JP2019158286A - Heat exchanger and air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger capable of suppressing heat transfer generated between each heat transfer tube and an air conditioner provided with the heat exchanger. SOLUTION: A heat exchanger 20 faces a first heat exchange unit 21 and a first heat exchange unit 21, and is arranged in a second heat exchange unit leeward of the first heat exchange unit 21 in the air flow. It has 22 and. 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. [Selection diagram] FIG. 4

Description

  The present invention relates to a heat exchanger and an air conditioner.

  Conventionally, in an air conditioner or the like, a heat exchanger including a plurality of fins and heat transfer tubes arranged in a flow of air supplied by a blower (fan) is used. The plurality of fins are stacked on each other. The heat transfer tube passes through the plurality of fins. An air conditioner equipped 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 that can be blown out in four directions while being embedded in the ceiling.

JP 2011-122819 A

  In the air conditioner described in the above publication, the product width of the heat exchanger is long. The 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 be generated in the heat transfer tube between the inlet and the outlet of the liquid single phase portion where the refrigerant becomes a liquid single phase in the heat exchanger. If a temperature difference occurs between the inlet and outlet of the liquid single-phase part, the amount of heat exchange between the refrigerants flowing through the heat transfer pipe between the inlet and outlet of the liquid single-phase part increases. Therefore, there exists a problem that the performance of a heat exchanger cannot fully be exhibited.

  The present invention has been made in view of the above problems, and its purpose is to provide a heat exchanger capable of suppressing heat exchange between refrigerants flowing through heat transfer tubes at the inlet and outlet of the liquid single-phase part, and It is to provide an air conditioner equipped with it.

  The heat exchanger according to the present invention includes a plurality of fins stacked on 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. This causes the refrigerant to condense. The heat exchanger includes a first heat exchange unit and a second heat exchange unit that faces the first heat exchange unit and is disposed further downwind than the first heat exchange unit in the air flow. The second heat exchange part has a first end and a second end, and extends continuously from the first end to the second end. The 1st heat exchange part has the 1st heat exchange field and the 2nd heat exchange field arranged along the direction where the 2nd heat exchange part extends. The second heat exchange region is separated from the first heat exchange region along the direction in which the second heat exchange unit extends.

  According to the heat exchanger of the present invention, in the first heat exchange unit, the second heat exchange region is separated from the first heat exchange region along the direction in which the second heat exchange unit extends. For this reason, the heat transfer which generate | occur | produces between the refrigerant | coolants which flow through a heat exchanger tube by the inlet_port | entrance and exit of a liquid single phase part can be suppressed. Therefore, the performance of the heat exchanger can be improved.

It is a figure which shows roughly the refrigerating cycle in the air_conditioning | 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 roughly the structure of the heat exchanger which concerns on Embodiment 1 of this invention. It is a perspective view which shows roughly the structure of the heat exchanger which concerns on Embodiment 1 of this invention. It is a figure which shows schematically the path | pass of the heat exchanger which concerns on Embodiment 1 of this invention. It is an expanded view which shows schematically the 1st heat exchange part of the heat exchanger which concerns on Embodiment 1 of this invention. It is a top view which shows roughly the structure of the heat exchanger which concerns on a comparative example. It is a perspective view which shows roughly the structure of the heat exchanger which concerns on a comparative example. It is a figure which shows roughly the path | pass of the heat exchanger which concerns on a comparative example. It is an expanded view which shows the 1st heat exchange part of the heat exchanger which concerns on a comparative example roughly. It is an expanded view which shows schematically the 1st heat exchange part of the heat exchanger which concerns on Embodiment 1 of this invention. It is a top view which shows roughly the structure of the heat exchanger which concerns on Embodiment 3 of this invention. It is an expanded view which shows roughly the 1st heat exchange part of the heat exchanger which concerns on Embodiment 3 of this invention. It is an expanded view which shows schematically 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 which shows roughly the state by which the indoor unit of the air conditioner which concerns on Embodiment 4 of this invention was installed in the ceiling. It is sectional drawing which follows the XVI-XVI line | wire of FIG.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Embodiment 1 FIG.
With reference to FIG. 1, the structure of the air conditioner 100 which concerns on Embodiment 1 of this invention is demonstrated. FIG. 1 is a schematic diagram showing a configuration of an air conditioner 100 according to the present embodiment. 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, an 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. 7 and piping 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 through a pipe 8. Thus, a refrigeration cycle is configured 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 disposed 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 number of rotations can be variably controlled. Specifically, the compressor 1 may be an inverter compressor having a variable compression capacity. In this inverter compressor, the rotational frequency is adjusted by changing the drive frequency based on an instruction from the control device. Thereby, the compression capacity changes. 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 performing heat exchange between the refrigerant and 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 serves as a throttle device that decompresses the refrigerant condensed by the outdoor unit heat exchanger 2 during the cooling operation. The expansion valve 3 serves as a throttle device that decompresses the refrigerant condensed by the indoor unit heat exchanger 4 during heating operation. The expansion valve 3 may be, for example, an electronic expansion valve or a capillary tube.

  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 serves as 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 heating operation.

  The outdoor unit fan 6 is for flowing air to the outdoor unit heat exchanger 2. The outdoor unit fan 6 includes blades that generate wind and a fan motor that rotates the blades. The indoor unit fan 7 is for flowing air through the indoor unit heat exchanger 4. It has the blade | wing which generate | occur | produces a wind, and the fan motor which rotates a blade | wing.

  Each of the outdoor unit heat exchanger 2 and the indoor unit heat exchanger 4 includes a plurality of fins FI and a transmission for exchanging heat 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 pipe PI (see FIGS. 3 and 3). The plurality of fins FI are attached to the outside of the straight portion of the heat transfer pipe PI. The heat transfer pipe PI is configured such that the refrigerant flows inside. The heat transfer pipe PI passes through the plurality of fins FI.

  Next, with reference to FIG. 1 and FIG. 2, operation | movement of the air conditioner 100 which concerns on this Embodiment is demonstrated. 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 and 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 decompressed 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 low-pressure gas in the indoor unit heat exchanger 4 passes through the four-way valve 5, flows into the compressor 1, and is pressurized and discharged again.

  During the heating operation, the air conditioner 100 has the refrigerant circuit shown in FIG. The high-temperature and 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 refrigerant is condensed by heat radiation, and the air is heated.

  The condensed high-pressure liquid refrigerant flows into the expansion valve 3 and is decompressed 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 becomes a low-pressure gas refrigerant. The refrigerant that has become low-pressure gas in the outdoor unit heat exchanger 2 passes through the four-way valve 5, flows into the compressor 1, and is pressurized and discharged again.

  Next, with reference to FIGS. 1-6, the structure of the heat exchanger 20 which concerns on this Embodiment is demonstrated. The 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. Moreover, the case where the heat exchanger 20 which concerns on this Embodiment is used for the indoor unit 10 of a commercial air conditioner is demonstrated to an example. However, the heat exchanger 20 according to the present embodiment is not limited to this structure.

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

  The heat exchanger 20 includes a plurality of fins FI stacked on each other and a heat transfer pipe PI passing through the plurality of fins FI. The heat exchanger 20 condenses the refrigerant by exchanging heat between the refrigerant flowing inside the heat transfer pipe PI and the air flowing outside the plurality of heat transfer pipes PI. The heat exchanger 20 includes 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 includes a plurality of fins FI and a heat transfer pipe PI. The plurality of fins FI may be integrated 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, or may be separated. .

  Each of the 1st heat exchange part 21, the 2nd heat exchange part 22, the 3rd heat exchange part 23, and the 4th heat exchange part 24 is arrange | positioned so that the circumference | surroundings of the air blower 30 may be surrounded. The first heat exchange unit 21 and the second heat exchange unit 22 are arranged on four sides of the blower 30. Moreover, each of the 3rd heat exchange part 23 and the 4th heat exchange part 24 is arrange | positioned at the four directions of the air blower 30. FIG.

  Each of the 1st heat exchange part 21, the 2nd heat exchange part 22, the 3rd heat exchange part 23, and the 4th heat exchange part 24 is the 1st heat exchange part 21 and the 2nd heat exchange part from the windward toward the leeward. 22, the 3rd heat exchange part 23, and the 4th heat exchange part 24 are arrange | positioned in 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 includes the first heat exchange unit 21, the second heat exchange unit 22, and the third heat exchange unit 22, respectively. It arrange | positions so that it may leave | separate from the air blower 30 in order of the heat exchange part 23 and the 4th heat exchange part 24. FIG.

  The second heat exchange unit 22 is disposed so as to face the first heat exchange unit 21. The second heat exchanging unit 22 is arranged more leeward than the first heat exchanging 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 part 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 unit 22 extends.

  The first heat exchange region 21 </ b> A and the second heat exchange region 21 </ b> B are branched from the second heat exchange unit 22. That is, the first heat exchange region 21 </ b> A and the second heat exchange region 21 </ b> B 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 with the blower 30 interposed therebetween. 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 disposed so as to face the second heat exchange unit 22. The third heat exchanging unit 23 is arranged more leeward than the second heat exchanging unit 22 in the flow of air supplied from the blower 30. The fourth heat exchange unit 24 is disposed 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.

  4 and 5, the number of passes of the heat transfer pipe PI in the first heat exchange unit 21 is smaller than the number of passes of the heat transfer pipe PI in the second heat exchange unit 22. This number of passes is the number of refrigerant flow paths. In other words, the number of passes is the number of a plurality of refrigerant flow paths through which refrigerant flows. 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 merge with the four heat transfer paths of the first heat exchange unit 21.

  Next, the path arrangement of the heat exchanger 20 according to the present embodiment will be described in more detail by taking the upper four-stage heat transfer path as an example. Of the upper four stages passing through the B side of the second heat exchange section 22 in the second row, the upper two stages of the heat transfer paths merge together to form the B side (second heat) of the first heat exchange section 21 in the first row. It flows into the heat transfer path of the exchange area 21B). When the refrigerant flows into the upper part on the B side of the first heat exchange unit 21 in the first row, the first heat exchange unit 21 is divided into the first heat exchange region 21A and the second heat exchange region 21B. Does not move to the A side (first heat exchange region 21A) of the first heat exchanging part 21, but is folded back on the divided C side. At this time, since the heat transfer pipe 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 folded back from the C side to the B side, and the first heat exchange section in the first row. It flows out from the lower stage which flowed into the B side of 21. By repeating this movement, the refrigerant flows out from the lowermost of the upper four stages on the B side of the first heat exchange unit 21 and joins the liquid pipe.

  Of the upper four stages passing through the B side of the second heat exchange section 22 in the second row, the lower two stages of heat transfer paths merge together, and the first heat on the A side of the first heat exchange section 21 in the first row. It flows into the exchange area 21A. For example, when the refrigerant flows into the lowermost stage among the upper four stages on the A side of the first heat exchange section 21 in the first row, the first heat exchange section 21 moves to the first heat exchange area 21A and the second heat exchange area 21B. Therefore, the refrigerant does not move to the B side and is folded back on the divided C side. At this time, since the heat transfer pipe PI is coupled in the step direction of the first heat exchange unit 21 in the first row on the C side, the refrigerant is folded back from the C side to the A side, and the first heat exchange unit in the first row. It flows out from the upper stage which flowed in 21 A side. By repeating this movement, the refrigerant flows out from the lowest of the upper four stages on the A side of the first heat exchange unit 21 and joins the liquid pipe.

  Referring to FIG. 6, in the present embodiment, first heat exchange section 21 in the first row on the most windward side is divided in the product width direction. That is, the first heat exchanging portion 21 is divided into two parts, that is, a first heat exchange area 21A on the A side and a second heat exchange area 21B on the B side. Thereby, the temperature difference which arises for every heat exchanger tube PI of the step direction adjacent in the 1st heat exchange part 21 can be suppressed.

Next, the effects of the present embodiment will be described in comparison with a comparative example.
With reference to FIGS. 7-10, the structure of the heat exchanger of a comparative example is demonstrated. The heat exchanger 20 of the comparative example mainly includes the first heat exchanging portion 21 and is not separated into the first heat exchanging region and the second heat exchanging region. It is different from the exchanger 20.

  With reference to FIG. 7 and FIG. 8, the flow of the refrigerant in the heating operation will be described. In the heating operation, the refrigerant flows into the fourth heat exchange unit 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 side by the U-shaped pipe provided on the B side, and again on the A side. Return to. Thereafter, the refrigerant moves to the windward side by the U-shaped pipe installed on the A side and moves to the B side. The refrigerant repeats the movement from the A side to the B side, and moves to the first heat exchange unit 21 in the first row installed on the furthest side. During this time, the refrigerant changes from the gas phase to the 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 refrigerant in each stage joins and moves to the expansion valve 3. In the cooling operation, the flow of the refrigerant is reversed, and the refrigerant flows into the heat exchanger 20 from the liquid side and flows out from the heat exchanger 20 to the gas side.

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

  Referring 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. For this reason, in the 1st heat exchange part 21, the temperature difference which arises for every heat transfer path of the adjacent step direction cannot be controlled. Therefore, the transfer of heat increases. Thereby, the performance of the heat exchanger 20 falls.

  On the other hand, according to the heat exchanger 20 according to the present embodiment, in the first heat exchanging portion 21, the second heat exchanging region 21B is the first heat along the direction in which the second heat exchanging portion 22 extends. It is separated from the exchange area 21A. For this reason, as shown in FIG. 6, it is possible to suppress heat exchange between refrigerants flowing through the heat transfer pipe PI at the inlet and the outlet of the first heat exchange unit 21 that is a liquid single-phase unit. 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 pipe PI in the first heat exchange unit 21 is smaller than the number of passes of the heat transfer pipe PI in the second heat exchange unit 22. For this reason, the plurality of heat transfer paths of the second heat exchange unit 22 merge with the heat transfer path of the first heat exchange unit 21. Since the flow rate of the liquid refrigerant increases due to the joining of the 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 pipe PI that has occurred in the product width direction can be suppressed by dividing the first heat exchange unit 21. For this reason, heat transfer between the heat transfer paths stacked in the step direction can be suppressed. Furthermore, the heat transfer coefficient in the heat transfer pipe PI can be increased by increasing the flow rate of the refrigerant by merging the liquid phase refrigerant. Thereby, the performance of the heat exchanger 20 can be improved further effectively.

  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 that can improve 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. For this reason, the air conditioner 100 can be applied to a four-way ceiling cassette type.

Embodiment 2. FIG.
With reference to FIG. 11, the heat exchanger 20 which concerns on Embodiment 2 of this invention is demonstrated. The following second to fourth embodiments have the same configuration and effects as those of the heat exchanger according to the first embodiment unless otherwise specified. Therefore, the same components as those in the heat exchanger according to the first embodiment are denoted by the same reference numerals, and description thereof is not 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 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 from the second heat exchange region 21B.

  In the heat exchanger 20 according to the present embodiment, the heat transfer pipe PI in the first heat exchange unit 21 has a first heat transfer pipe part PI1 and a second heat transfer pipe part PI2 adjacent to the first heat transfer pipe part PI1. ing. Each of the first heat transfer pipe part PI1 and the second heat transfer pipe part PI2 passes through the first heat exchange part 21 a plurality of times so as to be folded along the direction in which the second heat exchange part 22 extends. 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 pipe part PI1 at the inlet and outlet of the first heat exchange part 21 is the first of the second heat transfer pipe part PI2. It is the same as the number of times of passing through either the heat exchange area 21A or the second heat exchange area 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 side on the B side. In the flow path FL1, the refrigerant flowing into the upper heat transfer path on the B side flows out from the C side, flows into the upper heat transfer path on the A side as it is, and then the second and third heat 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 and fourth heat transfer paths from the upper part on the B side, passes through the C side and is fourth from the upper part on the A side. Flows into the heat transfer path and joins to the liquid side.

  As indicated by a broken line in FIG. 11, in the heat exchanger 20 according to the present embodiment, the portion where the heat transfer paths of the flow path FL1 and the flow path FL2 are adjacent to each other is in the first heat exchange section 21 in the first row. These are the first and fourth locations counted from the inflow location. Whenever the refrigerant passes through the heat transfer pipe PI, heat exchange with air is performed, the refrigerant is cooled and the temperature is lowered, so that the temperature of the heat transfer pipe PI gradually decreases from the first to the fourth place. Therefore, heat transfer between the heat transfer pipes PI in the flow path FL1 and the flow path FL2 is reduced.

  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 pipe part PI1 at the inlet and the outlet of the first heat exchange unit 21 is It is the same as the number of times of passing through either the first heat exchange region 21A or the second heat exchange region 21B of the second heat transfer pipe part PI2. Therefore, heat transfer between the first heat transfer tube portion PI1 and the second heat transfer tube portion PI2 can be suppressed.

Embodiment 3 FIG.
With reference to FIGS. 12-14, the heat exchanger 20 which concerns on Embodiment 3 of this invention is demonstrated. 12 and 13 show a heat exchanger 20 according to the present embodiment. FIG. 14 shows a heat exchanger 20 according to a modification 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. 13 and 14, the first heat transfer pipe PI, the fourth heat transfer pipe PI, the fifth heat transfer pipe PI, and the eighth heat transfer pipe are counted from the upstream side of the refrigerant. The heat pipes PI are arranged adjacent to each other.

  In the heat exchanger 20 according to the present embodiment and the modification, the first heat exchange unit 21 includes 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 unit 22 extends. ing.

  At a location where the first heat transfer pipe part PI1 and the second heat transfer pipe part PI2 are adjacent to each other in the middle of the first heat exchange part 21, the first heat exchange area 21A, the second heat exchange area 21B of the first heat transfer pipe part PI1, The number of times of passing through either the third heat exchange region 21C or 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 pipe part PI2. This is the same as the number of passes through any one of the fourth heat exchange regions 21D.

  In the heat exchanger 20 according to the present embodiment and the modification, the first heat exchanging portion 21 is divided into four in the product width direction, so the first heat exchanging portion 21 is separated into two in the product width direction. Compared with the case where it is done, heat transfer between the heat transfer pipes PI can be reduced. In addition, since the first heat transfer pipe PI, the fourth heat transfer pipe PI, the fifth heat transfer pipe PI, and the eighth heat transfer pipe PI are arranged adjacent to each other from the upstream side of the refrigerant, Heat transfer between the first heat transfer pipe part PI1 and the second heat transfer pipe part PI2 can be further suppressed. Therefore, the performance of the heat exchanger 20 can be further improved.

Embodiment 4 FIG.
With reference to FIG. 15 and FIG. 16, the indoor unit 10 of the air conditioner 100 which concerns on Embodiment 4 of this invention is demonstrated. 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 includes a case 11, a panel 12, a heat exchanger 20, and a blower 30.

  A heat exchanger 20 and a blower 30 are disposed in the case 11. Most of the case 11 is embedded in the back side of the ceiling 15 (the side opposite to the room). The panel 12 faces the room interior. The panel 12 has an inlet 12a and four outlets 12b. Each outlet 12b is arrange | positioned at the four directions around the suction inlet 12a. The blower 30 is configured to blow the air sucked into the case 11 from the suction port 12a through the heat exchanger 20 and blow out from the blower outlet 12b. The four air outlets 12b are arranged 90 degrees apart around the inlet 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 the four outlets 12b.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

  DESCRIPTION OF SYMBOLS 1 Compressor, 2 Outdoor unit heat exchanger, 3 Expansion valve, 4 Indoor unit heat exchanger, 5 Four 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 part, 21A 1st heat exchange area, 21B 2nd heat exchange area, 21C 3rd heat exchange area, 21D 4th heat exchange area, 22 2nd heat exchange part, 23 3rd heat Exchange part, 24 4th heat exchange part, 30 air blower, 100 air conditioner, FI fin, PI heat transfer pipe, PI1 first heat transfer pipe, PI2 second heat transfer pipe.

Claims (6)

A plurality of fins stacked on each other and a heat transfer tube penetrating the plurality of fins, and heat exchange between the refrigerant flowing inside the heat transfer tube and the air flowing outside the heat transfer tube A heat exchanger for condensation,
A first heat exchange section;
A second heat exchanging part that faces the first heat exchanging part and is arranged leeward than the first heat exchanging part in the air flow,
The second heat exchange part 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 a direction in which the second heat exchange unit extends,
The second heat exchange region is a heat exchanger that is separated from the first heat exchange region along a direction in which the second heat exchange unit extends.   2. The heat exchanger according to claim 1, wherein the number of passes of the heat transfer tubes in the first heat exchange unit is smaller than the number of passes of the heat transfer tubes in the second heat exchange unit. In the first heat exchange section, the heat transfer tube has a first heat transfer tube portion and a second heat transfer tube portion adjacent to the first heat transfer tube portion,
Each of the first heat transfer tube portion and the second heat transfer tube portion passes through the first heat exchange portion a plurality of times so as to be folded along the direction in which the second heat exchange portion extends,
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 portion at the inlet and the outlet of the first heat exchange portion is the first number of the second heat transfer tube portion. The heat exchanger according to claim 1 or 2, wherein the number of times of passing through either one of the first heat exchange region and the second heat exchange region is the same. The first heat exchange unit has a third heat exchange region and a fourth heat exchange region arranged along a direction in which the second heat exchange unit extends,
The fourth heat exchange region is separated from the third heat exchange region along a direction in which the second heat exchange unit 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 a direction in which the second heat exchange unit extends. And
In 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 of the first heat transfer tube portion, the second heat exchange region, The number of times of passing through either the third heat exchange region or the fourth heat exchange region is that the first heat exchange region, the second heat exchange region, the third heat exchange region, The heat exchanger according to claim 3, wherein the heat exchanger has the same number of passes through any one of the fourth heat exchange regions. The heat exchanger according to any one of claims 1 to 4,
An air conditioner comprising: 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.