper heat transfer path on the B side, and the other flow path FL2 flows into the second heat transfer path from the upper part on the B side. In the flow path FL1, the refrigerant that has flowed into the upper heat transfer path on the B side flows out from the C side, flows directly into the upper heat transfer path on the A side, and then is the second and third transfer from the upper part on the A side. It passes through the heat path and joins the liquid side. In the flow path FL2, the refrigerant flowing into the second heat transfer path from the upper part on the B side flows into the third heat transfer path from the upper part on the B side, passes through the C side, and is the fourth from the upper part on the A side. It flows into the heat transfer path and joins the liquid side.

As shown by the broken line in FIG. 11, in the heat exchanger 20 according to the present embodiment, the location where the heat transfer paths of the flow paths FL1 and the flow path FL2 are adjacent to each other is located in the first heat exchange section 21 in the first row. It is the first and fourth place counting from the place where it flowed in. Each time the refrigerant passes through the heat transfer tube PI, heat is exchanged with air, the refrigerant is cooled, and the temperature becomes low, so that the temperature of the heat transfer tube PI gradually decreases from the first to the fourth portion. Therefore, the heat transfer between the heat transfer tubes PI in the flow path FL1 and the flow path FL2 becomes small.

According to the present embodiment, the number of times of passing through either the first heat exchange region 21A or the second heat exchange region 21B of the first heat transfer tube unit PI1 at the inlet and outlet of the first heat exchange unit 21 is the second. 2 The number of times the heat transfer tube portion PI2 passes through either the first heat exchange region 21A or the second heat exchange region 21B is the same. Therefore, it is possible to suppress heat transfer between the first heat transfer tube portion PI1 and the second heat transfer tube portion PI2.

Embodiment 3.
The heat exchanger 20 according to the third embodiment of the present invention will be described with reference to FIGS. 12 to 14. 12 and 13 show the heat exchanger 20 according to the present embodiment. FIG. 14 shows a heat exchanger 20 according to a modified example of the present embodiment. As shown in FIGS. 12 to 14, in the heat exchanger 20 according to the present embodiment, the first heat exchange unit 21 is divided into four in the product width direction. Further, as shown by the broken line in FIGS. 13 and 14, the first heat transfer tube PI, the fourth heat transfer tube PI, the fifth heat transfer tube PI, and the eighth heat transfer tube counting from the upstream of the refrigerant. The heat tube PIs are arranged so as to be adjacent to each other.

In the heat exchanger 20 according to the present embodiment and the modification, the first heat exchange unit 21 has the third heat exchange region 21C and the fourth heat arranged along the direction in which the second heat exchange unit 22 extends. It has an exchange area 21D. The fourth heat exchange region 21D is separated from the third heat exchange region 21C along the direction in which the second heat exchange unit 22 extends. Each of the third heat exchange region 21C and the fourth heat exchange region 21D is separated from each of the first heat exchange region 21A and the second heat exchange region 21B along the direction in which the second heat exchange portion 22 extends. ing.

At a location where the first heat transfer tube portion PI1 and the second heat transfer tube portion PI2 are adjacent to each other in the middle of the first heat exchange section 21, the first heat exchange region 21A and the second heat exchange region 21B of the first heat transfer tube portion PI1. The number of times of passing through any of the third heat exchange region 21C and the fourth heat exchange region 21D is the first heat exchange region 21A, the second heat exchange region 21B, the third heat exchange region 21C and the second heat transfer tube portion PI2. It is the same as the number of times of passing through any of the fourth heat exchange regions 21D.

In the heat exchanger 20 according to the present embodiment and the modified example, since the first heat exchange unit 21 is divided into four in the product width direction, the first heat exchange unit 21 is divided into two in the product width direction. It is possible to reduce the heat transfer between the heat transfer tube PIs as compared with the case where the heat transfer tube PI is used. Further, since the first heat transfer tube PI, the fourth heat transfer tube PI, the fifth heat transfer tube PI, and the eighth heat transfer tube PI are arranged adjacent to each other counting from the upstream of the refrigerant. It is possible to further suppress heat transfer between the first heat transfer tube portion PI1 and the second heat transfer tube portion PI2. Therefore, the performance of the heat exchanger 20 can be further improved.

Embodiment 4.
The indoor unit 10 of the air conditioner 100 according to the fourth embodiment of the present invention will be described with reference to FIGS. 15 and 16. The indoor unit 10 of the air conditioner 100 according to the present embodiment is a four-way ceiling cassette type indoor unit 10. 15 and 16 show a state in which the indoor unit 10 is installed on the ceiling 15. The indoor unit 10 has a case 11, a panel 12, a heat exchanger 20, and a blower 30.

A heat exchanger 20 and a blower 30 are arranged in the case 11. Most of the case 11 is buried behind the ceiling 15 (opposite the room). The panel 12 faces the interior of the room. The panel 12 has a suction port 12a and four outlets 12b. Each outlet 12b is arranged on all four sides around the suction port 12a. The blower 30 is configured to pass the air sucked into the case 11 from the suction port 12a through the heat exchanger 20 and blow it out from the air outlet 12b. The four outlets 12b are arranged so as to be offset by 90 degrees around the suction port 12a. Therefore, the indoor unit 10 of the air conditioner 100 according to the present embodiment can be blown out in four directions by blowing out from each of the four outlets 12b.

It should be considered that the embodiments disclosed this time are exemplary in all respects and not restrictive. The scope of the present invention is shown by the scope of claims rather than the above description, and is intended to include all modifications within the meaning and scope equivalent to the scope of claims.

1 Compressor, 2 Outdoor unit heat exchanger, 3 Expansion valve, 4 Indoor unit heat exchanger, 5 4-way valve, 6 Outdoor unit fan, 7 Indoor unit fan, 8 Piping, 9 Outdoor unit, 10 Indoor unit, 20 Heat exchanger, 21 1st heat exchange section, 21A 1st heat exchange area, 21B 2nd heat exchange area, 21C 3rd heat exchange area, 21D 4th heat exchange area, 22 2nd heat exchange section, 23 3rd heat Exchange part, 24 4th heat exchange part, 30 blower, 100 air conditioner, FI fin, PI heat transfer tube, PI1 1st heat transfer tube, PI2 2nd heat transfer tube.

Claims (6)

The refrigerant has a plurality of fins laminated to each other and a heat transfer tube penetrating the plurality of fins, and the refrigerant flows by exchanging heat between the refrigerant flowing inside the heat transfer tube and the air flowing outside the heat transfer tube. A heat exchanger that condenses
The first heat exchange unit and
It is provided with a second heat exchange unit facing the first heat exchange unit and arranged leeward of the first heat exchange unit in the air flow.
The second heat exchange section has a first end and a second end, and extends continuously from the first end to the second end.
The first heat exchange unit has a first heat exchange region and a second heat exchange region arranged along the direction in which the second heat exchange unit extends.
The second heat exchange region is separated from the first heat exchange region along the direction in which the second heat exchange portion extends .
A heat exchanger in which the heat transfer tubes of the first heat exchange region and the second heat exchange region are adjacent to each other in the step direction and are folded back along the direction in which the second heat exchange portion extends . The heat exchanger according to claim 1, wherein the number of passes of the heat transfer tube in the first heat exchange section is smaller than the number of passes of the heat transfer tube in the second heat exchange section. In the first heat exchange section, the heat transfer tube has a first heat transfer tube section and a second heat transfer tube section adjacent to the first heat transfer tube section.
Each of the first heat transfer tube portion and the second heat transfer tube portion has passed through the first heat exchange section a plurality of times so as to be folded back along the direction in which the second heat exchange section extends.
At the inlet and outlet of the first heat exchange section, the number of times of passing through either the first heat exchange region or the second heat exchange region of the first heat transfer tube section is the number of times the second heat transfer tube section is passed. The heat exchanger according to claim 1 or 2, which is the same as the number of times of passing through either one heat exchange region and the second heat exchange region. The first heat exchange unit has a third heat exchange region and a fourth heat exchange region arranged along the direction in which the second heat exchange unit extends.
The fourth heat exchange region is separated from the third heat exchange region along the direction in which the second heat exchange portion extends.
Each of the third heat exchange region and the fourth heat exchange region is separated from each of the first heat exchange region and the second heat exchange region along the direction in which the second heat exchange portion extends. And
At a location where the first heat transfer tube portion and the second heat transfer tube portion are adjacent to each other in the middle of the first heat exchange portion, the first heat exchange region and the second heat exchange region of the first heat transfer tube portion. The number of times of passing through any of the third heat exchange region and the fourth heat exchange region is the first heat exchange region, the second heat exchange region, the third heat exchange region, and the second heat transfer tube portion. The heat exchanger according to claim 3, which is the same as the number of times of passing through any of the fourth heat exchange regions. The heat exchanger according to any one of claims 1 to 4.
An air conditioner including a blower that blows air to the heat exchanger. The air conditioner according to claim 5, wherein the first heat exchange unit and the second heat exchange unit are arranged on four sides of the blower.

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