JP2016095094A - Heat exchanger and refrigeration cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger and a refrigeration cycle device capable of improving heat transfer performance and oil return performance and restricting occurrence of dew condensation.SOLUTION: One header of a first header and a second header in the heat exchanger in one preferred embodiment is provided with a partition member for parting one header into an upstream side and a downstream side in an air flowing direction. Within a heat exchanging tube are arranged a first flow passage block and a second flow passage block. The first flow passage block is communicated with a portion positioned at one side in the air flowing direction in respect to the partition member in one header. The second flow passage block is communicated with a part positioned at the other side in an air flowing direction in respect to the partition member in one header. Then, an equivalent diameter of the second flow passage block where gas-rich gas-liquid double phase refrigerant flows, of the first flow passage block and the second flow passage block, is larger as compared with an equivalent diameter of the first flow passage block where liquid rich gas-liquid double phase refrigerant flows.SELECTED DRAWING: Figure 3

Description

  Embodiments described herein relate generally to a heat exchanger and a refrigeration cycle apparatus.

  A refrigeration cycle apparatus such as an air conditioner is equipped with a heat exchanger for exchanging heat between the refrigerant and the heat exchange air. As this type of heat exchanger, a so-called parallel flow type comprising a pair of headers and a plurality of heat exchange tubes arranged in parallel in the extending direction of the headers and connecting the headers in parallel. There is a heat exchanger. In this type of heat exchanger, fins are joined between adjacent heat exchange tubes, and heat exchange is performed by passing heat exchange air through a gap between the fins and the heat exchange tubes.

  By the way, in the parallel flow type heat exchanger described above, when the number of heat exchange tubes connected between the headers increases as the length of each header increases, the heat flows through each heat exchange tube. The mass speed of the refrigerant is reduced. Then, there are concerns such as a decrease in heat transfer performance in each heat exchange tube and a decrease in oil return to the compressor.

  For example, when using a heat exchanger as an evaporator in an indoor unit, it is desirable that the evaporation is completed (dry out) when the refrigerant passes through the heat exchange tube. However, in a heat exchanger having a so-called single-row configuration in which the heat exchange tubes are arranged in only one row (the refrigerant flow direction is one direction) in the flow direction of the heat exchange air, depending on the external environment or the like, The refrigerant may dry out. In this case, in the heat exchange tube, the heat exchange air that passes through the region (superheated region) downstream from the position where the refrigerant is dried out passes through the heat exchanger as raw air that is not heat exchanged by the heat exchanger. After that, the heat exchange air that has passed through the superheated area comes into contact with the fan or air outlet cooled by the heat exchange air that has passed through the upstream area (non-superheated area) of the heat exchange tube. May occur and water droplets may scatter in the room.

JP 2009-270781 A JP 2002-206890 A

  The problem to be solved by the present invention is to provide a heat exchanger and a refrigeration cycle apparatus that can improve heat transfer performance and oil return and can suppress the occurrence of condensation.

  The heat exchanger of the embodiment includes a first header and a second header, a heat exchange tube, and fins. The heat exchange tubes are arranged at intervals in the extending direction of the first header and the second header, and connect between the first header and the second header. The fin is disposed between adjacent heat exchange tubes. At least one of the first header and the second header is provided with a partition member for partitioning one header on the upstream side and the downstream side in the air flow direction of the heat exchange air passing between adjacent heat exchange tubes. Established. The heat exchange tube has a first flow path block and a second flow path block. The first flow path block communicates with a portion located on one side in the air flow direction with respect to the partition member in one header. The second flow path block communicates with a portion located on the other side in the air flow direction with respect to the partition member in one header. Of the first flow path block and the second flow path block, the equivalent diameter of the second flow path block through which the gas-rich gas-liquid two-phase refrigerant with a large dryness of the refrigerant circulates is a liquid rich with a small dryness of the refrigerant. This is larger than the equivalent diameter of the first flow path block through which the gas-liquid two-phase refrigerant flows.

The schematic block diagram of the refrigerating-cycle apparatus in embodiment. The front view which looked at the indoor heat exchanger in embodiment from the Y direction. Sectional drawing equivalent to the III-III line | wire of FIG. 2 at the time of making the indoor heat exchanger in 1st Embodiment function as an evaporator. The top view which looked at the heat exchange tube in 1st Embodiment from the 1st header side. The top view which looked at the heat exchange tube in 1st Embodiment from the 2nd header side. The fragmentary sectional view equivalent to the VI-VI line of FIG. Sectional drawing equivalent to the III-III line | wire of FIG. 2 at the time of making the indoor heat exchanger in 1st Embodiment function as a condenser. The top view equivalent to FIG. 4 which concerns on the other structure of 1st Embodiment. The fragmentary sectional view equivalent to FIG. 6 in 2nd Embodiment. The fragmentary sectional view of the 1st header and heat exchange tube in a 3rd embodiment. Sectional drawing equivalent to the III-III line | wire of FIG. 2 at the time of making the indoor heat exchanger in 4th Embodiment function as an evaporator. The top view which looked at the heat exchange tube in 4th Embodiment from the 1st header side. The top view which looked at the heat exchange tube in 4th Embodiment from the 2nd header side. Sectional drawing equivalent to the III-III line | wire of FIG. 2 at the time of making the indoor heat exchanger in 4th Embodiment function as a condenser. FIG. 13 is a plan view corresponding to FIG. 12 according to another configuration of the fourth embodiment.

Hereinafter, the refrigeration cycle apparatus of the embodiment will be described with reference to the drawings.
(First embodiment)
As shown in FIG. 1, the refrigeration cycle apparatus 1 of this embodiment includes a compressor 2, a four-way valve 3, an outdoor heat exchanger 4, an expansion valve 5, a gas-liquid separator 6, and an indoor heat exchanger 7. 8 are sequentially connected. In the example shown in FIG. 1, the solid line arrow indicates the refrigerant flow direction during cooling, and the broken line arrow indicates the refrigerant flow direction during heating.

The compressor 2 includes a compressor body 11 and an accumulator 12.
The accumulator 12 is configured to capture a liquid refrigerant among the refrigerants supplied to the compressor body 11 and supply a gas refrigerant to the compressor body 11.
The compressor main body 11 compresses the gas refrigerant taken in through the accumulator 12 into a high-temperature and high-pressure gas refrigerant.

The gas-liquid separator 6 is arranged on the upstream side of the indoor heat exchanger 7, and among the refrigerants flowing through the refrigerant flow path 8, the liquid refrigerant is circulated toward the indoor heat exchanger 7 to heat the gas refrigerant. It is made to circulate toward the exchanger detour 14.
The heat exchanger bypass circuit 14 connects the gas-liquid separator 6 and the downstream side of the indoor heat exchanger 7 in the refrigerant flow path 8 to bypass the indoor heat exchanger 7. An on-off valve 15 is provided on the heat exchanger bypass 14. The on-off valve 15 is controlled to be closed when the heating operation is performed and is opened when the cooling operation is performed.

In such a refrigeration cycle apparatus 1, a cooling operation or a heating operation is performed by changing the flow of the refrigerant by the four-way valve 3. For example, in the cooling operation, in the refrigerant flow path 8, the compressor 2, the four-way valve 3, the outdoor heat exchanger 4, the expansion valve 5, the gas-liquid separator 6, and the indoor heat exchanger 7 are connected in order. At this time, the outdoor heat exchanger 4 is made to function as a condenser, the indoor heat exchanger 7 is made to function as an evaporator, and the room is cooled. Of the refrigerant that has flowed into the gas-liquid separator 6, the gas refrigerant flows through the heat exchanger bypass 14 and bypasses the indoor heat exchanger 7 and flows directly into the compressor 2.
On the other hand, in the heating operation, the compressor 2, the four-way valve 3, the indoor heat exchanger 7, the gas-liquid separator 6, the expansion valve 5, and the outdoor heat exchanger 4 are sequentially connected in the refrigerant flow path 8. At this time, the indoor heat exchanger 7 is caused to function as a condenser, and the outdoor heat exchanger 4 is caused to function as an evaporator, thereby heating the room.

Next, the indoor heat exchanger 7 will be described in detail.
As shown in FIG. 2, the indoor heat exchanger 7 is a so-called parallel flow type heat exchanger, and includes a plurality of first headers 21 and second headers 22 and a plurality of these headers 21 and 22 connected in parallel. And a heat exchange tube 23. In the following description, the extending direction of the heat exchange tube 23 will be described as the Z direction, and the directions orthogonal to the Z direction will be described as the X direction and the Y direction, respectively. In the present embodiment, the indoor heat exchanger 7 is arranged such that the Z direction is the vertical direction, and the first header 21 side along the Z direction is located below and the second header 22 side is located above.

  The first header 21 and the second header 22 have a tubular shape extending along the X direction, and extend in parallel to each other.

  As shown in FIGS. 2-5, each heat exchange tube 23 is made into the ellipse shape (flat tube) which makes the Y direction a major axis direction, and is mutually arrange | positioned in parallel with the X direction at intervals. Each heat exchange tube 23 has an upper end connected to the second header 22 and a lower end connected to the first header 21. Moreover, in each heat exchange tube 23, the some refrigerant | coolant circulation hole 24 which penetrates the heat exchange tube 23 to a Z direction is formed at intervals in the Y direction. In this embodiment, each refrigerant | coolant circulation hole 24 is made into the equivalent flow-path cross-sectional area, respectively, and is arrange | positioned at intervals in the Y direction. In the indoor heat exchanger 7 of the present embodiment, the aspect ratio (the length dimension (X direction) of each header 21 and 22 with respect to the length dimension (Z direction) of the heat exchange tube 23) is 2 or more. Yes.

  As shown in FIGS. 2 and 6, the indoor heat exchanger 7 includes fins 31 that connect the adjacent heat exchange tubes 23. The fin 31 is, for example, a corrugated fin, and has a wave shape extending along the Z direction between the heat exchange tubes 23, and a peak portion and a valley portion thereof are respectively joined to the adjacent heat exchange tubes 23. . In the indoor heat exchanger 7, the heat exchange air A passes through the gaps between the fins 31 and the heat exchange tubes 23 along the Y direction. At this time, the heat exchange between the refrigerant circulating in the heat exchange tube 23 and the heat exchange air A is performed via the heat exchange tube 23 and the fins 31. The fins 31 are not limited to corrugated fins, and for example, plate fins may be used.

  Here, as shown in FIG. 3, the first header 21 described above extends in the first header 21 over the entire area in the X direction, and the first header 21 extends to one side and the other side in the Y direction. A partition member 32 for partitioning is provided. Thereby, the heat exchange tube 23 is connected to the first flow path block 33 communicating with the portion located on one side in the Y direction with respect to the partition member 32 in the first header 21, and the Y to the partition member 32. The second flow path block 34 communicates with a portion located on the other side of the direction.

  In this case, the partition member 32 divides the heat exchange tube 23 (refrigerant flow hole 24) so that the equivalent diameter of the second flow path block 34 is larger than the equivalent diameter of the first flow path block 33. . The partition member 32 according to the present embodiment is disposed closer to one side with respect to the central portion in the Y direction in the first header 21. Therefore, the total (number of holes) of the refrigerant flow holes 24 on the second flow path block 34 side is larger than the total of the refrigerant flow holes 24 on the first flow path block 33 side. The equivalent diameter is a diameter when the refrigerant circulation holes 24 constituting the flow path blocks 33 and 34 are converted into one equivalent circular pipe. In this case, the equivalent diameter is expressed as 4 S / T, where S is the cross-sectional area of the flow path blocks 33 and 34, and T is the circumferential length of the flow path blocks 33 and 34.

  Further, in the first header 21, portions located on one side and the other side in the Y direction with respect to the partition member 32, one side refrigerant inlet / outlet 41 connected to the refrigerant flow path (outside) 8 and the other side refrigerant. Each doorway 42 is provided. In this case, when the indoor heat exchanger 7 functions as an evaporator, the one-side refrigerant inlet / outlet 41 becomes an inlet / outlet to the indoor heat exchanger 7, and the other-side refrigerant inlet / outlet 42 becomes an outlet / outlet from the indoor heat exchanger 7. . As shown in FIG. 7, when the indoor heat exchanger 7 functions as a condenser, the other-side refrigerant inlet / outlet 42 becomes an inlet / outlet to the indoor heat exchanger 7, and the one-side refrigerant inlet / outlet 41 becomes an indoor heat exchanger 7. It becomes the outflow from.

  In the above-described configuration, as shown in FIG. 3, when the indoor heat exchanger 7 functions as an evaporator, the refrigerant decompressed by the expansion valve 5 is liquid refrigerant or liquid-rich gas-liquid two with a low dryness of the refrigerant. The refrigerant flows into the first header 21 from the one-side refrigerant inlet / outlet 41 as a phase refrigerant (see arrow C in the figure). The refrigerant that has flowed into the first header 21 flows into the refrigerant flow hole 24 on the first flow path block 33 side in the heat exchange tube 23, and faces the first flow path block 33 upward (second header 22 side). And then flows into the second header 22. Thereafter, the refrigerant that has flowed into the second header 22 flows into the refrigerant flow hole 24 on the second flow path block 34 side in the heat exchange tube 23, and moves down the second flow path block 34 (on the first header 21 side). Circulate towards Thereafter, the refrigerant flows into a portion located on the other side in the first header 21 with respect to the partition member 32, is discharged to the refrigerant flow path 8 through the other-side refrigerant inlet / outlet 42, and flows toward the compressor 2.

  As described above, in the indoor heat exchanger 7 of the present embodiment, after the refrigerant flowing upward in the first flow path block 33 is folded back by the second header 22, the second flow path block 34 is directed downward. Circulate. Thereby, the refrigerant flows from one side in the Y direction to the other side while meandering in the Z direction. In other words, the first flow path block 33 and the second flow path block 34 of the present embodiment are arranged in parallel in the Y direction while the refrigerant flow directions are different in the Z direction. In this case, the heat exchange tubes 23 of the present embodiment have only one row in the Y direction, but the so-called two rows in which a plurality of flow paths having different refrigerant flow directions are arranged in two rows in the Y direction. You can think of it as a configuration.

  In the indoor heat exchanger 7 of the present embodiment, the heat exchange air A passes through the indoor heat exchanger 7 from one side (upstream side) to the other side (downstream side) in the Y direction. The exchange air A and the refrigerant are parallel flows having the same flow direction. Specifically, the heat exchange air A passes through the gaps between the fins 31 and the heat exchange tubes 23 along the Y direction, so that the heat exchange air A passes through the heat exchange tubes 23 and the fins 31 and enters the heat exchange tubes 23. Heat exchange with the refrigerant flowing through At this time, the refrigerant flowing into the indoor heat exchanger 7 absorbs heat in the process of flowing through the heat exchange tube 23, thereby cooling the heat exchange air A and gradually increasing the gas rich from the liquid-rich gas-liquid two-phase refrigerant. It becomes a gas-liquid two-phase refrigerant. Therefore, the refrigerant flowing through the first flow path block 33 becomes richer than the refrigerant flowing through the second flow path block 34.

  On the other hand, when the indoor heat exchanger 7 is caused to function as a condenser, the refrigerant flows in the opposite direction to the case where the indoor heat exchanger 7 functions as an evaporator. That is, the refrigerant discharged from the compressor 2 flows into the first header 21 from the other-side refrigerant inlet / outlet 42 as a gas refrigerant or a gas-rich gas-liquid two-phase refrigerant. The refrigerant that has flowed into the first header 21 circulates with the second flow path block 34 facing upward, is then folded back by the second header 22, and circulates with the first flow path block 33 facing downward. Thereafter, the refrigerant is discharged to the refrigerant flow path 8 through the one-side refrigerant inlet / outlet 41 of the first header 21 and flows toward the expansion valve 5. Thereby, the refrigerant flows from the other side in the Y direction toward the one side while meandering in the Z direction.

  Further, as described above, the heat exchange air A passes through the indoor heat exchanger 7 from one side in the Y direction toward the other side. That is, when the indoor heat exchanger 7 of the present embodiment is caused to function as a condenser, the heat exchange air A and the refrigerant are opposed to each other in the opposite flow directions. At this time, the refrigerant flowing into the indoor heat exchanger 7 dissipates heat in the process of flowing through the heat exchange tube 23, thereby heating the heat exchange air A and liquid-rich gas from the gas-rich gas-liquid two-phase refrigerant. Becomes a liquid two-phase refrigerant. Therefore, the refrigerant flowing through the first flow path block 33 becomes richer than the refrigerant flowing through the second flow path block 34.

  According to this embodiment, since the partition member 32 is disposed in the first header 21, the flow direction of the refrigerant is different in the Z direction, and a plurality of flow path blocks 33 arranged in parallel in the Y direction. The heat exchange tube 23 can be divided into 34. Therefore, for example, when the indoor heat exchanger 7 is made to function as an evaporator, an overheat region is generated at least on the first flow path block 33 side by designing to complete the evaporation when the heat exchanger tube 23 is passed. Can be suppressed. That is, since at least the entire first flow path block 33 side can be set as a non-superheated region in which the liquid-rich gas-liquid two-phase refrigerant flows, the non-superheated region is extended over the entire Z direction in the indoor heat exchanger 7. Can be formed. As a result, the heat exchange air A can be prevented from passing through the indoor heat exchanger 7 as raw air, and the occurrence of condensation can be suppressed.

In the present embodiment, the equivalent diameter of the second flow path block 34 through which the gas-rich gas-liquid two-phase refrigerant flows is set to be larger than the equivalent diameter of the first flow path block 33 through which the liquid-rich gas-liquid two-phase refrigerant flows. It was set as the structure enlarged.
According to this configuration, the pressure loss of the refrigerant can be reduced in the second flow path block 34. In particular, when the indoor heat exchanger 7 functions as an evaporator, a pressure drop on the suction side of the compressor 2 can be suppressed, so that a load applied to the compressor 2 can be reduced.
Moreover, in the 1st flow path block 33, the mass velocity of a refrigerant | coolant can be increased, and while improving heat transfer performance, oil return property can be improved.

  In addition, the flow direction of the refrigerant in each of the flow path blocks 33 and 34 is different from each other in the Z direction, and is arranged in parallel in the Y direction. Therefore, when one of the condenser and the evaporator functions, The exchange air A can be a counterflow. Therefore, the heat source temperature difference between the refrigerant and the heat exchange air A can be secured on the downstream side in the flow direction of the heat exchange air A, and the efficiency of heat exchange can be improved. Thereby, the amount of supercooling when functioning as a condenser and the degree of superheat when functioning as an evaporator can be ensured.

And since the refrigeration cycle apparatus 1 of this embodiment is equipped with the indoor heat exchanger 7 mentioned above, the refrigeration cycle apparatus 1 with high quality and high reliability can be provided.
In addition, in the present embodiment, the gas-liquid separator 6 is disposed upstream of the indoor heat exchanger 7, so that when the indoor heat exchanger 7 functions as an evaporator, the liquid-rich gas-liquid two is used. Phase refrigerant can be supplied to the indoor heat exchanger 7. Thereby, the pressure loss of the refrigerant in the indoor heat exchanger 7 can be reduced, and the distribution of the refrigerant flowing into each heat exchange tube 23 can be made uniform.

  In the above-described embodiment, the case where the equivalent diameter of each flow path block 33, 34 is adjusted by adjusting the number of refrigerant circulation holes 24 between the flow path blocks 33, 34 has been described. Not limited to. For example, as shown in FIG. 8, the equivalent diameter of each flow path block 33, 34 may be adjusted by adjusting the flow path cross-sectional area of the refrigerant flow hole 24 between each flow path block 33, 34. Absent.

  That is, in the heat exchange tube 23 shown in FIG. 8, the flow passage cross-sectional area of the refrigerant flow hole 24 on the first flow passage block 33 side is larger than the flow passage cross-sectional area of the refrigerant flow hole 24 on the second flow passage block 34 side. It is getting smaller. And the partition member 32 is arrange | positioned in the center part of the Y direction in the 1st header 21, and has divided | segmented the refrigerant | coolant circulation hole 24 by the same number on the one side and the other side of a Y direction. In addition, you may adjust both the number of the refrigerant | coolant circulation holes 24, and a flow-path cross-sectional area, and may adjust the equivalent diameter of each flow-path block 33,34.

(Second Embodiment)
In the following description, the same components as those in the first embodiment described above are denoted by the same reference numerals, and description thereof is omitted.
In the indoor heat exchanger 101 shown in FIG. 9, the fin 131 penetrates the fin 131 in the Z direction in the portion located between the flow path blocks 33 and 34 of the fin 131 (the portion located in the Y direction equivalent to the partition member 32). A fin cut portion 102 is formed. The fin cut portion 102 has a predetermined width in the Y direction and has a slit shape extending along the X direction, and divides the fin 131 into one side and the other side in the Y direction.

  According to this configuration, since heat transfer between the flow path blocks 33 and 34 (between the same heat sources) via the fins 131 can be suppressed, so-called thermal interference that hinders the original heat exchange function of the evaporator and the condenser is prevented. Generation | occurrence | production can be suppressed and the heat exchange between a refrigerant | coolant and the heat exchange air A can be accelerated | stimulated. In addition, if the structure of the fin cut part 102 is a structure which suppresses the heat transfer between each flow path blocks 33 and 34 via the fin 131, a design change is possible suitably. In this case, the fin cut portion 102 may be a cut that penetrates the fin 131 in the Z direction. Further, the fin cut portion 102 may be a hole formed intermittently in the X direction.

(Third embodiment)
In the following description, the same components as those in the above-described embodiments are denoted by the same reference numerals and description thereof is omitted.
In the indoor heat exchanger 201 shown in FIG. 10, a recessed portion 222 that is recessed upward is formed in a portion of the first header 221 that is positioned in the same direction as the partition member 32 in the Y direction. The recess 222 extends over the entire area of the first header 221 in the X direction, and the partition member 32 described above is disposed on the top thereof. That is, the first header 221 is divided into one side and the other side in the Y direction by the partition member 32 and the recessed portion 222.

  According to this configuration, since the recess 222 is formed at the same position as the partition member 32 in the Y direction, the area of the partition member 32 can be reduced, and one side and the other side of the first header 21 in the Y direction. There will be an air layer between the sides. Therefore, heat transfer between one side and the other side (between the same heat sources) in the Y direction in the first header 21 via the partition member 32 can be suppressed. Thereby, since generation | occurrence | production of a heat interference can be suppressed, while being able to ensure the amount of supercooling at the time of functioning the indoor heat exchanger 7 as a condenser, it is the refrigerant | coolant at the time of functioning the indoor heat exchanger 7 as an evaporator. Recooling can be suppressed. In addition, you may fill with heat insulation etc. in the hollow part 222 separately.

(Fourth embodiment)
The present embodiment is different from the above-described embodiments in that the partition members 332a and 332b are disposed on both the first header 321 and the second header 322. In the following description, the same components as those in the above-described embodiments are denoted by the same reference numerals and description thereof is omitted.
As shown in FIG. 11, the indoor heat exchanger 301 of the present embodiment includes a first partition member 332 a disposed in the first header 321 and a second partition member 332 b disposed in the second header 322. And have.

The first partition member 332a is disposed closer to one side with respect to the central portion in the Y direction in the first header 321, and partitions the first header 321 in the Y direction.
The second partition member 332b is disposed in the second header 322 on the other side in the Y direction with respect to the first partition member 332a described above (in the illustrated example, the center portion in the Y direction in the second header 322). The second header 322 is partitioned in the Y direction.

  As shown in FIGS. 11 to 13, each heat exchange tube 23 includes a first flow path block 333 located on one side in the Y direction with respect to the first partition member 332 a, a first partition member 332 a, and a second partition member. The second flow path block 334 located between the second flow path block 334 and the third flow path block 335 located on the other side in the Y direction with respect to the second partition member 332b. That is, in each heat exchange tube 23 of the present embodiment, the first flow path block 333, the second flow path block 334, and the third flow path block 335 are sequentially arranged from one side to the other side in the Y direction.

  In this case, the partition members 332a and 332b are configured so that the equivalent diameters of the flow path blocks 333 to 335 increase in the order of the first flow path block 333, the second flow path block 334, and the third flow path block 335. Each heat exchange tube 23 is divided. In the illustrated example, each partition member 332a, 332b has a total (number of holes) of the refrigerant flow holes 24 constituting the flow path blocks 333 to 335 such that the first flow path block 333, the second flow path block 334, And each heat exchange tube 23 is divided so that it may increase in order of the 3rd channel block 335.

A portion of the first header 321 located on one side in the Y direction with respect to the first partition member 332a (portion communicating with the first flow path block 333) is connected to the expansion valve 5 via the refrigerant flow path 8. A first refrigerant inlet / outlet 341 to be connected is formed.
Of the second header 322, a portion located on the other side in the Y direction with respect to the second partition member 332 b (portion communicating with the third flow path block 335) is connected to the compressor 2 via the refrigerant flow path 8. A second refrigerant inlet / outlet 342 to be connected is formed.

  In the configuration described above, when the indoor heat exchanger 7 functions as an evaporator, a gas refrigerant or a gas-rich gas-liquid two-phase refrigerant flows into the first header 321 from the first refrigerant inlet / outlet 341. Thereafter, the refrigerant flowing into the first header 321 circulates from one side in the Y direction toward the other side while meandering in the Z direction. Specifically, the refrigerant that has flowed into the first header 321 flows upward through the first flow path block 333 and is folded back within the second header 322, and then the second flow path block 334 is moved downward. Circulate towards. The refrigerant is folded in the first header 321 and flows upward through the third flow path block 335, and then is discharged to the refrigerant flow path 8 from the second refrigerant inlet / outlet 342 formed in the second header 322. The

  According to this configuration, since the second refrigerant inlet / outlet 342 is formed in the second header 322 located above, simple gas-liquid separation is performed in the process in which the refrigerant flows toward the second header 322. become. That is, since the liquid refrigerant is hardly discharged from the second refrigerant inlet / outlet 342 and the gas refrigerant is positively discharged, more gas-rich refrigerant can be supplied to the compressor 2. Therefore, the operation reliability of the compressor 2 can be improved.

  On the other hand, as shown in FIG. 14, when the indoor heat exchanger 7 functions as a condenser, the refrigerant discharged from the compressor 2 flows into the second header 322 from the second refrigerant inlet / outlet 342. Thereafter, the refrigerant flowing into the second header 322 circulates from the other side in the Y direction toward one side while meandering in the Z direction. Specifically, the refrigerant that has flowed into the second header 322 flows downward through the third flow path block 335, and then is folded back by the first header 321 and flows upward through the second flow path block 334. To do. Then, the refrigerant is folded at the first header 321, flows downward through the first flow path block 333, and then discharged to the refrigerant flow path 8 through the first refrigerant inlet / outlet 341.

  According to this configuration, since the first refrigerant inlet / outlet 341 is formed in the first header 321 positioned below, simple gas-liquid separation is performed in the process in which the refrigerant flows toward the first header 321. become. That is, it is difficult for the gas refrigerant to be discharged from the first refrigerant inlet / outlet 341 and the liquid refrigerant is actively discharged, so that a liquid-rich refrigerant can be supplied to the expansion valve 5. Therefore, the opening degree of the expansion valve 5 can be maintained in an appropriate range.

In the above-described fourth embodiment, the case where the equivalent diameter of each flow path block 333 to 335 is adjusted by adjusting the number of the refrigerant circulation holes 24 between the flow path blocks 333 to 335 has been described. However, it is not limited to this. For example, as shown in FIG. 15, the equivalent diameter of each flow path block 333 to 335 may be adjusted by adjusting the flow path cross-sectional area of the refrigerant flow hole 24 between the flow path blocks 333 to 335. Absent.
That is, in the heat exchange tube 23 shown in FIG. 15, the flow passage cross-sectional area of the refrigerant circulation hole 24 increases sequentially from the first flow passage block 333 to the third flow passage block 335. The partition members 332a and 332b divide the coolant circulation holes 24 by the same number. Moreover, you may adjust both the number of the refrigerant | coolant circulation holes 24, and a flow-path cross-sectional area, and may adjust the equivalent diameter of each flow-path block 333-335.

Moreover, although the case where the heat exchanger of embodiment was used for the indoor heat exchanger 7 was demonstrated in the description mentioned above, it is not restricted to this. That is, the configuration of the heat exchanger according to the embodiment may be adopted for the outdoor heat exchanger 4.
Moreover, although embodiment mentioned above demonstrated the case where the indoor heat exchanger 7 was functioned as a condenser and the refrigerant | coolant and the heat exchange air A became a counterflow, it is not restricted to this. You may comprise so that it may become a counterflow when the indoor heat exchanger 7 is functioned as an evaporator.

Further, the aspect ratio of the indoor heat exchanger 7 can be changed as appropriate.
Moreover, although embodiment mentioned above demonstrated the case where the indoor heat exchanger 7 was arrange | positioned so that a 1st header and a 2nd header may become up and down, it is not restricted to this.
In the above-described embodiment, the configuration in which each flow path block has the plurality of refrigerant circulation holes 24 has been described. However, the flow path block may have at least one refrigerant circulation hole 24.
Further, in the above-described embodiment, the configuration in which the heat exchange tubes 23 are arranged in one row in the flow direction (Y direction) of the heat exchange air A has been described.

According to at least one embodiment described above, since the partition member is disposed in at least one of the headers, the flow direction of the refrigerant is different in the Z direction, and the first and the first arranged in parallel in the Y direction. The heat exchange tube can be divided into two flow path blocks. Therefore, for example, when an indoor heat exchanger functions as an evaporator, it is designed to complete evaporation when it passes through the heat exchange tube, thereby suppressing the occurrence of an overheating region at least on the first flow path block side. it can. That is, since a non-superheated region can be formed over the entire Z direction in the indoor heat exchanger, it is possible to suppress heat exchange air from passing through the indoor heat exchanger as raw air and to suppress the occurrence of condensation.
Further, the equivalent diameter of the second flow path block through which the gas-rich gas-liquid two-phase refrigerant flows is made larger than the equivalent diameter of the first flow path block through which the liquid-rich gas-liquid two-phase refrigerant flows, so that the first The pressure loss of the refrigerant can be reduced in the flow path block. In particular, when the indoor heat exchanger functions as an evaporator, the pressure drop on the suction side of the compressor can be suppressed, so the load on the compressor can be reduced.
Moreover, in the 2nd flow path block, the mass velocity of a refrigerant | coolant can be increased, and while improving heat transfer performance, oil return property can be improved.

  Although several embodiments of the present invention have been described, these embodiments are presented by way of example and are not intended to limit the scope of the invention. These embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the spirit of the invention. These embodiments and their modifications are included in the scope and gist of the invention, and are also included in the invention described in the claims and the equivalents thereof.

DESCRIPTION OF SYMBOLS 1 ... Refrigeration cycle apparatus, 2 ... Compressor (external), 4 ... Outdoor heat exchanger, 5 ... Expansion valve (external), 7, 101, 201, 301 ... Indoor heat exchanger (heat exchanger), 21,221 , 321 ... first header, 22, 322 ... second header, 23 ... heat exchange tube, 31, 131 ... fins, 32 ... partition members, 33, 333 ... first flow path block, 34, 334 ... second flow path Block 102, fin cut part 222 222 dent part 332 a first partition member 332 b second partition member 335 third channel block 341 first refrigerant inlet / outlet 342 second refrigerant inlet / outlet

Claims (5)

A first header and a second header;
A plurality of heat exchange tubes arranged between the first header and the second header at intervals in the extending direction, and connecting between the first header and the second header;
A heat exchanger comprising: fins disposed between adjacent heat exchange tubes;
In at least one of the first header and the second header, the one header is partitioned on the upstream side and the downstream side in the air flow direction of the heat exchange air passing between the adjacent heat exchange tubes. A partition member is provided,
In the heat exchange tube,
A first flow path block communicating with a portion located on one side of the air flow direction with respect to the partition member in the one header;
A second flow path block communicating with a portion located on the other side in the air flow direction with respect to the partition member in the one header;
Including
Of the first flow path block and the second flow path block, the equivalent diameter of the second flow path block through which the gas-rich gas-liquid two-phase refrigerant with a high dryness of the refrigerant flows is a liquid with a low dryness of the refrigerant. It is larger than the equivalent diameter of the first flow path block through which the rich gas-liquid two-phase refrigerant flows.
Heat exchanger. A fin cut portion is formed in a portion of the fin located between the first flow path block and the second flow path block of the heat exchange tube in the air flow direction.
The heat exchanger according to claim 1. A recess is formed in a portion of the one header where the partition member in the air flow direction is located.
The heat exchanger according to claim 1 or 2. Inside the first header and the second header, the partition members are arranged separately,
The first header is disposed below the second header, and has a first refrigerant inlet / outlet communicating the first flow path block side with the outside,
The second header has a second refrigerant inlet / outlet communicating the second flow path block side with the outside.
The heat exchanger according to any one of claims 1 to 3. A compressor for compressing the refrigerant;
An indoor heat exchanger and an outdoor heat exchanger connected to the compressor;
An expansion device disposed between the indoor heat exchanger and the outdoor heat exchanger,
At least one of the indoor heat exchanger and the outdoor heat exchanger includes the heat exchanger according to any one of claims 1 to 4.
Refrigeration cycle equipment.

Images