JP6188951B2 - Refrigerant distributor, heat exchanger and refrigeration cycle apparatus - Google Patents

Description

  The present invention relates to a refrigerant distributor, a heat exchanger, and a refrigeration cycle apparatus having a first cylinder portion in which refrigerant flows upward and a second cylinder portion in which refrigerant flows downward.

  Conventionally, a refrigerant distributor connected to a heat exchanger provided with a plurality of heat transfer tubes along the direction of gravity is known (see, for example, Patent Document 1). In the refrigerant distributor of Patent Document 1, the refrigerant supply pipe is inserted into the header pipe, and the discharge port formed at the tip of the refrigerant supply pipe faces the refrigerant collision surface formed at the end of the header pipe. Are arranged. In the refrigerant distributor described in Patent Document 1, the refrigerant discharged from the discharge port of the refrigerant supply pipe is caused to collide with the refrigerant collision surface to mix the gas phase refrigerant and the liquid phase refrigerant.

JP 2013-002773 A

  However, in the refrigerant distributor described in Patent Document 1, it is not possible to adjust the flow rate of the liquid-phase refrigerant flowing through the plurality of heat transfer tubes provided at different heights.

  The present invention has been made against the background of the above problems, and a refrigerant distributor, a heat exchanger, and a refrigeration cycle capable of adjusting the flow rate of refrigerant flowing through a plurality of heat transfer tubes provided at different heights. The object is to provide a device.

  A refrigerant distributor according to the present invention is a refrigerant distributor that constitutes a part of a heat exchanger including a plurality of heat transfer tubes arranged in parallel at different heights, and is connected to the plurality of heat transfer tubes, with the refrigerant facing upward A first cylindrical portion that flows through the first cylindrical portion, and a second cylindrical portion that is connected to the first cylindrical portion and flows downward from the first cylindrical portion, and includes a plurality of first cylindrical portions and second cylindrical portions. The heat transfer tubes are connected to heat transfer tubes of different heights.

  A heat exchanger according to the present invention includes a refrigerant distributor, a first heat exchange part including a heat transfer pipe connected to the first cylinder part, and a heat transfer pipe connected to a second cylinder part. 2 heat exchange parts.

  Moreover, the refrigeration cycle apparatus according to the present invention is a refrigeration cycle apparatus including the heat exchanger described above, and when the heat exchanger acts as an evaporator, the refrigerant is changed from the first cylinder part to the second cylinder part. The thing that flows into.

  According to the present invention, it is possible to provide a refrigerant distributor, a heat exchanger, and a refrigeration cycle apparatus that can adjust the flow rate of the refrigerant flowing through a plurality of heat transfer tubes provided at different heights.

It is the refrigerant circuit figure which described schematically an example of the refrigerant circuit structure of the refrigerating-cycle apparatus which concerns on Embodiment 1 of this invention. FIG. 2 is a perspective perspective view schematically illustrating a heat source side unit of FIG. 1. It is a schematic diagram which shows an example of the heat source side heat exchanger of FIG. FIG. 2 is a PH diagram illustrating a refrigeration cycle when the refrigerant is a hydrofluorocarbon refrigerant R410a in the refrigeration cycle apparatus of FIG. 2 is a graph showing the relationship between the height position of the refrigerant distributor and the amount of deviation of the liquid refrigerant flow rate for the refrigerant distributor shown in FIG. 1. It is a schematic diagram of the comparative example of the refrigerant distributor which concerns on Embodiment 1 of this invention. It is a graph which shows the relationship between the height position of a refrigerant distributor, and the deviation | shift amount of a liquid refrigerant flow volume about the refrigerant distributor which concerns on the comparative example of FIG. It is the perspective perspective view which described roughly the heat-source side unit which concerns on Embodiment 2 of this invention. It is a front schematic diagram which shows an example of the heat source side heat exchanger of FIG. It is a back surface schematic diagram of the heat source side heat exchanger of FIG. It is sectional drawing which described schematically the cross section of the heat source side heat exchanger of FIG. 9 and FIG. It is the refrigerant circuit figure which described schematically an example of the refrigerant circuit structure of the refrigerating-cycle apparatus which concerns on Embodiment 3 of this invention. It is the perspective view which described the utilization side unit of FIG. 12 roughly. It is a perspective view which shows the state which removed the cover from the utilization side unit of FIG. It is the refrigerant circuit figure which described schematically an example of the refrigerant circuit structure of the refrigerating-cycle apparatus which concerns on Embodiment 4 of this invention. FIG. 16 is a perspective perspective view schematically illustrating the heat source side unit of FIG. 15. FIG. 17 is a graph showing the relationship between the height position of a heat transfer tube and the amount of air passing through the heat source side heat exchanger in the heat source side heat exchanger described in FIG. 16. FIG. 17 is a graph showing the relationship between the height position of the heat transfer tube and the refrigerant flow rate through which the liquid refrigerant flows in the heat source side heat exchanger shown in FIG. 16. It is the refrigerant circuit figure which described schematically an example of the refrigerant circuit structure of the refrigerating-cycle apparatus which concerns on Embodiment 5 of this invention. FIG. 20 is a perspective perspective view schematically illustrating the heat source side unit of FIG. 19. 20 is a graph showing the relationship between the height position of the heat transfer tube and the refrigerant flow rate through which the liquid refrigerant flows in the heat source side heat exchanger shown in FIG.

  Embodiments of the present invention will be described below with reference to the drawings. In the drawings, the same or corresponding parts are denoted by the same reference numerals, and the description thereof is omitted or simplified as appropriate. Moreover, the shape, size, arrangement, and the like of the configurations described in the drawings can be changed as appropriate within the scope of the present invention.

Embodiment 1 FIG.
1 is a refrigerant circuit diagram schematically illustrating an example of a refrigerant circuit configuration of a refrigeration cycle apparatus according to Embodiment 1 of the present invention, and FIG. 2 schematically illustrates a heat source side unit of FIG. It is a perspective perspective view. The refrigeration cycle apparatus 1 according to this embodiment is an air conditioner that performs air conditioning in a room that is an air conditioning target, for example, and includes a heat source side unit 1A and a use side unit 1B.

  The heat source side unit 1A constitutes a refrigeration cycle that circulates the refrigerant together with the use side unit 1B, thereby waste heat or supplying heat of the air conditioning. The heat source unit 1A is installed outdoors, for example. The heat source side unit 1A has a housing 20, and houses the compressor 10, the flow path switch 60, the heat source side heat exchanger 40, the blower unit 30, the expansion device 50, the accumulator 70, and the like in the housing 20. doing.

  The use side unit 1 </ b> B is installed in a room or the like to be air-conditioned and includes a use side heat exchanger 80. The refrigeration cycle apparatus 1 includes the compressor 10, the flow path switch 60, the use side heat exchanger 80, the expansion device 50, the heat source side auxiliary heat exchange unit 40B, the capillary tube 33, the refrigerant distributor 100, and the heat source side main heat. It has a refrigeration cycle composed of an exchange unit 40A, a merging pipe 200, and an accumulator 70.

  The compressor 10 compresses the sucked refrigerant to a high temperature and high pressure state, and is composed of, for example, a scroll compressor, a reciprocating compressor, a vane compressor, or the like. The flow path switching device 60 performs switching between the heating flow path and the cooling flow path according to switching of the operation mode of the cooling operation or the heating operation, and is configured by, for example, a four-way valve. The flow path switch 60 connects the discharge side of the compressor 10 and the use side heat exchanger 80 and connects the heat source side heat exchanger 40 and the accumulator 70 during the heating operation. On the other hand, the flow path switch 60 connects the discharge side of the compressor 10 and the heat source side heat exchanger 40 and also connects the use side heat exchanger 80 and the accumulator 70 during the cooling operation. In addition, although the case where a four-way valve is used as the flow path switching device 60 is illustrated, the present invention is not limited to this, and for example, a plurality of two-way valves may be combined.

  The heat source side heat exchanger 40 performs heat exchange between the refrigerant and the outside air, and has, for example, a shape bent in an L shape on the front left side of the housing 20. The heat source side heat exchanger 40 includes a heat source side main heat exchange unit 40A and a heat source side sub heat exchange unit 40B. The heat source side main heat exchanging part 40A is arranged on the upper side in the direction of gravity, and the heat source side sub heat exchanging part 40B is arranged below the heat source side main heat exchanging part 40A. The heat source side main heat exchange part 40A and the heat source side sub heat exchange part 40B are integrally formed, and are provided in different regions of the common heat transfer fin 40D.

  FIG. 3 is a schematic diagram illustrating an example of the heat source side heat exchanger of FIG. 2. The heat source side heat exchanger 40 is configured by inserting a large number of heat transfer fins 40D at intervals of 1 mm, for example, into a plurality of heat transfer tubes 40C. The heat source side heat exchanger 40 has a plurality of heat transfer tubes 40C arranged in parallel at different heights. During operation, air is blown from the direction along the gap between the plurality of heat transfer fins 40 </ b> D as indicated by arrow A, and the refrigerant flows in the axial direction of the heat transfer tube 40 </ b> C as indicated by arrow B. Thereby, heat exchange between the refrigerant and air is performed, and waste heat and heat supply are realized. The heat source side main heat exchanging part 40A and the heat source side sub heat exchanging part 40B are integrally provided on the same heat transfer fin 40D, and the heat transfer tube 40C includes the heat source side main heat exchanging part 40A and the heat source side sub heat exchanging part. The heat exchange unit 40B is independent of each other.

  As shown in FIG. 1, the heat-source-side main heat exchange unit 40 </ b> A is connected to the junction pipe 200 and the refrigerant distributor 100. The junction pipe 200 serves as a refrigerant outlet when the heat source side main heat exchange unit 40A functions as an evaporator (at the time of heating operation), and is connected to the flow path switch 60. The refrigerant distributor 100 serves as a refrigerant inlet when the heat source side main heat exchange unit 40A functions as an evaporator (at the time of heating operation). During the heating operation, the refrigerant flowing into the refrigerant distributor 100 is distributed to the heat transfer tubes 40C of the heat source side main heat exchange unit 40A and flows out from the junction tube 200.

  The expansion device 50 is connected to one of the heat source side auxiliary heat exchanging units 40B, and the refrigerant distributor 100 is connected to the other via a capillary tube 33. During the heating operation, the refrigerant flows from the expansion device 50 into the heat source side auxiliary heat exchange unit 40B and flows out to the refrigerant distributor 100 side.

  The refrigerant distributor 100 is a header-type distributor having a first cylinder part 100A and a second cylinder part 100B. Each of the first tube portion 100A and the second tube portion 100B is a header-type distribution pipe and extends vertically in the direction of gravity. Each of the first cylinder part 100A and the second cylinder part 100B has a branch pipe connected from the header and the header to each heat transfer pipe 40C of the heat source side main heat exchange part 40A. The upper part of the first cylinder part 100A and the upper part of the second cylinder part 100B are connected, and during the heating operation, the refrigerant flowing into the refrigerant distributor 100 flows upward in the first cylinder part 100A, and then Then, while flowing downward in the second cylindrical portion 100B, the heat is transferred to each heat transfer tube 40C. The first tube portion 100A and the second tube portion 100B may be configured by separate members and connected by refrigerant piping, or the first tube portion 100A and the second tube portion 100B may be bent into one member. It may be formed by processing or the like.

  The first cylinder part 100A and the second cylinder part 100B are connected to the heat transfer tube 40C of the heat source side main heat exchange part 40A at different positions in the direction of gravity. That is, the first cylinder portion 100A is connected to the upper heat transfer tube 40C in the gravity direction, and the second cylinder portion 100B is connected to the lower heat transfer tube 40C in the gravity direction. Preferably, the first tube portion 100A is connected to the second tube portion 100B above the heat transfer tube 40C connected to the first tube portion 100A, and the second tube portion 100B is connected to the second tube portion 100B. Above the heat transfer tube 40C connected to the cylinder part 100B, it is connected to the first cylinder part 100A.

  The lower part of the second cylinder part 100B is bypassed by the lower part of the first cylinder part 100A and the bypass path 100C. Preferably, the lower end of the second cylinder portion 100B is connected to the bypass path 100C. The bypass passage 100C allows a fluid such as a refrigerant to pass at least during a cooling operation in which the refrigerant flows in a direction opposite to that during the heating operation (when the heat source side heat exchanger 40 operates as a condenser). In the bypass passage 100C, for example, a switching unit 100D configured by a check valve may be installed. When the heat source side heat exchanger 40 operates as a condenser, the switching unit 100D switches the flow path so that a fluid such as a refrigerant passes through the bypass path.

  The blower unit 30 blows air to the heat source side heat exchanger 40 and is provided to face the heat source side heat exchanger 40. The air blowing unit 30 in FIG. 2 is compatible with the compressor 10, the accumulator 70 (not shown), and the flow path switch 60 in the housing 20. For example, the 1st ventilation unit 30A is arranged at the upper part of case 20 so as to oppose heat source side main heat exchange part 40A, and the 2nd ventilation unit 30B is heat source side sub heat exchange part 40B and heat source side main heat exchange. It arrange | positions at the lower part of the housing | casing 20 so that the part 40A may be opposed.

  The expansion device 50 is provided between the use side heat exchanger 80 and the heat source side sub heat exchange unit 40B, and adjusts the temperature of the refrigerant by adjusting the flow rate. The throttle device 50 includes, for example, a throttle device typified by LEV (linear electronic expansion valve) or the like, or an open / close valve that turns the refrigerant flow on and off by opening and closing. The accumulator 70 is provided on the suction side of the compressor 10 and stores the refrigerant. The compressor 10 sucks and compresses the gas refrigerant among the refrigerant stored in the accumulator 70.

  Next, with reference to FIG. 1, an operation example of the refrigeration cycle apparatus 1 when the heat source side heat exchanger 40 operates as an evaporator (heating operation) will be described. First, the refrigerant becomes a gas refrigerant compressed in the compressor 10 and flows from the compressor 10 to the use side heat exchanger 80 via the flow path switch 60. Thereafter, the gas refrigerant dissipates heat in the use side heat exchanger 80 and condenses from gas to liquid, and the condensed refrigerant is decompressed in the expansion device 50 to be in a gas-liquid two-phase state. Then, the gas-liquid two-phase refrigerant flows into the heat source side auxiliary heat exchanging unit 40B, and the liquid evaporates by absorbing heat from the air by the ventilation of the second blower unit 30B, and the ratio of the gas in the gas-liquid two-phase state Rises. Thereafter, the gas-liquid two-phase refrigerant is decompressed by the capillary tube 33 and then flows into the refrigerant distributor 100. In the refrigerant distributor 100, the refrigerant in the gas-liquid two-phase state is distributed to the plurality of heat transfer tubes 40C of the heat source side main heat exchanging section 40A, and absorbs heat from the air by the blowing of the first blowing unit 30A and the second blowing unit 30B. Thus, the gas-liquid two-phase state becomes the gas phase and flows to the accumulator 70 through the flow path switch 60. Thereafter, the gas-phase refrigerant in the accumulator 70 is sucked into the compressor 10.

  FIG. 4 is a PH diagram illustrating the refrigeration cycle when the refrigerant is the hydrofluorocarbon refrigerant R410a in the refrigeration cycle apparatus 1 of FIG. In addition, in FIG. 4, the case where the heat source side heat exchanger 40 operates as an evaporator (heating operation) will be described. In FIG. 4, the substantially trapezoidal solid line indicates the operating state of the refrigeration cycle, and the line from X = 0.1 to X = 0.9 extending from the horizontal enthalpy axis indicates the ratio of the refrigerant gas phase. The convex solid line is a saturation line, the region on the right side of the saturation line is gas, and the region on the left side is liquid.

  The refrigeration cycle during the heating operation described above is operated from point AB to point AC, point AD, point AE, point AF, and point AA. Point AB is a superheated gas at the discharge part of the compressor 10. The refrigerant dissipates heat in the use side heat exchanger 80, and becomes a supercooled liquid at the point AC at the outlet of the use side heat exchanger 80. Thereafter, the refrigerant is depressurized by passing through the expansion device 50 and becomes a gas-liquid two-phase state with a dryness of about 0.05 at the point AD. This gas-liquid two-phase refrigerant partially absorbs and evaporates in the heat source side auxiliary heat exchanging section 40B, thereby increasing the dryness X and decreasing the pressure to the point AE, and further reducing the pressure in the capillary tube 33. It becomes a gas-liquid two-phase state with an AF dryness of about 0.20 and flows into the refrigerant distributor 100. The refrigerant distributed by the refrigerant distributor 100 flows into the heat source side main heat exchanging part 40 </ b> A and is absorbed and evaporated to change into a superheated gas at the point AA, and is sucked into the compressor 10 via the accumulator 70.

  As described above, when the heat source side heat exchanger 40 operates as an evaporator, the refrigerant in the gas-liquid two-phase state flows into the refrigerant distributor 100. In the refrigerant distributor 100, the gas-liquid two-phase refrigerant is a mixture of gas-phase refrigerant and liquid-phase refrigerant with different densities, and each phase has a balance between kinetic energy depending on flow velocity and potential energy determined by gravity. Flow while maintaining. At this time, in order to increase the heat exchange efficiency of the heat source side heat exchanger 40, it may be desirable that the liquid-phase refrigerant having a low enthalpy is evenly distributed from the refrigerant distributor 100 to each heat transfer tube 40C. . However, for example, when the refrigerant circulation amount is small when the refrigeration cycle apparatus 1 is operating at a low load, the liquid-phase refrigerant is unevenly distributed depending on the height position depending on the dryness of the refrigerant. There is. This is because the momentum of the refrigerant tends to be small and the proportion of the gas-phase refrigerant tends to increase on the upper side in the gravity direction of the refrigerant distributor. Therefore, the refrigerant distributor 100 according to this embodiment is connected to the first cylinder part 100A in which the refrigerant flows upward and the first cylinder part 100A, and the refrigerant that has flowed out of the first cylinder part 100A flows downward. The first cylindrical portion 100A is connected to the upper heat transfer tube in the gravity direction among the plurality of heat transfer tubes 40C, and the second cylindrical portion 100B is connected to the plurality of heat transfer tubes 40C. It is connected to the lower heat transfer tube.

  FIG. 5 is a graph showing the relationship between the height position of the refrigerant distributor and the amount of deviation of the liquid refrigerant flow rate in the refrigerant distributor shown in FIG. FIG. 5 illustrates a case where the dryness of the refrigerant flowing into the inlet of the refrigerant distributor 100 is X = 0.20. As shown in FIG. 5, the refrigerant distributor 100 according to this embodiment can evenly distribute the liquid-phase refrigerant to the heat source side main heat exchanging section 40A on the upper side and the lower side in the direction of gravity. This is because the first cylinder portion 100A of the refrigerant distributor 100 is on the refrigerant inflow side and has a large momentum of the refrigerant, so that the liquid phase refrigerant can be introduced to the upper end portion even in an upward flow that opposes gravity. Moreover, in the 2nd cylinder part 100B, the liquid phase refrigerant | coolant which flowed in from the 1st cylinder part 100A flows in the direction where gravity acts. As a result, in this embodiment, the liquid phase refrigerant can reach the upper part of the refrigerant distributor 100, and the liquid phase refrigerant can be evenly distributed to the plurality of heat transfer tubes 40C arranged in parallel at different heights in the direction of gravity. Therefore, the liquid-phase refrigerant can be evenly distributed to the heat source side main heat exchange unit 40A.

  6 is a schematic diagram of a comparative example of the refrigerant distributor according to Embodiment 1 of the present invention, and FIG. 7 shows the height position of the refrigerant distributor in the refrigerant distributor according to the comparative example shown in FIG. It is a graph which shows the relationship between the amount of deviation of a liquid refrigerant flow rate. FIG. 7 illustrates a case where the dryness of the refrigerant flowing into the inlet of the refrigerant distributor 500 is X = 0.05. As shown in FIG. 6, the refrigerant distributor 500 of the comparative example has a cylindrical shape extending along the direction of gravity. In the refrigerant distributor 500 of the comparative example, the ratio of the gas-phase refrigerant increases on the upper side in the gravity direction, and the ratio of the liquid-phase refrigerant tends to increase on the lower side. For this reason, as shown in FIG. 7, in the refrigerant distributor 500 of the comparative example, the liquid-phase refrigerant flows unevenly in the lower position of the heat exchanger 510 depending on the dryness and the circulation amount of the refrigerant, and in the higher position. Liquid phase refrigerant may not flow. As described above, in the refrigerant distributor 500 of the comparative example, the liquid-phase refrigerant may be significantly unevenly distributed to the heat exchanger 510, and at this time, the heat exchange efficiency is lowered. In the above description, the case where the dryness of the refrigerant is X = 0.05 is illustrated, but when the dryness X of the refrigerant is, for example, 0.2 or less, the liquid phase refrigerant is evenly distributed from the refrigerant distributor 500. There is a tendency not to be distributed.

  As described above, in this embodiment, the refrigerant distributor 100 is connected to the first cylinder part 100A in which the refrigerant flows upward and the first cylinder part 100A, and the refrigerant that has flowed out of the first cylinder part 100A is directed downward. The first cylinder part 100A is connected to the upper side in the gravitational direction of the plurality of heat transfer tubes 40C, and the second cylinder part 100B is connected to the plurality of heat transfer tubes 40C. It is connected to the lower side. For this reason, according to this embodiment, a liquid phase refrigerant can be equally distributed to heat source side main heat exchange part 40A.

  Furthermore, according to this embodiment, when the heat source side heat exchanger 40 operates as a condenser (during the cooling operation of the refrigeration cycle apparatus 1), the compressor oil stays in the lower part of the second cylindrical portion 100B. Can be suppressed. During the cooling operation of the refrigeration cycle apparatus 1, the direction in which the refrigerant flows is reversed, and the liquid-phase or gas-liquid two-phase refrigerant flows from the heat source side main heat exchange unit 40A into the second cylinder 100B. At this time, in this embodiment, the lower part of the second cylinder part 100B is bypassed by the lower part of the first cylinder part 100A and the bypass passage 100C, and at least when the refrigerant flows back, the fluid such as the refrigerant flows. Since it is configured so that it can pass through, it is possible to suppress the compressor oil from staying in the lower portion of the second cylindrical portion 100B. Note that the switching unit 100D may be provided in the bypass passage 100C so that the refrigerant actively flows in the bypass passage 100C when the refrigerant flows backward. By configuring in this way, most of the liquid-phase or gas-liquid two-phase refrigerant that has flowed from the heat source side main heat exchange section 40A into the second cylinder section 100B flows out to the switching means 100D side where the pressure loss is small, A part flows out to the first tube portion 100A.

  This embodiment is not limited to the above description. For example, in the above description, the example in which the refrigerant distributor 100 is configured to include the two distribution pipes of the first cylinder part 100A and the second cylinder part 100B has been described. The refrigerant distributor may be configured to include a further distribution pipe in addition to the first cylinder part 100A and the second cylinder part 100B. In the case of a refrigerant distributor provided with three or more distribution pipes, the distribution pipe on the side where the momentum of the refrigerant is large may be connected to the heat transfer pipe on the upper side in the gravity direction.

Embodiment 2. FIG.
FIG. 8 is a perspective perspective view schematically showing a heat source side unit according to Embodiment 2 of the present invention. The heat source side unit 102A will be described with reference to FIG. In addition, in the heat source side unit 102A of FIG. 8, the same code | symbol is attached | subjected to the site | part which has the structure same as the heat source side unit 1A of FIG. 2, and the description is abbreviate | omitted. The heat source side unit 102A in FIG. 8 is different from the heat source side unit 1A in FIG. 1 in that the heat source side heat exchanger 41 includes a flat heat transfer tube.

  Specifically, FIG. 9 is a schematic front view showing an example of the heat source side heat exchanger of FIG. 8, FIG. 10 is a schematic back view of the heat source side heat exchanger shown in FIG. It is sectional drawing which described roughly the cross section of the heat source side heat exchanger of FIG. 9 and FIG. The heat source side heat exchanger 41 includes a heat source side main heat exchanging part 41A and a heat source side sub heat exchanging part 41B, and a plurality of heat transfer fins 41D are inserted into a plurality of flat heat transfer tubes 41C at intervals of 1 mm, for example. Yes. As shown in FIG. 10, the flat heat transfer tube 41 </ b> C according to this embodiment is bent on the back side, and one flat heat transfer tube 41 </ b> C forms two adjacent upper and lower flow paths. . The flat heat transfer tubes 41C are arranged in two rows in the left-right direction, and the upper sides of the flat heat transfer tubes 41C adjacent to the left and right are connected by a connection tube 41E on the front side as shown in FIG. Yes.

  The heat source side main heat exchanging part 41A is connected to the junction pipe 200 and the refrigerant distributor 100 on the front side. That is, on the right side of FIG. 9, the junction pipe 200 is connected to the lower side of the flat heat transfer pipe 41C to which the connection pipe 41E is not connected, and on the left side, to the lower side of the flat heat transfer pipe 41C to which the connection pipe 41E is not connected. The refrigerant distributor 100 is connected.

  As shown in FIG. 11, the flat heat transfer tube 41 </ b> C is a flat multi-hole heat transfer tube having a flat shape and having a plurality of channels formed in a substantially rectangular cross section. By using the flat heat transfer tube 41C, it is possible to form a flow channel having a cross-sectional area of less than 5 mm in diameter per flow channel, which is difficult to manufacture, in a pipe tube or the like in which a flow channel is formed one by one. In this embodiment, since the cross-sectional area of the flow path can be reduced, the refrigerant capacity can be reduced and the flow rate of the refrigerant is increased. Furthermore, in this embodiment, since the refrigerant flow rate is configured to be high, the refrigerant distributor 100 can evenly distribute the liquid-phase refrigerant to the heat source side main heat exchange unit 41A. Furthermore, in this embodiment, the refrigerant distributor 100 is connected to the lower side of the two upper and lower connection ports of the flat heat transfer tube 41C, and a refrigerant having a large momentum flows into the flat heat transfer tube 41C. Thus, the liquid-phase refrigerant can be evenly distributed to the heat source side main heat exchange section 41A.

  This embodiment is not limited to the above description. For example, in the above description, an example in which the refrigerant distributor 100 is connected to the lower side of the two upper and lower connection ports of the flat heat transfer tube 41C and the connection tube 41E is connected to the upper connection port has been described. The refrigerant distributor 100 may be connected to the upper side, and the connection pipe 41E may be connected to the lower side.

Embodiment 3 FIG.
FIG. 12 is a refrigerant circuit diagram schematically illustrating an example of the refrigerant circuit configuration of the refrigeration cycle apparatus according to Embodiment 3 of the present invention, and FIG. 13 schematically illustrates the usage-side unit of FIG. FIG. 14 is a perspective view showing a state where a cover is removed from the use side unit shown in FIG. The refrigeration cycle apparatus 301 will be described with reference to FIGS. In addition, in the refrigeration cycle apparatus 301 of FIG. 12, the same code | symbol is attached | subjected to the site | part which has the same structure as the refrigeration cycle apparatus 1 of FIG. 1, and the description is abbreviate | omitted. The refrigeration cycle apparatus 301 in FIG. 13 differs from the refrigeration cycle apparatus 1 in FIG. 1 in that the refrigerant distributor 100 is applied to the use side heat exchanger 80A of the use side unit 1B1.

  As shown in FIGS. 13 and 14, the usage-side unit 1B1 has a casing 82 having openings on the top and bottom surfaces, and in the casing 82, a usage-side heat exchanger 80A and a refrigerant distributor. 100 and the ventilation unit 39 are accommodated. A filter 84 </ b> A is installed in the opening on the top surface side of the housing 82, and a filter 84 </ b> B is installed in the opening on the bottom surface side of the housing 82.

  The use side heat exchanger 80A is connected to the junction pipe 200 and the refrigerant distributor 100. The junction pipe 200 serves as a refrigerant outlet when the use side heat exchanger 80A functions as an evaporator (during cooling operation), and is connected to the flow path switch 60. The refrigerant distributor 100 serves as a refrigerant inlet when the use side heat exchanger 80A functions as an evaporator (at the time of cooling operation), and is connected to the heat source side heat exchanger 40 via the expansion device 50. Yes.

  A blower unit 39 is installed below the use side heat exchanger 80A. Since the usage-side unit 1B1 is installed indoors, for example, the installation space is often limited. For this reason, in this embodiment, in order to obtain a desired air blowing amount, two air blowing units 39 are installed on the left and right (longitudinal direction). In addition, the structure which has the one ventilation unit 39 may be sufficient, and the structure which has the 3 or more ventilation units 39 may be sufficient.

  The blower unit 39 sucks room air from the opening on the bottom surface side of the casing 82, passes through the use side heat exchanger 80A, and generates an air flow so as to blow out from the opening on the top surface side of the casing 82. Is. At this time, the indoor air taken into the casing 82 exchanges heat with the refrigerant flowing inside the use side heat exchanger 80A (refrigerant supplied from the outside), and is cooled or heated to become conditioned air. The air is blown out from the opening on the top surface side of the casing 82. At this time, dust in the air is removed by the filter 84A, the filter 84B, a dust collection filter not shown, and the like.

Embodiment 4 FIG.
FIG. 15 is a refrigerant circuit diagram schematically illustrating an example of the refrigerant circuit configuration of the refrigeration cycle apparatus according to Embodiment 4 of the present invention, and FIG. 16 schematically illustrates the heat source side unit of FIG. It is a perspective perspective view. 15 and FIG. 16, parts having the same configurations as those in FIGS. 1 and 2 are denoted by the same reference numerals, and description thereof is omitted. In the refrigeration cycle apparatus 1-1 in FIG. 15, the capillary tube 33, the heat source side auxiliary heat exchange unit 40B, the expansion device 50, the bypass passage 100C, and the switching means 100D are omitted as compared with the refrigeration cycle apparatus 1 in FIG. Yes. In addition, in the refrigeration cycle apparatus 1-1 of FIG. 15, the heat source side heat exchanger 40 includes the first heat exchange unit 40A1 and the second heat exchange unit 40A2 as compared to the refrigeration cycle apparatus 1 of FIG. It is configured. In addition, the refrigeration cycle apparatus 1-1 in FIG. 15 includes two usage-side units 1B-1 as compared with the refrigeration cycle apparatus 1 in FIG.

  The heat source side unit 1A-1 has a housing 20A, and the compressor 10, the flow path switch 60, the heat source side heat exchanger 40-1, the blower unit 31, the accumulator 70, and the like are accommodated in the housing 20A. doing. Two use side units 1B-1 are connected in parallel to the heat source side unit 1A-1. Each of the usage side units 1B-1 includes a usage side heat exchanger 80-1 and an expansion device 81-1. In the example of FIG. 15, two use side units 1 </ b> B- 1 are connected in parallel to one heat source side unit 1 </ b> A- 1, but this embodiment is not limited to this. . That is, three or more use side units 1B-1 may be connected in parallel to one heat source side unit 1A-1, or one use side unit 1B-1 may be connected. Good. The refrigeration cycle apparatus 1-1 joins the compressor 10, the flow path switch 60, the use side heat exchanger 80-1, the expansion device 81-1, the refrigerant distributor 100, and the heat source side heat exchanger 40-1. It has a refrigeration cycle composed of a tube 200-1 and an accumulator 70.

  The heat source side heat exchanger 40-1 includes a first heat exchange unit 40A1 and a second heat exchange unit 40A2. The first heat exchanging unit 40A1 and the second heat exchanging unit 40A2 are configured as separate separate bodies. That is, the heat transfer fins of the first heat exchange unit 40A1 and the heat transfer fins of the second heat exchange unit 40A2 are configured separately. As shown in FIG. 16, the first heat exchange unit 40A1 and the second heat exchange unit 40A2 have a twice-bending shape when viewed from above. The first heat exchange unit 40A1 is installed above the second heat exchange unit 40A2.

  As shown in FIG. 15, the heat source side heat exchanger 40-1 is connected to the junction pipe 200-1 and the refrigerant distributor 100. The junction pipe 200-1 serves as a refrigerant outlet when the heat source side heat exchanger 40-1 functions as an evaporator (at the time of heating operation), and is connected to the flow path switch 60. The refrigerant distributor 100 serves as a refrigerant inlet when the heat source side heat exchanger 40-1 functions as an evaporator (during heating operation). During the heating operation, the refrigerant that has flowed into the refrigerant distributor 100 is distributed to the heat transfer tubes of the heat source side heat exchanger 40-1 and flows out from the junction tube 200-1.

  The refrigerant distributor 100 has a first cylinder part 100A and a second cylinder part 100B. The first cylinder portion 100A is connected to the first heat exchange portion 40A1 above the second heat exchange portion 40A2. The second cylinder part 100B is connected to the second heat exchange part 40A2 below the first heat exchange part 40A1. In the example of this embodiment, the first tube portion 100A is formed longer than the second tube portion 100B. The first heat exchange unit 40A1 to which the first cylinder part 100A is connected has a larger refrigerant flow rate through which the refrigerant flows than the second heat exchange part 40A2 to which the second cylinder part 100B is connected. The first cylinder part 100A is formed shorter than the second cylinder part 100B, and the flow rate of the refrigerant flowing through the first heat exchange part 40A1 is smaller than that of the second heat exchange part 40A2. It may be configured.

  The merge pipe 200-1 has a first merge pipe 200A and a second merge pipe 200B. The first joining pipe 200A is connected to the first heat exchange unit 40A1 above the second heat exchange unit 40A2. The second junction pipe 200B is connected to the second heat exchange part 40A2 below the first heat exchange part 40A1. During the heating operation, the refrigerant that has flowed out from the first merging pipe 200A and the refrigerant that has flowed out from the second merging pipe 200B merge and flow to the flow path switch 60. In the example shown in FIG. 15, the first joining pipe 200 </ b> A and the second joining pipe 200 </ b> B are configured by separate members, but the first joining pipe 200 </ b> A and the second joining pipe 200 </ b> B are integrally formed. It may be configured.

  As shown in FIG. 16, the blower unit 31 blows air to the first heat exchange unit 40A1 and the second heat exchange unit 40A2 of the heat source side heat exchanger 40-1, and is provided at the top of the housing 20A. is set up. In addition, the air blower unit 31 makes it compatible not to interfere with the compressor 10, the accumulator 70 which is not shown in figure, and the flow path switch 60 inside the housing | casing 20A. For example, the housing 20A of the example of this embodiment is configured to suck air from three directions among the side surfaces of the housing 20A and blow out air from the upper surface of the housing 20A in a substantially vertical direction. For example, the air blowing unit 31 sucks air from three directions of the side surface of the housing 20A, changes the air flow inside the housing 20A, and blows out air from the top of the housing 20A. Is generated. That is, in the example of this embodiment, the direction of the airflow passing through the first heat exchange unit 40A1 and the second heat exchange unit 40A2 is different from the direction of the airflow sucked by the blower unit 31.

  The expansion device 81-1 is provided between the use side heat exchanger 80-1 and the heat source side heat exchanger 40-1, and adjusts the state of the refrigerant by adjusting the flow rate. The expansion device 81-1 includes, for example, an expansion device represented by LEV (linear electronic expansion valve) or the like, or an open / close valve that turns the refrigerant flow on and off by opening and closing.

  Next, with reference to FIG. 15 and FIG. 16, the refrigeration cycle apparatus when the first heat exchange unit 40A1 and the second heat exchange unit 40A2 of the heat source side heat exchanger 40-1 operate as an evaporator (heating operation). An example of operation 1-1 will be described. First, the refrigerant becomes a gas refrigerant compressed in the compressor 10 and flows from the compressor 10 via the flow path switch 60 to the use side heat exchanger 80-1. Thereafter, the gas refrigerant dissipates heat in the use-side heat exchanger 80-1, condenses from gas to liquid, and the condensed refrigerant is decompressed in the expansion device 81-1, so that a gas-liquid two-phase state is obtained. Thereafter, the refrigerant in the gas-liquid two-phase state flows into the first heat exchange unit 40A1 and the second heat exchange unit 40A2 while flowing in the order of the first cylinder part 100A and the second cylinder part 100B. The refrigerant that has flowed into the first heat exchanging unit 40A1 and the second heat exchanging unit 40A2 absorbs heat from the air by the air blown by the blower unit 31, so that the gas-liquid two-phase state becomes a gas phase, and the first merge pipe 200A and the second merge It merges through the pipe 200 </ b> B and flows in the order of the flow path switch 60 and the accumulator 70. Thereafter, the gas-phase refrigerant in the accumulator 70 is sucked into the compressor 10.

  Here, when 1st heat exchange part 40A1 and 2nd heat exchange part 40A2 operate | move as an evaporator, the refrigerant | coolant of a gas-liquid two-phase state flows in into 1st cylinder part 100A and 2nd cylinder part 100B. In the gas-liquid two-phase refrigerant, the gas-phase refrigerant and the liquid-phase refrigerant are mixed in different densities, and each phase flows while maintaining a balance between the kinetic energy depending on the flow velocity and the potential energy determined by gravity. At this time, if the heat load of the first heat exchange unit 40A1 and the heat load of the second heat exchange unit 40A2 are different, the heat load of the first heat exchange unit 40A1 and the heat load of the second heat exchange unit 40A2 Accordingly, the heat exchange efficiency of the heat source side heat exchanger 40-1 can be improved by adjusting and distributing the amount of refrigerant flowing through the first heat exchange unit 40A1 and the second heat exchange unit 40A2.

  FIG. 17 is a graph showing the relationship between the height position of the heat transfer tube and the amount of air passing through the heat source side heat exchanger in the heat source side heat exchanger shown in FIG. 16, and FIG. In a heat source side heat exchanger, it is a graph which shows the relationship between the height position of a heat exchanger tube, and the refrigerant | coolant flow rate through which a liquid refrigerant flows. As shown in FIG. 16, in the heat source side unit 1 </ b> A- 1, the first heat exchange unit 40 </ b> A <b> 1 and the second heat exchange unit 40 </ b> A <b> 2 are arranged at different distances from the blower unit 31, and therefore shown in FIG. 17. Thus, the air volume of the air passing through the first heat exchange unit 40A1 and the air volume of the air passing through the second heat exchange unit 40A2 are different. Therefore, in the heat source side unit 1A-1, the heat load of the first heat exchange unit 40A1 and the heat load of the second heat exchange unit 40A2 are different. Specifically, in the example of this embodiment, the first heat exchange unit 40A1 installed above the second heat exchange unit 40A2 is closer to the blower unit 31 than the second heat exchange unit 40A2. is set up. Therefore, in the example of this embodiment, since the air volume of the air passing through the first heat exchange unit 40A1 is relatively large compared to the air volume of the air passing through the second heat exchange unit 40A2, the first heat The heat load of the exchange unit 40A1 is relatively large compared to the heat load of the second heat exchange unit 40A2.

  The heat exchange efficiency when the first heat exchange unit 40A1 and the second heat exchange unit 40A2 of the heat source side heat exchanger 40-1 function as an evaporator is important as the performance of the refrigeration cycle apparatus 1-1. The amount of refrigerant flowing through each of the first heat exchange unit 40A1 and the second heat exchange unit 40A2 is adjusted and distributed according to the ratio of the heat load of the first heat exchange unit 40A1 and the heat load of the second heat exchange unit 40A2. It is desirable to do. That is, in the example of this embodiment, since the heat load of the first heat exchange unit 40A1 is relatively large compared to the heat load of the second heat exchange unit 40A2, the first heat exchange unit 40A1 includes There is a need to allow a larger amount of liquid-phase refrigerant having larger latent heat to flow in than in the second heat exchange unit 40A2. Therefore, the refrigerant distributor 100 according to the example of this embodiment is connected to the first cylinder part 100A in which the refrigerant flows upward and the first cylinder part 100A, and the refrigerant that has flowed out of the first cylinder part 100A flows downward. The first cylinder part 100A and the second cylinder part 100B are composed of a plurality of heat transfer tubes (not shown) of the heat source side heat exchanger 40-1. It is connected to heat transfer tubes of different heights. Specifically, the first tube portion 100A is connected to the first heat exchange portion 40A1 having a large heat load, and the second tube portion 100B is connected to the second heat exchange portion 40A2 having a small heat load. According to this embodiment, since the first cylinder part 100A is connected to the first heat exchange part 40A1, as shown in FIG. 18, the flow rate of the refrigerant distributed to the first heat exchange part 40A1 is increased. be able to. This is because the first cylinder portion 100A is on the refrigerant inflow side of the refrigerant distributor 100 and therefore has a large momentum of the refrigerant. Furthermore, in the upper part of the first cylinder part 100A, the flow rate of the refrigerant distributed to the first heat exchange part 40A1 increases due to the influence of inertial force.

  As described above, according to this embodiment, when the heat source side heat exchanger 40-1 functions as an evaporator, a large amount of liquid-phase refrigerant is caused to flow into the first heat exchange unit 40A1 having a large heat load. Therefore, the heat exchange efficiency of the heat source side heat exchanger 40-1 is improved. Therefore, according to this embodiment, energy saving of the refrigeration cycle apparatus 1-1 can be achieved.

  Note that this embodiment is not limited to the above example. For example, depending on the position where the blower unit 31 is installed, or the position where the first heat exchange unit 40A1 and the second heat exchange unit 40A2 are installed, compared with the heat load of the upper first heat exchange unit 40A1, The heat load of the lower second heat exchange unit 40A2 may increase. Even in such a case, the flow rate of the refrigerant distributed to the second heat exchange unit 40A2 increases due to the influence of gravity in the lower part of the second cylindrical part 100B where the refrigerant flows downward, so the second heat exchange unit A large amount of liquid-phase refrigerant can flow into the lower part of 40A2.

  Further, for example, when the heat load of the lower second heat exchange unit 40A2 is large compared to the heat load of the upper first heat exchange unit 40A1, the lower second heat exchange unit 40A2 having a large heat load. In addition, the second cylinder part 100B may be connected to the upper first heat exchange part 40A1 to which the second cylinder part 100B is connected and the heat load is small.

  As described above, according to this embodiment, the first cylinder portion 100A in which the refrigerant flows upward and the second cylinder portion 100B in which the refrigerant flows downward are connected to the heat transfer tubes having different heights, The flow rate of the refrigerant flowing through the heat source side heat exchanger 40-1 can be adjusted. For example, the heat exchange efficiency of the heat source side heat exchanger 40-1 can be improved by adopting a configuration in which a large amount of liquid-phase refrigerant flows into the heat exchange section having a large heat load.

Embodiment 5. FIG.
19 is a refrigerant circuit diagram schematically illustrating an example of the refrigerant circuit configuration of the refrigeration cycle apparatus according to Embodiment 5 of the present invention, and FIG. 20 schematically illustrates the heat source side unit of FIG. FIG. 21 is a perspective view, and FIG. 21 is a graph showing the relationship between the height position of the heat transfer tube and the refrigerant flow rate through which the liquid refrigerant flows in the heat source side heat exchanger shown in FIG. 19 and 20, parts having the same configurations as those in FIGS. 15 and 16 are denoted by the same reference numerals, and description thereof is omitted. In the refrigeration cycle apparatus 1-2 in FIG. 19, a flow rate adjusting device 101 is provided as compared with the refrigeration cycle apparatus 1-1 in FIG. In addition, the refrigeration cycle apparatus 1-2 in FIG. 19 includes a bypass path 100C and a switching unit 100D disposed in the bypass path 100C, as compared with the refrigeration cycle apparatus 1-1 in FIG. Note that the bypass path 100C and the switching unit 100D are the same as the bypass path 100C and the switching unit 100D described in the first embodiment, and thus description thereof is omitted below.

  As shown in FIGS. 19 and 20, the refrigerant distributor 100-1 of this embodiment includes a flow rate adjusting device 101 disposed between the first cylinder portion 100A and the second cylinder portion 100B. Yes. The flow rate adjusting device 101 adjusts the flow rate of the refrigerant that flows out from the first cylindrical portion 100A and flows into the second cylindrical portion 100B. For example, the flow rate adjusting device 101 is a throttle valve that can adjust the opening degree. Capillary tubes that cannot be used may be used. According to this embodiment, when the heat source side heat exchanger 40-1 functions as an evaporator, the pressure loss from the flow control device 101 to the compressor 10 can be adjusted. The flow rate of the refrigerant flowing through the first heat exchange unit 40A1 and the flow rate of the refrigerant flowing through the second heat exchange unit 40A2 are matched to the heat load of the first heat exchange unit 40A1 and the heat load of the second heat exchange unit 40A2. Can be adjusted.

  The present invention is not limited to the above-described embodiment, and various modifications can be made within the scope of the present invention. That is, the configuration of the above embodiment may be improved as appropriate, or at least a part of the configuration may be replaced with another configuration. Furthermore, the constituent elements that are not particularly limited with respect to the arrangement are not limited to the arrangement disclosed in the embodiment, and can be arranged at positions where the functions can be achieved.

  For example, in Embodiment 1, Embodiment 2, Embodiment 4 and Embodiment 5, an example in which the refrigerant distributor 100 is connected to the heat source side heat exchanger will be described. The example in which the refrigerant distributor 100 is connected to the side heat exchanger has been described, but a configuration in which the refrigerant distributor 100 is connected to the heat source side heat exchanger and the use side heat exchanger may be employed. In the above description, at least one of the heat source side heat exchanger and the use side heat exchanger corresponds to the “heat exchanger” of the present invention.

  DESCRIPTION OF SYMBOLS 1 Refrigeration cycle apparatus, 1-1 Refrigeration cycle apparatus, 1-2 Refrigeration cycle apparatus, 1A heat source side unit, 1A-1 heat source side unit, 1B utilization side unit, 1B-1 utilization side unit, 1B1 utilization side unit, 10 compression Machine, 20 housing, 20A housing, 30 air blowing unit, 30A first air blowing unit, 30B second air blowing unit, 31 air blowing unit, 33 capillary tube, 39 air blowing unit, 40 heat source side heat exchanger, 40-1 heat source side Heat exchanger, 40A heat source side main heat exchange part, 40A1 first heat exchange part, 40A2 second heat exchange part, 40B heat source side auxiliary heat exchange part, 41B heat source side auxiliary heat exchange part, 40C heat transfer tube, 40D heat transfer fin , 41 heat source side heat exchanger, 41A heat source side main heat exchange part, 41C flat heat transfer tube, 41D heat transfer fin, 41E connecting tube 50 throttle device, 60 flow switching device, 70 accumulator, 80 utilization side heat exchanger, 80-1 utilization side heat exchanger, 80A utilization side heat exchanger, 81-1 expansion device, 82 housing, 84A filter, 84B Filter, 100 Refrigerant distributor, 100-1 Refrigerant distributor, 100A first cylinder part, 100B second cylinder part, 100C bypass path, 100D switching means, 101 flow rate adjusting device, 102A heat source side unit, 200 junction pipe, 200- DESCRIPTION OF SYMBOLS 1 Merge pipe, 200A 1st merge pipe, 200B 2nd merge pipe, 301 Refrigeration cycle apparatus, 500 Refrigerant distributor, 510 Heat exchanger.

Claims (13)

A refrigerant distributor that constitutes a part of a heat exchanger that includes a plurality of heat transfer tubes arranged in parallel at different heights and is connected to the plurality of heat transfer tubes,
A first tubular portion in which the refrigerant flows upward;
A second cylinder part connected to the first cylinder part and the refrigerant flowing out of the first cylinder part flowing downward,
The first tube portion and the second tube portion are connected to heat transfer tubes having different heights among the plurality of heat transfer tubes.
Refrigerant distributor. The first tube portion is connected to an upper heat transfer tube among the plurality of heat transfer tubes,
The second tube portion is connected to a lower heat transfer tube among the plurality of heat transfer tubes,
The refrigerant distributor according to claim 1. The first tube portion causes the refrigerant that has flowed out from above the heat transfer tube connected to the first tube portion to flow into the second tube portion.
The refrigerant distributor according to claim 1 or 2. A bypass path for bypassing the lower portion of the second cylindrical portion to the lower portion of the first cylindrical portion;
The bypass passage allows the refrigerant to pass therethrough at least when the refrigerant is caused to flow backward;
The refrigerant distributor as described in any one of Claims 1-3. The bypass path is connected to a lower end of the second cylinder part.
The refrigerant distributor according to claim 4. Switching that is arranged in the bypass passage and switches the flow path so that the refrigerant does not pass through the bypass passage when the refrigerant does not flow backward, and the refrigerant passes through the bypass passage when the refrigerant flows backward. Further comprising means,
The refrigerant distributor according to claim 4 or 5. A flow rate adjusting device that is disposed between the first tube portion and the second tube portion and controls a flow rate of the refrigerant flowing through the second tube portion;
The refrigerant distributor as described in any one of Claims 1-6. The refrigerant distributor according to any one of claims 1 to 7,
A first heat exchange section including a heat transfer tube to which the first tube section is connected;
A second heat exchange part including a heat transfer tube to which the second cylinder part is connected,
Heat exchanger. The first heat exchange unit and the second heat exchange unit are configured separately.
The heat exchanger according to claim 8. A main heat exchange section having the first heat exchange section and the second heat exchange section;
A sub heat exchange part,
The refrigerant distributor connects the main heat exchange unit and the sub heat exchange unit,
The heat exchanger according to claim 8 or 9. A refrigeration cycle apparatus comprising the heat exchanger according to any one of claims 8 to 10,
When the heat exchanger acts as an evaporator, the refrigerant flows from the first tube portion to the second tube portion.
Refrigeration cycle equipment. A refrigeration cycle apparatus comprising the heat exchanger according to claim 10,
When the heat exchanger acts as an evaporator, the refrigerant flows from the auxiliary heat exchange portion into the main heat exchange portion, and flows from the first tube portion to the second tube portion.
Refrigeration cycle equipment. Further comprising a blower that blows air to the heat exchanger;
The blower device is disposed near the first heat exchange unit as compared with the second heat exchange unit.
The refrigeration cycle apparatus according to claim 11 or 12.

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