JP5677220B2 - Refrigeration cycle equipment - Google Patents

Description

  The present invention relates to a refrigeration cycle apparatus.

  As a background art in this technical field, there is JP-A-2009-121708 (Patent Document 1). In this publication, in a heat exchanger used for an air conditioner, a refrigerator, etc., a pair of header pipes 11 and 12 that are horizontally opposed to each other, and upper and lower ends thereof are connected in communication with the header pipes 11 and 12. It describes that a plurality of flat heat exchange tubes 13A arranged in parallel with the flat surfaces, and heat exchange fins 14A closely attached to the gaps between the flat heat exchange tubes 13A (see summary). In this heat exchanger, the refrigerant is supplied from one header pipe to each flat heat exchange pipe 13A, and heat is exchanged with air in the flat heat exchange pipe 13A, and then the refrigerant flows through the other header pipe. ing.

JP 2009-121708 A

  As shown in FIG. 2 of Patent Document 1, the heat exchanger described in Patent Document 1 has a plurality of flat heat exchange pipes each having a horizontal upper end and a lower end. The inlet of the refrigerant passage to the flat heat exchange pipe is located on the same horizontal plane and has the same height. And with respect to such a heat exchanger, heat exchange can be efficiently performed by blowing air from a direction parallel to the flat surface of the flat heat exchange tube.

  In this case, when a two-phase refrigerant of liquid and gas flows from one header pipe to the flat heat exchange pipe, the liquid refrigerant and the gas refrigerant flow through the flat heat exchange pipe at approximately the same ratio in each refrigerant passage. This point will be described with reference to FIG. 12. In FIG. 12, 10 is an upper header pipe, 11 is a lower header pipe, 12 is a flat heat transfer tube connecting these header pipes, The figure which looked at the flat surface from the front is shown. A plurality of refrigerant flow paths (not shown) are formed in the flat heat transfer tube 12 in the vertical direction, and the refrigerant flows from the header pipe 10 to the header pipe 11 after flowing through these refrigerant flow paths. In addition, the arrow of FIG. 12 has shown the flow of air, and has shown flowing through the flat surface of the flat heat exchanger tube 12 from the left side to the right side.

  The air flows to the right side while exchanging heat with the refrigerant flowing in the respective refrigerant flow paths, but since the temperature of the air decreases toward the right side, the refrigerant in the refrigerant flow path formed on the right side The heat exchange efficiency becomes worse compared to the left side. If it does so, it will flow out of a heat exchanger, without a liquid refrigerant evaporating, it will be in the state with the low specific enthalpy of the refrigerant | coolant in an exit, and the cooling capability will fall, since the latent heat of vaporization which a refrigerant has cannot be fully used. Further, when this liquid refrigerant flows into the compressor, it becomes a wet operation state, and lubrication failure due to dilution of the lubricating oil in the compressor is likely to occur. In severe cases, liquid compression may occur and cause a compressor failure.

  Therefore, the present invention is a refrigeration cycle apparatus including a heat exchanger (evaporator) in which a plurality of refrigerant flow paths are formed, and heat exchange is performed by improving distribution for each refrigerant passage in the heat exchanger (evaporator). The objective is to improve efficiency.

In order to solve the above problems, for example, the configuration described in the claims is adopted. The present application includes a plurality of means for solving the above problems. For example , a compressor that compresses the refrigerant, a condenser that condenses the refrigerant compressed by the compressor, and a condenser that is condensed. In a refrigeration cycle apparatus comprising: a decompression unit that decompresses a refrigerant; an evaporator that evaporates the refrigerant decompressed by the decompression unit; and a blower unit that blows air to the evaporator. A first pipe for flowing the refrigerant in a direction orthogonal to the direction to the evaporator, and a second pipe disposed below the first pipe and for flowing the refrigerant in a direction orthogonal to the direction from the blowing means to the evaporator And a plurality of heat transfer tubes that connect the first pipe and the second pipe and that are arranged in a direction perpendicular to the direction from the blower means to the evaporator, and inside the heat transfer pipe, Multiple towards the evaporator A refrigerant flow path is formed, and the refrigerant from the first pipe flows in from the respective inflow portions of the plurality of refrigerant flow paths, flows through the respective refrigerant flow paths, and then flows to the second pipe, whereby the plurality of refrigerant flows The height position of each inflow portion of the path is configured so as to increase in the direction from the blower means to the evaporator, and the height of the inflow portions of the plurality of heat transfer tubes into which the refrigerant from the first pipe flows. A position is comprised so that it may become low toward the direction where the refrigerant | coolant of a 1st pipe flows .

  ADVANTAGE OF THE INVENTION According to this invention, in the refrigerating-cycle apparatus provided with the heat exchanger (evaporator) in which the some refrigerant | coolant flow path was formed, the heat exchange efficiency in a heat exchanger (evaporator) can be improved. Problems, configurations, and effects other than those described above will be clarified by the following description of embodiments.

1 is a configuration diagram of a refrigeration cycle apparatus of Example 1. FIG. 1 is an overview diagram of a heat exchanger of Example 1. FIG. Sectional drawing of the heat exchanger of Example 1. FIG. 1 is a schematic view of a flat heat transfer tube of Example 1. FIG. Sectional drawing of the flat heat exchanger tube of Example 3. FIG. FIG. 5 is a schematic view of a flat heat transfer tube of Example 3. FIG. 7 is an overview of a heat exchanger according to a fourth embodiment. Sectional drawing of the flat heat exchanger tube of Example 4. FIG. FIG. 6 is an overview diagram of a heat transfer pipe group of Example 4. Sectional drawing of the flat heat exchanger tube of Example 5. FIG. FIG. 9 is an overview diagram of a heat transfer pipe group of Example 5. Sectional drawing of the heat exchanger tube employ | adopted with the conventional heat exchanger.

  Embodiments of the present invention will be described below with reference to the drawings.

  Hereinafter, Example 1 will be described with reference to FIGS. This embodiment relates to a heat exchanger used in an air conditioner, a refrigerator, etc., and in particular, a flat heat transfer tube or a pipe group in which a plurality of flat heat transfer tubes or heat transfer tubes are arranged in a vertical direction. The present invention relates to refrigerant distribution in a heat exchanger in which a plurality of are arranged.

  FIG. 1 shows a configuration diagram of a refrigeration cycle apparatus that includes the heat exchanger of the present embodiment and forms a refrigeration cycle. In the following, an operation state during cooling operation will be described as an example.

  The refrigerant compressed by the compressor 31 built in the outdoor unit 500 passes through the four-way valve 32 and is cooled and liquefied by the outdoor air in the outdoor heat exchanger 1a acting as a condenser. The liquid refrigerant passes through the outdoor expansion valve 33 to be in a low temperature / low pressure state, and is then sent to the indoor unit 501 through the liquid blocking valve 34 and the liquid side connection pipe 35. In the indoor unit, the refrigerant is decompressed by the indoor expansion valve 36 to become a gas-liquid two-phase refrigerant, and flows into the indoor heat exchanger 1b that functions as an evaporator. Here, the refrigerant is heated by the indoor air blown by the indoor blower 51 to become a gas refrigerant. Thereby, the cooling operation which cools indoor air is made.

  Then, it returns to the outdoor unit 500 through the gas side connection pipe 37. In the outdoor unit 500, it passes through the gas blocking valve 38, the four-way valve 32, and the accumulator 39, and is returned to the compressor 31 again to constitute a series of refrigeration cycles. A predetermined amount of refrigerant is enclosed in the refrigeration cycle. Examples of the refrigerant include R410A, R407C, R404A, R134a, R32, HFO1234yf, HFO1234ze (E), R152a, R290, R600a, R744, and R717. Etc. are used.

  Here, in the indoor heat exchanger 1b that acts as an evaporator during cooling, since a gas-liquid two-phase refrigerant flows in, the flow rate distribution ratio is adjusted when the refrigerant is divided into a large number of refrigerant passages of the heat exchanger. Becomes difficult. In particular, when a porous flat tube is used as a heat exchanger as in this embodiment, the number of flow splits increases, so that an imbalance in the flow rate distribution ratio is likely to occur, and sufficient adjustment is necessary for adjustment. Become.

  FIG. 2 shows the heat exchanger 1 of this embodiment. As shown in FIG. 2, in the heat exchanger 1 of this embodiment, header pipes 10 and 11 are arranged at the top and bottom, and a plurality of flat heat transfer tubes 12 are provided between the header pipes. The upper end and the lower end of the flat heat transfer tube 12 are connected to and connected to the header pipes 10 and 11, respectively. In addition, refrigerant connection pipes 101 and 102 are connected to the header pipes 10 and 11, respectively. The arrows in FIG. 2 indicate the flow of air, and air is sent to the flat heat transfer tube 12 by air blowing means (not shown) (corresponding to 50 or 51 in FIG. 1). By this blowing means, air flows along the flat surfaces of the plurality of flat heat transfer tubes 12 provided between the header pipes 10 and 11.

  Here, as shown in FIG. 12, when the positions of the inlets (inflow portions) of the plurality of refrigerant flow paths 15 of the flat heat transfer tube 12 are horizontal and low, the amount of the refrigerant is almost the same for each refrigerant flow path. Two-phase refrigerant will flow in. In FIG. 12, 10 is an upper header pipe, 11 is a lower header pipe, 12 is a flat heat transfer tube connecting these header pipes, and shows a view of the flat surface of the flat heat transfer tube 12 as seen from the front. It is. Moreover, the arrow of FIG. 12 has shown the flow of air, and has shown flowing through the flat surface of the flat heat exchanger tube 12 from the left side to the right side.

  In this case, the air flows to the right side while exchanging heat with the refrigerant flowing in the respective refrigerant flow paths, but the air temperature is lower toward the right side, so that the refrigerant flow path formed on the right side The heat exchange efficiency with the refrigerant is worse than that on the left side. If it does so, liquid refrigerant will flow out of a heat exchanger, without evaporating, and if this liquid refrigerant flows into a compressor, liquid compression will be caused and it may cause a failure of a compressor. Therefore, in this embodiment, this problem is solved by employing the flat heat exchanger shown in FIGS.

  FIG. 3 is a cross-sectional view of the heat exchanger 1 of this embodiment when the flat surface of the flat heat transfer tube 12 is viewed from the front, and FIG. 4 is a perspective view of the flat heat transfer tube 12. As shown in FIG. 4, the flat heat transfer tube 12 is provided with a plurality of refrigerant channels 15 provided in approximately one row. Explaining the flow of the refrigerant in the heat exchanger 1, the gas-liquid two-phase refrigerant supplied from the refrigerant connection pipe 101 to the header pipe 10 flows to the header pipe 11 through the plurality of refrigerant flow paths 15 of the flat heat transfer pipe 12. It is discharged from the refrigerant connection tube 102. While the refrigerant flows through the refrigerant flow path 15 of the plurality of flat heat transfer tubes 12, heat is exchanged with air, the refrigerant evaporates to become a gas refrigerant, and the air is cooled. Here, as shown in FIG. 4, the gas-liquid two-phase refrigerant supplied from the refrigerant connection pipe 101 to the header pipe 10 is separated from the liquid refrigerant downward and the gas refrigerant upward in the header pipe 10.

  The heat exchanger 1 of a present Example is employ | adopted as refrigeration cycle apparatuses, such as an air conditioner, for example. As shown in FIG. 1, the refrigeration cycle apparatus includes a compressor 31 that compresses a refrigerant, a condenser 1a that condenses the refrigerant compressed by the compressor 31 (* in the case of cooling operation), and a condenser 1a that condenses the refrigerant. Decompression means 33, 36 for decompressing the refrigerant, evaporator 1b (for cooling operation) for evaporating the refrigerant decompressed by the decompression means 33, 36, and air blowing means 51 for blowing air to the evaporator 1b And.

  And as shown in FIG. 3, the evaporator 1b (heat exchanger 1) is arrange | positioned below the 1st pipe (header pipe 10) which flows a refrigerant | coolant inside, and a 1st pipe (header pipe 10). A heat transfer pipe (flat heat transfer pipe 12) connecting the second pipe (header pipe 11) through which the refrigerant flows, the first pipe (header pipe 10) and the second pipe (header pipe 11); A plurality of refrigerant channels 15 are formed inside the heat transfer tube (flat heat transfer tube 12). And the refrigerant | coolant from a 1st pipe (header pipe 10) flows in from each inflow part of the some refrigerant | coolant flow path 15, and flows into each 2nd pipe | tube (header pipe 11) after flowing through each refrigerant | coolant flow path 15. Flowing. Furthermore, as shown in FIG. 4, the height position of each inflow portion of the plurality of refrigerant flow paths 15 moves in the direction from the blowing means to the evaporator, that is, in the direction of air flow (on the downstream side of the passing air). It is configured to be higher (as you go to).

  Thus, by changing the height position of the inflow part of the refrigerant flow path 15, in the state where the temperature of the air is high, that is, in the first stage where the air flows into the heat exchanger 1 (left side of the flat surface in FIG. 3). Although the circulation amount of the two-phase refrigerant is increased, the air temperature is high, so that the liquid refrigerant can be evaporated by heat exchange and then discharged from the heat exchanger. On the other hand, in a state where the temperature of the air is low, that is, in a stage in which air flows while being heat-exchanged in the heat exchanger 1 (on the right side of the flat surface in FIG. 3), the amount of heat exchange decreases, and the refrigerant Since the circulation amount is also reduced accordingly, the liquid refrigerant can be evaporated and flowed out of the heat exchanger 1 even if the air temperature is low. In addition, the variation in the dryness of the refrigerant flowing into the flat heat transfer tube 12 is also reduced on the inflow side (refrigerant connection tube 101 side) of the header pipe 10 that is easily affected by the gas-liquid two-phase flow pattern. Therefore, it is possible to optimize the refrigerant distribution of the entire heat exchanger 1.

  Therefore, according to the present embodiment, a large amount of liquid refrigerant flows out of the heat exchanger 1 without evaporating in the evaporator, and is then sent to the compressor, causing so-called liquid compression and causing a compressor failure. Thus, a highly reliable refrigeration cycle apparatus can be provided. Moreover, the refrigerant | coolant exit state for every refrigerant path of a heat exchanger tube can be equalize | homogenized, and a highly efficient refrigerating-cycle apparatus can be provided.

  As shown in FIGS. 2 to 4, in the refrigeration cycle apparatus, the flat heat transfer tube 12 has a flat shape and has a flat surface in substantially the same direction as the direction from the blowing means 51 to the evaporator 1 b. It is desirable. The evaporator 1b preferably includes a plurality of flat heat transfer tubes 12 substantially in parallel. With such a configuration, it is possible to provide a highly reliable refrigeration cycle apparatus as described above.

  Example 2 will be described below. The heat exchanger 1 of the present embodiment is also employed in a refrigeration cycle apparatus using a refrigeration cycle such as an air conditioner as in the first embodiment. When performing the cooling operation in FIG. 1, the evaporator 1b It acts as.

  When the two-phase refrigerant flows through the flat heat transfer tube 12, the flow rate of the refrigerant flow path 15 of the flat heat transfer tube 12 through which a large amount of gas refrigerant flows increases, the pressure loss increases, the refrigerant flow rate decreases, and the refrigerant latent heat also decreases. This reduces the heat exchange capacity. On the other hand, the flat heat transfer tube 12 through which a large amount of liquid refrigerant flows increases the refrigerant flow rate, and the heat exchange capacity does not decrease. In this way, when refrigerants having different liquid gas ratios are respectively supplied to the flat heat transfer tubes, the heat exchange amount is unbalanced and the ability as a heat exchanger is reduced.

  In other words, when the positions of the inlets (inflow portions) of the plurality of refrigerant flow paths 15 are horizontal and low, a large amount of liquid refrigerant flows in the flat heat transfer tube close to the refrigerant connection tube 101, and gas flows in the distant flat heat transfer tubes. A lot of refrigerant flows. In the flat heat transfer tube 12 through which a large amount of gas refrigerant flows, the flow rate of the refrigerant flow path 15 increases, the pressure loss increases, the refrigerant flow rate decreases, and the refrigerant latent heat also decreases, so the heat exchange capacity decreases. On the other hand, the flat heat transfer tube 12 through which a large amount of liquid refrigerant flows increases the refrigerant flow rate, and the heat exchange capacity does not decrease. In this way, when refrigerants having different liquid gas ratios are respectively supplied to the flat heat transfer tubes, the heat exchange amount is unbalanced and the ability as a heat exchanger is reduced.

  More specifically, in the case of a two-phase refrigerant, as shown in FIG. 3, a large amount of liquid refrigerant flows on the lower side of the header pipe and a large amount of gas refrigerant flows on the upper side. Although details are not shown in FIG. 2, when two-phase refrigerant flows from the refrigerant connection pipe 101 to the header pipe 10 when the height positions of the plurality of flat heat transfer pipes 12 are the same, the inlet side (refrigerant connection) The liquid refrigerant flows through the flat heat transfer tube 12 on the tube 101 side), and the gas refrigerant flows through the flat heat transfer tube 12 as it travels through the header pipe 10 (on the side opposite to the refrigerant connection tube 101). That is, when the height positions of the inflow portions of the plurality of flat heat transfer tubes 12 into which the refrigerant from the header pipe 10 flows are the same, a large amount of liquid refrigerant flows through the flat heat transfer tubes 12 on the inlet side (refrigerant connection tube 101 side). Therefore, the flat heat transfer tube 12 does not completely evaporate and flows to the header pipe 11. Since the refrigerant flowing out of the heat exchanger in such a state cannot sufficiently exhibit the heat exchanging ability, the heat exchange amount is reduced, and the efficiency as the refrigeration cycle apparatus is reduced. Further, if the refrigerant pipe contains a large amount of liquid refrigerant and flows from the header pipe 11 to the refrigerant connection pipe 102, and this refrigerant flows to the compressor 31 in FIG. 1, the refrigeration oil of the compressor is diluted with the liquid refrigerant. In some cases, the lubricating action of the refrigerator is reduced and the compressor is worn. When the state is bad, so-called liquid compression is caused, which may cause a compressor failure.

  Therefore, in the present embodiment, although details are not shown, in FIG. 2, the refrigerant in the header pipe 10 flows through the height positions of the inflow portions of the plurality of flat heat transfer tubes 12 into which the refrigerant from the header pipe 10 flows. It is configured to become lower in the direction. That is, the height position of the inflow portion of the flat heat transfer tube 12 is lowered from the inlet side of the two-phase refrigerant (the refrigerant connection tube 101 side) toward the right side of FIG. As shown in FIG. 4, when a plurality of refrigerant flow paths 15 are formed in the flat heat transfer tube 12, the average value of the height positions of the plurality of inflow portions (upper portions of the refrigerant flow paths 15) is the header pipe 10. What is necessary is just to comprise so that it may become low toward the direction where the refrigerant | coolant flows.

  With this configuration, the liquid refrigerant flows in the same manner in the flat heat transfer tube 12 on the side opposite to the refrigerant connection tube 101 with respect to the flat heat transfer tube 12 on the inlet side (refrigerant connection tube 101 side). The deterioration of the heat transfer performance of the heat exchanger can be suppressed. Further, it is possible to prevent a large amount of liquid refrigerant from flowing through some of the flat heat transfer tubes 12 as described above, and to allow the two-phase refrigerant to flow through the flat heat transfer tubes 12 on average. Therefore, since the efficiency reduction of the heat exchanger as described above is prevented and liquid compression of the compressor 31 is prevented, the reliability of the refrigeration cycle apparatus can be improved.

  As described above, the refrigeration cycle apparatus of the present embodiment includes the compressor 31 that compresses the refrigerant, the condenser 1a that condenses the refrigerant compressed by the compressor 31 (in the case of the cooling operation), and the condenser 1a. Pressure reducing means 33, 36 for reducing the pressure of the refrigerant condensed by the pressure reducing means 33, and an evaporator 1b (in the case of cooling operation) for evaporating the pressure reduced by the pressure reducing means 33, 36. And the evaporator 1b is arrange | positioned below the 1st pipe (header pipe 10) which flows a refrigerant | coolant inside, and a 1st pipe (header pipe 10), and the 2nd pipe (header) which flows a refrigerant | coolant inside The pipe 11), the first pipe (header pipe 10) and the second pipe (header pipe 11) are connected, and the first pipe (header pipe 10) is formed by a plurality of refrigerant flow paths 15 formed inside. A plurality of heat transfer tubes (flat heat transfer tubes 12) that flow the refrigerant from the first to the second pipe (header pipe 11), and a plurality of refrigerant flow paths formed in each of the plurality of heat transfer tubes (flat heat transfer tubes 12) 15, the average value of the height position of the inflow portion into which the refrigerant from the first pipe (header pipe 10) flows becomes lower in the direction in which the refrigerant flows in the first pipe (header pipe 10). Is composed

  The upper end of the flat heat transfer tube 12 is inclined with respect to the horizontal, and the inlet positions of the plurality of refrigerant flow paths 15 are respectively changed with respect to the horizontal. As a result, a large amount of liquid refrigerant flows through the refrigerant flow path 15 at a position where the inlet of the refrigerant flow path 15 is low, and a large amount of gas refrigerant flows through the refrigerant flow path 15 at a high position. In this way, by changing the inlet positions of the plurality of refrigerant flow paths 15 with respect to the horizontal, the liquid gas ratio can be evenly distributed to each flat heat transfer tube 12, and the entire heat exchanger can be used effectively. it can. Therefore, according to the present embodiment, it is possible to provide a refrigeration cycle apparatus with high reliability and high efficiency as described above.

  Hereinafter, Example 3 will be described with reference to FIGS. 5 and 6. The heat exchanger 1 of the present embodiment is also employed in a refrigeration cycle apparatus using a refrigeration cycle such as an air conditioner as in the first and second embodiments. When performing a cooling operation in FIG. Acting as a vessel 1b.

  The flat heat transfer tube 13 provided in the heat exchanger 1 of the present embodiment is obtained by changing the position of the refrigerant flow path 15 with respect to the horizontal with the upper and lower ends being V-shaped. That is, each upper end part of the some flat heat exchanger tube 13 with which the heat exchanger 1 is provided is made into the shape dented to the lower header pipe 11 side in FIG. By thus forming the upper end portion in a V shape, the occupied area in the header pipe 10 at the upper end portion of the flat heat transfer tube 13 is reduced, and the flow path resistance in the header pipe 10 is reduced. Thereby, the pressure drop on the downstream side in the header pipe 10 is reduced, and the refrigerant distribution to the flat heat transfer tubes 13 is further uniformized.

  In addition, the above-described configuration of the present embodiment is adopted in combination with the configuration of the heat exchanger 1 described in the first and second embodiments, so that the effect of the configuration of the first and second embodiments (improved reliability of the refrigeration cycle apparatus). In addition, it is possible to improve the efficiency of the refrigeration cycle by reducing the pressure drop described above.

  A fourth embodiment of the present invention will be described with reference to FIGS. The heat exchanger 2 of the present embodiment is also employed in a refrigeration cycle apparatus using a refrigeration cycle such as an air conditioner as in the first and second embodiments. When performing a cooling operation in FIG. Acting as a vessel 1b.

  The heat exchanger 2 of the present embodiment is configured by configuring the flat heat transfer tube 12 described in the first embodiment with a pipe group 22. Therefore, the operation is the same as in the first embodiment, and a large amount of liquid refrigerant flows out of the heat exchanger 1 without evaporating in the evaporator, and then sent to the compressor to cause the so-called liquid compression and the failure of the compressor. It is possible to prevent a situation that can be a cause and to provide a highly reliable refrigeration cycle apparatus. Moreover, the refrigerant | coolant exit state for every refrigerant path of a heat exchanger tube can be equalize | homogenized, and there exists an effect that a highly efficient refrigerating-cycle apparatus can be provided.

  According to the present embodiment, the pipe group 22 is formed by arranging the heat transfer tubes 24 in approximately one row as shown in FIGS. The heat transfer tubes 24 are vertically displaced so that the tube end positions of the pipe group 22 are inclined. That is, the refrigeration cycle apparatus of the present embodiment is arranged below the first pipe (header pipe 20) for flowing the refrigerant inside and the second pipe (header pipe 20) for flowing the refrigerant inside. Pipe (header pipe 21), and a plurality of heat transfer tubes 24 connecting the first pipe (header pipe 20) and the second pipe (header pipe 21). In the plurality of heat transfer tubes 24, the refrigerant from the first pipe (header pipe 20) flows in from the respective inflow portions (the upper portion of 24), flows through the respective refrigerant flow paths, and then passes through the second pipe (header). It is arranged to flow through the pipe 21). And the height position of each inflow part of the some heat exchanger tube 24 is comprised so that it may become high as it goes to the direction (arrow direction of FIG. 7) from a ventilation means to an evaporator.

  Thus, by comprising the flat heat exchanger tube 12 with the pipe group 22, in addition to the effect acquired by the structure of Example 1, an unevenness | corrugation is formed in the air side surface, a heat transfer area increases, and the air side heat transfer performance Can be improved and the amount of heat exchange can be increased. In addition, it is also possible to employ | adopt the structure of Example 2 further to a present Example.

  A fifth embodiment of the present invention will be further described with reference to FIGS. The heat exchanger 2 of the present embodiment is also employed in a refrigeration cycle apparatus using a refrigeration cycle such as an air conditioner as in the other embodiments. When performing a cooling operation in FIG. It acts as 1b.

  The heat exchanger of the present embodiment is configured such that the flat heat transfer tube 13 is configured by a pipe group 23 with respect to the flat heat transfer tube 13 of FIGS. 5 and 6 described in the third embodiment. As shown in FIG. 11, the pipe group 23 is configured by arranging the heat transfer tubes 24 in approximately one row. The heat transfer tubes 24 are shifted up and down so that the tube end positions of the pipe group 23 are V-shaped. The basic functions and effects are the same as those described in the third embodiment. However, by forming the flat heat transfer tube 13 with the pipe group 23, unevenness is formed on the air-side surface and the heat transfer area is increased. The heat transfer performance on the side is improved, and the amount of heat exchange can be increased.

1, 2 Heat exchanger 10, 11, 20, 21 Header pipe 12, 13 Flat heat transfer tube 15 Refrigerant flow path 22, 23 Pipe group 24 Heat transfer tube 31 Compressor 101, 102, 201, 202 Refrigerant connection tube

Claims (6)

A compressor for compressing the refrigerant;
A condenser for condensing the refrigerant compressed by the compressor;
Decompression means for decompressing the refrigerant condensed by the condenser;
An evaporator for evaporating the refrigerant decompressed by the decompression means;
In a refrigeration cycle apparatus comprising a blowing means for blowing air to the evaporator,
The evaporator is
A first pipe for flowing a refrigerant in a direction perpendicular to the direction from the blowing means to the evaporator ;
A second pipe that is disposed below the first pipe and allows the refrigerant to flow in a direction perpendicular to the direction from the blowing means to the evaporator ;
A plurality of heat transfer tubes that connect the first pipe and the second pipe and that are arranged in a direction perpendicular to the direction from the blowing means to the evaporator ;
Inside the heat transfer tube, a plurality of refrigerant flow paths are formed in the direction from the blowing means to the evaporator ,
The refrigerant from the first pipe flows in from the inflow portions of the plurality of refrigerant flow paths, flows through the respective refrigerant flow paths, and then flows to the second pipe.
The height position of each inflow portion of the plurality of refrigerant flow paths is configured to become higher as it goes from the blowing means to the evaporator ,
The height position of the inflow portions of the plurality of heat transfer tubes into which the refrigerant from the first pipe flows is configured to become lower in the direction in which the refrigerant of the first pipe flows. A refrigeration cycle apparatus characterized by. The refrigeration cycle apparatus of claim 1,
The heat transfer tube has a flat shape and has a flat surface in substantially the same direction as the direction from the blower to the evaporator. In the refrigeration cycle apparatus according to claim 1 or 2,
The refrigeration cycle apparatus characterized in that an upper end portion of the heat transfer tube has a shape recessed toward the second pipe. In the refrigerating cycle device according to any one of claims 1 to 3 ,
The evaporator is
A refrigeration cycle apparatus comprising a plurality of the heat transfer tubes substantially in parallel. In the refrigerating cycle device according to any one of claims 1 to 4 ,
The plurality of heat transfer tubes are:
A refrigeration cycle apparatus configured such that an average value of height positions of inflow portions of a plurality of refrigerant flow paths formed in each of the refrigerant flow paths becomes lower in a direction in which the refrigerant of the first pipe flows. .   The refrigeration cycle apparatus according to any one of claims 1 to 5,
  A cycle apparatus characterized in that a liquid drain hole is not provided in a tube wall inserted into the first pipe of the heat transfer tube.