JP5208030B2 - Air conditioner - Google Patents

Description

  The present invention relates to an air conditioner having a refrigerant distributor that distributes refrigerant to a predetermined distribution ratio.

  Conventionally, there is an air conditioner equipped with a refrigerant distributor that distributes a refrigerant at a predetermined distribution ratio. In order to evenly distribute the low-pressure gas-liquid two-phase refrigerant, the refrigerant distributor first causes the conical orifice to contract the flow, and then discharges the gas-liquid two-phase refrigerant to the gas part and the liquid part. Are generally mixed and introduced into a distribution pipe so as to be uniformly distributed. Therefore, when the gas-liquid two-phase refrigerant flows from the refrigerant pipe into the conical orifice in the distributor body, the flow velocity of the gas-liquid two-phase refrigerant can be gradually increased, and a sudden pressure drop can be prevented. It has become.

  As a result, the conventional refrigerant distributor is provided with a conical orifice, which is a constricted flow portion that gradually reduces the cross-sectional area inside the distributor main body, which causes a problem of increasing the size of the distributor itself. It was. In addition, the conical orifice provided in the refrigerant distributor can be inserted into the distributor main body in the reverse direction, so that the assembly procedure may not function as a refrigerant circuit by mistake during assembly. Also occurred. Various techniques for solving such problems have been proposed.

  As such, it is provided between the decompression device and the evaporator of the refrigerant circuit having a compressor, a condenser, a decompression device, and an evaporator, and has a cross-sectional area in the direction of the refrigerant flow in order from the inlet. A conical orifice that accelerates the flow of the reduced-flow refrigerant that gradually decreases, and a distribution hole that mixes the gas-liquid two-phase refrigerant accelerated by the conical orifice and to which a distribution pipe for distributing the refrigerant is connected In the distributor, a conical orifice for accelerating the flow of the refrigerant is inserted and disposed in the refrigerant pipe on the distributor insertion side, and the end of the conical orifice whose sectional area gradually decreases is distributed. In other words, there is a proposal that the flange portion is provided larger than the inner diameter of the inlet refrigerant pipe of the vessel and the other end is provided smaller than the inner diameter of the refrigerant pipe (see, for example, Patent Document 1).

  Further, as a refrigerant distributor mounted on an air conditioner, “a container having a shunt generation unit having a plane for colliding and splitting a gas-liquid two-phase fluid and a plane of the shunt generation unit from a vertical direction” An inflow portion that collides a gas-liquid two-phase fluid and divides the fluid to form a liquid film on the inner surface of the container; and a flow direction of the fluid that is provided in the liquid film forming portion of the inner surface of the container and flows in by the inflow portion. And a plurality of outflow portions that flow out fluids in different flow directions, and the flow passage cross-sectional areas of the plurality of outflow portions are changed according to the respective liquid distribution amounts (for example, Patent Document 2). reference).

Japanese Patent Laid-Open No. 10-253196 (Embodiment 1, FIG. 1, etc.) Japanese Patent Laid-Open No. 11-316066 (Embodiment 1, FIG. 1, etc.)

  In the refrigerant distributor of the air conditioner described in Patent Document 1, a conical orifice that is smaller than the inner diameter of the refrigerant pipe on the distributor insertion side is provided, so that a large pressure loss occurs when the fluid passes through. As a result, the performance of the heat exchanger alone was reduced. In addition, the coefficient of performance of the refrigeration cycle is reduced due to an increase in low-pressure pressure loss, and in particular, in the case of refrigerant distribution in a high-flow-rate gas-liquid two-phase refrigerant, there has been a problem that the decrease in the coefficient of performance becomes more significant. In order to reduce the pressure loss, measures such as using multiple distributors or increasing the size of the distributor can be considered, but there are problems such as an increase in the size of the distributor itself and an extra cost burden. It will be newly invited.

  Moreover, in the refrigerant distributor of an air conditioning apparatus as described in Patent Document 2, a large space is required because the gas-liquid two-phase refrigerant collides with a flat surface and diverts, and the refrigerant distributor itself is large. There is a problem that an extra cost burden is generated. Further, it is necessary to provide a member that partially shields the inside of the container and a guide for controlling the flow of the fluid with respect to the fluid flowing into the container, which further promotes an increase in size. Furthermore, when the refrigerant distributor is tilted, there is a problem that the distribution performance deteriorates.

  The present invention has been made to solve the above-described problem, and has a low pressure loss even in the case of a high-flow-rate gas-liquid two-phase refrigerant, and a refrigerant distributor capable of stable refrigerant distribution with a simple configuration. It aims at providing the air conditioning apparatus which has this.

  An air conditioner according to the present invention has a refrigeration cycle in which a compressor, a refrigerant distributor, a plurality of heat source apparatus side heat exchangers, a flow rate regulator, and a use side heat exchanger are connected by piping, and the refrigerant distribution The vessel has a box-like shape, an inflow portion for allowing the gas-liquid two-phase refrigerant to flow into the main body from the vertically lower side, a branch space portion for spreading the gas-liquid two-phase refrigerant flowing from the inflow portion, A plurality of portions that are formed so as to open radially around the branch space portion at equal angles from the center of the cross section in the refrigerant inflow direction of the branch space portion and distribute the refrigerant spread in the branch space portion. A distribution hole, and a plurality of outflow portions that communicate with each of the distribution holes and allow the gas-liquid two-phase refrigerant to flow out of the main body, and each of the plurality of outflow portions includes the plurality of heat source units. It is connected to each of the side heat exchangers .

  The air conditioner according to the present invention is formed so that a part thereof is radially opened around the branch space part at an equal angle from the center of the cross section in the refrigerant inflow direction of the branch space part, and spread in the branch space part. Since the refrigerant distributor having the plurality of distribution holes for distributing the fluid is provided, the refrigerant can be distributed evenly and the pressure loss can be reduced. In addition, since the refrigerant distributor has a simple configuration, it can be downsized and the cost can be reduced, which contributes to downsizing and cost reduction of the heat source unit constituting the air conditioner.

3 is an explanatory diagram for explaining a refrigerant distributor according to Embodiment 1. FIG. It is BB sectional drawing of FIG. It is AA sectional drawing of FIG. 6 is an explanatory diagram for explaining a refrigerant distributor according to Embodiment 2. FIG. 6 is an explanatory diagram for explaining a refrigerant distributor according to Embodiment 2. FIG. 6 is a circuit diagram illustrating a circuit configuration of an air-conditioning apparatus according to Embodiment 3. FIG. It is a schematic block diagram which shows the internal structural example of a heat source machine. It is a refrigerant circuit figure which shows the flow of the refrigerant | coolant at the time of the cooling main operation mode of an air conditioning apparatus. It is a refrigerant circuit diagram which shows the flow of the refrigerant | coolant at the time of heating main operation mode of an air conditioning apparatus.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Embodiment 1 FIG.
FIG. 1 is an explanatory diagram for explaining a refrigerant distributor 50 according to Embodiment 1 of the present invention. 2 is a cross-sectional view taken along the line BB in FIG. 3 is a cross-sectional view taken along the line AA in FIG. Based on FIGS. 1-3, the structure and effect | action of the refrigerant distributor 50 are demonstrated. 1A is an external perspective view showing a schematic configuration of the refrigerant distributor 50, FIG. 1B is a plan view showing the refrigerant distributor 50 viewed from the outflow portion forming surface side, and FIG. ) Show plan views seen through the refrigerant distributor 50 as seen from the inflow portion forming surface side. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one.

  The refrigerant distributor 50 according to Embodiment 1 is provided in the air conditioner according to Embodiment 2, and distributes the inflowing refrigerant (gas-liquid two-phase refrigerant) into a plurality of predetermined distribution ratios. The refrigerant distributor 50 includes a box-shaped main body 1, an inflow portion 2, three outflow portions 3 (outflow portion 3a, outflow portion 3b, and outflow portion 3c), a branch space portion 5, have. The main body 1 has a function as a container into which a fluid flows. In addition, although Embodiment 1 demonstrates as an example the case where the flowed-in fluid branches into three, it does not limit to this. For example, the inflowing fluid may be branched into four or more branches. FIG. 1 shows the valve body mounting hole 4, which will be described in detail in the second embodiment.

  The inflow portion 2 is formed on any surface of the main body 1 (described here as a lower surface), and a pipe that conducts fluid can be connected thereto. The inflow portion 2 is configured to allow fluid to flow into the inside of the main body 1 from a vertically downward direction through a connected pipe. The outflow portion 3 is formed on any surface of the main body 1 (any surface adjacent to the formation surface of the inflow portion 2, that is, a surface having an angle of 90 ° with the inflow portion formation surface). A pipe that conducts electricity can be connected. The outflow portions 3 communicate with the distribution holes, respectively, and allow the fluid branched in the branch space portion 5 to flow out to the connected pipe. In addition, the outflow part 3a, the outflow part 3b, and the outflow part 3c are formed so that it may be located in a line on a horizontal line centering on the outflow part 3b.

  The branch space portion 5 is formed inside the main body 1 so that the upper wall serving as a flat portion is parallel to the lower surface of the main body 1, and the fluid flowing in from the inflow portion 2 collides with the flat portion, and is evenly distributed radially. It is designed to spread. The branch space 5 has a plurality of distribution holes (distribution holes 5a, distribution holes 5b, and distribution holes 5c) for evenly distributing the evenly spread fluid around the periphery. The distribution holes are formed at equal angles and radially from the center of the branch space 5 (the center of the cross section in the fluid inflow direction of the branch space 5).

  The distribution holes are formed in the branch space 5 so as to open the branch space 5 by a predetermined flow path cross-sectional area 6 (cross-sectional area 6a, cross-sectional area 6b, and cross-sectional area 6c). That is, in the plurality of distribution holes formed around the branch space portion 5, a part of each flow path cross-sectional area 6 (cross-sectional area 6 a, cross-sectional area 6 b, and cross-sectional area 6 c) opens into the branch space portion 5. It is formed like this.

The formation position of the distribution hole will be described.
The fluid that has flowed into the branch space portion 5 from the inflow portion 2 collides with the flat surface portion (upper wall surface) of the branch space portion 5 and is evenly spread radially. In order to flow out the equally distributed fluid evenly, the distribution holes are formed at substantially equal intervals. Therefore, in the first embodiment, taking the case of three branches as an example, at the distribution angle of 120 ± 0.5 ° from the center of the branch space portion 5, the center of each distribution hole (the cross section of each distribution hole in the fluid inflow direction). The distribution hole 5a, the distribution hole 5b, and the distribution hole 5c are formed so as to be adjacent to each other. Further, the distance from the central axis (the axis in the fluid inflow direction at the center) of the branch space 5 to the center axis of each distribution hole (the axis in the point fluid inflow direction at the center of each distribution hole) is set to 22 to 24 mm. ing.

  In other words, in the refrigerant distributor 50, the flat portion of the branch space portion 5 that collides with the fluid flowing in from the vertically downward direction and spreads uniformly is provided with the distribution hole 5a, the distribution hole 5b, and the distribution hole 5c formed at substantially equal intervals. In the same flow path and close to the distribution hole 5a, the distribution hole 5b, and the distribution hole 5c. Therefore, in the refrigerant distributor 50, the fluid that is evenly spread in the branch space portion 5 can flow out from the outflow portion 3 evenly. When the fluid is evenly distributed in four directions, four distribution holes may be formed at a distribution angle of 90 ± 0.5 ° from the center point O of the branch space portion 5. That is, the distribution angle may be determined by 360 ° ÷ number of distribution holes. In addition, although a case where fluid is evenly distributed will be described as an example, it is assumed that even if there is some width in the distribution amount, it is equally included.

The operation of the refrigerant distributor 50 will be described.
A gas-liquid two-phase refrigerant flows in vertically upward from an inflow portion 2 formed in the main body 1 through a pipe. The refrigerant diffuses while flowing into the branch space 5 and forms an annular flow that forms a liquid film on the inner wall of the main body 1. The liquid film produced here tends to be uniform mainly due to the symmetry of the branch space 5 and the influence of the surface tension. For this reason, the ratio of the liquid amounts Ga, Gb, Gc per unit time flowing into the outflow part 3a, outflow part 3b, and outflow part 3c of the main body 1 is such that the distribution holes 5a and distribution holes opened radially in the branch space part 5 5b and the ratio of the sectional area 6a, the sectional area 6b, and the sectional area 6c of the distribution hole 5c.

  Accordingly, the ratio of the predetermined liquid distribution amount and the ratio of the cross-sectional area 6a, the cross-sectional area 6b, and the cross-sectional area 6c of the distribution hole 5a, distribution hole 5b, and distribution hole 5c can be variably adjusted to have an arbitrary ratio with a simple configuration. It is possible to accurately obtain the gas-liquid distribution amount. That is, since the refrigerant can be distributed with high accuracy only by variably adjusting the ratio of the cross-sectional area 6a, the cross-sectional area 6b, and the cross-sectional area 6c, the design can be easily performed. Further, since the distribution holes 5a, the distribution holes 5b, and the distribution holes 5c are formed at equal angles from the center of the branch space portion 5, the main body 1 can be downsized.

  Since the refrigerant distributor 50 is configured as described above, it is possible to distribute the fluid accurately and evenly with a simple structure. When the refrigerant distributor 50 having such a simple structure is incorporated in a refrigeration cycle and gas-liquid two-phase refrigerant is distributed to a plurality of evaporators, the amount of liquid distributed to each evaporator can be controlled. Sometimes the pressure loss can be reduced and the performance of the entire refrigeration cycle can be maintained. Further, with the simplification of the structure, the refrigerant distributor 50 can realize a reduction in processing man-hours and a reduction in size and weight.

  In the first embodiment, the case where the main body 1 has a rectangular parallelepiped shape has been described as an example, but a part of the rectangular parallelepiped may be excised. By doing so, it is possible to reduce the cost by reducing the mass of the member. The refrigerant distributor 50 has specifications such as distribution amount variation, pressure resistance, and corrosion resistance. In particular, in order to satisfy the pressure resistance specification, a minimum wall thickness is required for each hole (for example, the inflow portion 2 or the outflow portion 3) formed in the molding block on which the main body 1 is based. You should consider it. Therefore, the surplus portion of the box-shaped main body 1 can be excised.

Embodiment 2. FIG.
4 and 5 are explanatory diagrams for explaining the refrigerant distributor 51 according to Embodiment 2 of the present invention. Based on FIG.4 and FIG.5, the structure and effect | action of the refrigerant distributor 51 are demonstrated. FIG. 4 shows a state where the coil is not energized, and FIG. 5 shows a state where the coil is energized. 4A is a plan view showing the refrigerant distributor 51 as viewed from above, and FIG. 4B is a cross-sectional view taken along line AA in FIG. 4A. 5A is a plan view showing the state of the refrigerant distributor 51 as viewed from above, and FIG. 5B is a cross-sectional view taken along line AA of FIG. 5A. In the second embodiment, differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.

  This refrigerant distributor 51 is different from the refrigerant distributor 50 according to the first embodiment in that the switching valve 60 is integrally provided. That is, in the main body of the refrigerant distributor 51 (hereinafter referred to as the main body 1a), three valve body mounting holes 4 are formed corresponding to the respective distribution holes (see FIG. 1). The valve body mounting hole 4 is formed on any surface of the main body 1 (described here as an upper surface), and a switching valve 60 for adjusting the amount of fluid flowing out from the outflow portion 3 is integrally mounted. It is supposed to be. The valve body attachment hole 4 is formed at a position corresponding to the formation position of each distribution hole. 4 and 5, one switching valve 60 will be described as a representative.

  As shown in FIG. 2, the valve body mounting hole 4 is formed with a main valve chamber 7 communicating with the distribution hole and the outflow portion 3 in the vertical direction. Therefore, three main valve chambers 7 are formed in the main body 1a in accordance with the number of valve body mounting holes 4. A valve seat 8 is provided at the boundary between each distribution hole and each outflow portion. A bypass pipe 3d that bypasses a part of the refrigerant that has flowed in is attached to any of the distribution holes by brazing (the operation will be described in Embodiment 3). Further, a lid body 9 that shuts off the inside of the main valve chamber 7 from the outside is screwed by a female screw portion in the vicinity of the external opening 10 of the main valve chamber 7.

  The main valve 11 constituting the switching valve 60 is provided to be slidable in the vertical direction in the main valve chamber 7 and opens and closes the hole 12 formed in the valve seat 8. The lid body 9 is formed with a sub valve chamber 14 communicating with the main valve chamber 7 via the first communication port 13a. The sub valve chamber 14 is provided with a sub valve 18 that slides in the sub valve chamber 14 by the electromagnetic force of the electromagnetic coil 15 to open and close the pilot hole 17 of the lid port 16. And the 2nd communication port 19 which connects the sub valve chamber 14 and the outflow part 3 is formed in the main body port 20 formed in the main body 1a, the lid body port 16 formed in the lid body 9, and communicated with the main body port 20. It is composed of In addition, since the cylindrical space 21c is formed between the main body 1a and the lid body 9 when the screw is fixed, the lid body port 16 may be located in any of the circumferential directions.

  Further, the lid body 9 is configured as a component in which a case 23 containing a sub valve 18 and a spring 22 is attached to the opening of the sub valve chamber 14 and brazed, and an O-ring 24 is attached. The electromagnetic coil 15 for attracting the sub-valve 18 is configured to be separated and independent from the main body 1 a and is attached to the case 23. The O-ring 24 is attached to block the space 25 between the main valve 11 and the lid body 9 and the space 21. The first communication port 13 is formed in parallel with the main valve 11. A clearance necessary for sliding is provided between the main valve chamber 7 and the main valve 11.

  The operation of the refrigerant distributor 51 will be described focusing on the difference from the refrigerant distributor 50, that is, the operation of the switching valve 60. As shown in FIG. 4, when the electromagnetic coil 15 is not energized, the pilot hole 17 of the lid port 16 is closed by the spring 22. The pressures in the distribution hole space 26 (channel cross-sectional area 6), the space 25 in the main valve chamber 7, and the space 27 in the outflow portion 3 are P1, P2, and P3, respectively. The pressure relationship at this time is P1≈P2> P3, the main valve 11 remains in the state where the hole 12 of the valve seat 8 is closed, and the flow path is blocked.

  On the other hand, as shown in FIG. 5, when the electromagnetic coil 15 is energized, the sub valve 18 is attracted to the upper portion of the case 23 in the sub valve chamber 14 by the electromagnetic force. As a result, the pilot hole 17 of the lid port 16 is opened, and the space 25 near the first communication port 13 of the main valve chamber 7 is the first communication port 13, the sub valve chamber 14, the lid port 16, the space 21, and the main body. It passes through the port 20 and communicates with the space 27 of the outflow portion 3. Therefore, the pressure relationship is P1> P2≈P3, and the main valve 11 is pulled up by the pressure difference generated between the pressure P1 of the distribution hole and the pressure P2 of the space 25 near the first communication port 13, and the valve seat 8 The hole 12 is opened and a flow path is formed.

  Therefore, a specific flow path can be formed by energizing the electromagnetic coil 15 as necessary, and the flow rate of the refrigerant can be adjusted. That is, since the switching valve 60 is integrally attached to each of the distribution holes, the refrigerant flow rate flowing out through each distribution hole can be individually adjusted. Moreover, since the switching valve 60 is integrally attached to the main body 1a, the refrigerant distributor 51 can be downsized. Furthermore, it goes without saying that the flow rate can be further adjusted by making the cross-sectional area 6a, the cross-sectional area 6b, and the cross-sectional area 6c variable.

  Since the refrigerant distributor 51 is configured as described above, the fluid can be distributed with high accuracy and uniformity with a simple structure, and optimization of adjustment of the flow rate of the refrigerant flowing out can be easily realized. In this way, when the refrigerant distributor 51 in which the distributor and the switching valve are integrated is incorporated in the refrigeration cycle and the gas-liquid two-phase refrigerant is distributed to a plurality of evaporators, the amount of liquid distributed to each evaporator is determined. Since it can be controlled, the pressure loss can be reduced at a high flow rate, and the manufacturing cost can be reduced while maintaining the performance of the entire refrigeration cycle. Further, with the simplification of the structure, the refrigerant distributor 51 can realize a reduction in processing man-hours and a reduction in size and weight.

Embodiment 3.
FIG. 6 is a circuit diagram showing a circuit configuration of the air-conditioning apparatus 100 according to Embodiment 3 of the present invention. FIG. 7 is a schematic configuration diagram illustrating an internal configuration example of the heat source device A. Based on FIG.6 and FIG.7, the circuit structure of the air conditioning apparatus 100 and the internal structure of the heat-source equipment A are demonstrated. The air conditioner 100 is installed in a building, a hotel, or the like, and can simultaneously supply a cooling load and a heating load by using a refrigeration cycle that circulates a refrigerant. Note that the air conditioner 100 according to Embodiment 3 is provided with the refrigerant distributor 51 according to Embodiment 2.

  As shown in FIG. 7, the refrigerant distributor 51 is configured integrally with the switching valve 60 so that the refrigerant flows in from the bottom in the vertical direction, that is, the inflow portion 2 is the lower surface of the main body 1a. It arrange | positions above A and is supported by fixing members, such as a sheet metal. As shown in FIG. 6, the air conditioner 100 includes one heat source unit A and a plurality of indoor units (in FIG. 6, the indoor unit C, the indoor unit D, and the indoor unit E are illustrated. And a single repeater B interposed between these units. Note that the number of the heat source unit A, the indoor unit, and the relay unit B is not limited to the illustrated number.

  The heat source unit A has a function of supplying cold heat to the indoor unit via the relay unit B. The indoor unit is installed in a room or the like having an air-conditioning target area, and has a function of supplying cooling air or heating air to the air-conditioning target area. The relay unit B has a function of connecting the heat source unit A and the indoor unit and transmitting the cold heat supplied from the heat source unit A to the indoor unit. That is, the heat source unit A and the relay unit B are connected via the first branching unit 110 and the gas-liquid separator 112 built in the relay unit B, and the relay unit B and the indoor unit are It is connected via a first branching unit 110 and a second branching unit 111 built in the repeater B. Hereinafter, the configuration and function of each component device will be described.

[Heat source machine A]
The heat source unit A includes a compressor 101, a four-way valve 102 that is a flow path switching unit that switches a refrigerant flow direction, a refrigerant distributor 51, and a plurality of heat source side (outdoor) heat exchangers 103 as refrigerant pipes. It is configured to be connected in series. Among the plurality of heat source machine side heat exchangers 103, those connected to the outflow part 3a of the refrigerant distributor 51 are connected to the heat source machine side heat exchanger 103a, and the outflow part 3b of the refrigerant distributor 51 is connected to the heat source machine side. What is connected to the heat exchanger 103b and the outflow portion 3c of the refrigerant distributor 51 is referred to as a heat source apparatus side heat exchanger 103c.

  A switching valve illustrated between the refrigerant distributor 51 and the heat source apparatus side heat exchanger 103a is a switching valve 60 (hereinafter referred to as a switching valve 60a) attached to the refrigerant distributor 51. A check valve 123a is connected to the side of the heat source unit side heat exchanger 103a to which the switching valve 60a is not connected. The switching valve shown between the refrigerant distributor 51 and the heat source apparatus side heat exchanger 103b is a switching valve 60 (hereinafter referred to as a switching valve 60b) attached to the refrigerant distributor 51. A check valve 123b is connected to the side of the heat source device side heat exchanger 103b to which the switching valve 60b is not connected.

  A bypass pipe 3d for bypassing the heat source unit side heat exchanger 103c is connected to the refrigerant pipe connected to the outflow portion 3c. The switching valve illustrated in the bypass pipe 3d is a switching valve 60 (hereinafter referred to as a switching valve 60c) attached to the refrigerant distributor 51. That is, in the refrigerant distributor 51 described in the second embodiment, the outflow portions 3 corresponding to the number of refrigerant distributions are formed and the switching valves 60 are respectively attached. Even if closed, the refrigerant can flow out through the outflow portion 3c. Therefore, the flow rate of the refrigerant flowing out from the outflow portion 3c can be adjusted by the switching valve 60c in the bypass pipe 3d.

  In addition, the first connection pipe 70 to which the check valve 125 is connected, the second connection pipe 71 to which the check valve 126 is connected, and the third connection to which the check valve 120 is connected to the heat source machine A A pipe 72 and a fourth connection pipe 73 to which the check valve 121 is connected are provided. Further, a check valve 118 and a check valve 119 are connected between the connection portion of the third connection pipe 72 and the connection portion of the fourth connection pipe 73. Check valve 118, check valve 119, check valve 120, check valve 121, check valve 125, check valve 126, first connection pipe 70, second connection pipe 71, third connection pipe 72, and The fourth connection pipe 73 makes it possible to make the flow of the refrigerant flowing into the heat source unit side heat exchanger 103 in a certain direction regardless of the operation that the indoor unit is executing. An accumulator 104 is provided on the suction side of the compressor 101.

  The compressor 101 sucks the refrigerant and compresses the refrigerant to a high temperature / high pressure state, and may be composed of, for example, an inverter compressor capable of capacity control. The four-way valve 102 switches the refrigerant flow during the heating operation and the refrigerant flow during the cooling operation. The heat source unit side heat exchanger 103 functions as an evaporator during heating operation, functions as a condenser during cooling operation, and performs heat exchange between air supplied from a blower such as a fan (not shown) and the refrigerant, The refrigerant is evaporated or condensed and liquefied. The check valve 118, the check valve 119, the check valve 120, the check valve 121, the check valve 125, and the check valve 126 all allow the refrigerant to flow only in a predetermined direction.

  The check valve 118 is provided between the connection part of the third connection pipe 72 and the connection part of the fourth connection pipe 73 between the heat source apparatus side heat exchanger 103 and the gas-liquid separator 112, and the heat source apparatus A The flow of the refrigerant is permitted only in the direction from the relay to the relay B. The check valve 119 is provided between the connection portion of the third connection pipe 72 and the connection portion of the fourth connection pipe 73 between the four-way valve 102 and the first branch portion 110 and the second branch portion 111, and relays The flow of the refrigerant is permitted only in the direction from the machine B to the heat source machine A.

  The check valve 120 is provided in the third connection pipe 72, and the second extension pipe connecting the heat source apparatus side heat exchanger 103 and the relay machine B from the first extension pipe 106 connecting the four-way valve 102 and the relay machine B. The refrigerant flow is allowed only in the direction 107. The check valve 121 is provided in the fourth connection pipe 73 and allows the refrigerant to flow only in the direction from the first extension pipe 106 to the second extension pipe 107. The check valve 125 is provided in the first connection pipe 70 and allows the refrigerant to flow only in the direction from the second extension pipe 107 to the first extension pipe 106. The check valve 126 is provided in the second connection pipe 71 and allows the refrigerant to flow only in the direction from the second extension pipe 107 to the first extension pipe 106.

  The first connection pipe 70 connects the first extension pipe 106 between the four-way valve 102 and the refrigerant distributor 51 and the second extension pipe 107 between the heat source apparatus side heat exchanger 103 and the check valve 118. To do. The second connection pipe 71 is a first extension pipe 106 between the four-way valve 102 and the refrigerant distributor 51, which is closer to the four-way valve 102 than the connection portion of the first connection pipe 70, and the heat source machine side heat exchanger 103. And the check valve 118, the second extension pipe 107 is connected to the heat source unit side heat exchanger 103 side rather than the connection portion of the first connection pipe 70.

  The third connection pipe 72 connects the first extension pipe 106 and the second extension pipe 107 on the downstream side of the check valve 118 on the downstream side of the check valve 119. The fourth connection pipe 73 connects the first extension pipe 106 on the upstream side of the check valve 119 and the second extension pipe 107 on the upstream side of the check valve 118. The accumulator 104 has a function for storing surplus refrigerant generated depending on the operating state. Note that the accumulator 104 is not necessarily provided.

[Indoor unit]
In each indoor unit, a first flow rate regulator 109 and a use side (indoor) heat exchanger 105 are connected in series and built in. The use-side heat exchanger 105 functions as a condenser during heating operation, functions as an evaporator during cooling operation, and performs heat exchange between air supplied from a blower such as a fan (not shown) and the refrigerant, Heating air or cooling air to be supplied to the air conditioning target area is created. The use-side heat exchanger 105 is connected to the first branch 110 provided in the relay machine B via the first extension pipe 106. The usage-side heat exchanger 105 is illustrated as a usage-side heat exchanger 105c, a usage-side heat exchanger 105d, and a usage-side heat exchanger 105e from the left side of the page depending on the indoor unit to be mounted.

  The first flow rate regulator 109 has a function as a pressure reducing valve or an expansion valve, and decompresses and expands the refrigerant. During cooling operation, the degree of superheat on the outlet side of the use side heat exchanger 105 and during heating operation Is adjusted by the degree of supercooling. The first flow rate regulator 109 may be constituted by a valve whose opening degree can be variably controlled, for example, an electronic expansion valve. The first flow rate regulator 109 is connected to the second branch portion 111 provided in the relay machine B via the second extension pipe 107. Note that the first flow rate regulator 109 is illustrated as a first flow rate regulator 109c, a first flow rate regulator 109d, and a first flow rate regulator 109e from the left side of the page, depending on the indoor unit to be mounted.

[Repeater B]
The repeater B includes a first branching unit 110, a second branching unit 111, a gas-liquid separator 112, a second flow rate regulator 113, a third flow rate regulator 115, and a first heat exchanger 117. The second heat exchanger 116 is built in. For convenience of the following description, the first extension pipe 106, the second extension pipe 107, and the bypass pipe 114 will be described first.

  The first extension pipe 106 is a pipe that connects the four-way valve 102 and the first branch part 110 to each other and the first branch part 110 and each use side heat exchanger 105. The second extension pipe 107 is a pipe that connects the check valve 118 and the gas-liquid separator 112 to each of the first flow rate regulators 109 and the second branch portion 111. The bypass pipe 114 is branched from the second extension pipe 107 between the gas-liquid separator 112 and the second branch section 111 and connected to the second branch section 111 and the first extension pipe 106 on the heat source unit A side. It is piping.

  The first extension pipe 106 that connects the first branching section 110 and each use side heat exchanger 105 has a first extension pipe 106c and a first extension pipe from the left side of the drawing according to the connected use side heat exchanger 105. 106d and the first extension pipe 106e are illustrated. Similarly, the second extension pipe 107 connecting each first flow rate regulator 109 and the second branch portion 111 is connected to the second extension pipe 107c, the second extension pipe 107c from the left side of the page according to the connected first flow rate regulator 109. It is illustrated as a second extension pipe 107d and a second extension pipe 107e. The pipe diameters of the first extension pipe 106 and the second extension pipe 107 are not particularly limited. For example, if the pipe diameter of the first extension pipe 106 is made larger than the pipe diameter of the second extension pipe 107, Good.

  The first branching unit 110 has a function of switching the flow of the refrigerant according to the operation status of the indoor unit C, the indoor unit D, and the indoor unit E. In the first branching section 110, the first extension pipe 106 (the first extension pipe 106c, the first extension pipe 106d, and the first extension pipe 106e) on the indoor unit side is branched and opens and closes the pipes respectively. An electromagnetic valve 108 is provided. That is, the first extension pipe 106c includes the solenoid valve 108a and the solenoid valve 108b, the first extension pipe 106d includes the solenoid valve 108c and the solenoid valve 108d, and the first extension pipe 106e includes the solenoid valve 108e and the solenoid valve 108f. Each is provided.

  In the first branch portion 110, the opening and closing of each of the electromagnetic valves 108 is controlled, whereby the first extension pipe 106 on the heat source machine A side and the first extension pipe 106 on the indoor unit side are connected via the bypass pipe 114. Alternatively, the second extension pipe 107 and the first extension pipe 106 on the indoor unit side can be switched via the gas-liquid separator 112. Note that the number of solenoid valves is determined according to the number of first extension pipes 106 on the indoor unit side that increases in accordance with the number of indoor units connected to the relay unit B.

  The second branching unit 111 has a function of switching the flow of the refrigerant according to the operation status of the indoor unit C, the indoor unit D, and the indoor unit E. In the second branch portion 111, the second extension pipe 107 is branched into a second extension pipe 107 (a second extension pipe 107c, a second extension pipe 107d, and a second extension pipe 107e) on the indoor unit side. In other words, the second extension pipe 107 on the indoor unit side joins at the meeting part of the second branch part 111.

  The gas-liquid separator 112 includes a second extension pipe 107 on the downstream side of the check valve 118, a second extension pipe 107 joined at the second branch part 111, and a first extension branched at the first branch part 110. It is connected to the pipe 106. The gas-liquid separator 112 has a function of separating the refrigerant that has flowed into a gaseous refrigerant and a liquid refrigerant, and the gas phase component is divided into the first branch part 110 (the first branch part branched by the first branch part 110). The liquid phase part is connected to the extension pipe 106) to the second branch part 111 (the second extension pipe 107 joined at the second branch part 111).

  The second flow rate regulator 113 is provided between the gas-liquid separator 112 and the second branch part 111. The second flow rate regulator 113 functions as a pressure reducing valve or an expansion valve, and expands the refrigerant by reducing the pressure. The second flow rate regulator 113 may be configured by a variable controllable opening, for example, an electronic expansion valve. The third flow regulator 115 is provided in the bypass pipe 114. The third flow rate regulator 115 functions as a pressure reducing valve and an expansion valve, and expands the refrigerant by reducing the pressure. The third flow rate regulator 115 may be constituted by a device whose opening degree can be variably controlled, for example, an electronic expansion valve.

  The second heat exchanger 116 includes a refrigerant that flows through the second extension pipe 107 between the second flow rate regulator 113 and the second branch portion 111, and a refrigerant that flows through the bypass pipe 114 that has passed through the third flow rate regulator 115. , Heat exchange. The first heat exchanger 117 includes a refrigerant that flows through the second extension pipe 107 between the gas-liquid separator 112 and the second flow rate regulator 113, and a refrigerant that flows through the bypass pipe 114 that has passed through the second heat exchanger 116. , Heat exchange. That is, the second heat exchanger 116 and the first heat exchanger 117 have a function as a refrigerant-refrigerant heat exchanger.

  Each operation mode which the air conditioning apparatus 100 performs is demonstrated. The air conditioner 100 can perform a cooling operation or a heating operation with the indoor unit based on an instruction from each indoor unit. That is, the air conditioner 100 can perform the same operation for all the indoor units, and can perform different operations for each of the indoor units. Below, two operation modes which the air conditioning apparatus 100 performs, ie, a cooling main operation mode and a heating main operation mode, are demonstrated with the flow of a refrigerant | coolant.

[Cooling operation mode]
FIG. 8 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 is in the cooling main operation mode. The cooling main operation mode is a simultaneous cooling / heating operation mode in the case where the cooling load is larger, for example, in which two indoor units perform cooling operation and one indoor unit performs heating operation. FIG. 8 illustrates an example in which the indoor unit C and the indoor unit D perform a cooling operation, and the indoor unit E performs a heating operation. Moreover, in FIG. 8, the flow direction of the refrigerant | coolant is shown with the solid line arrow.

  In the heat source machine A, the four-way valve 102 is switched so that the refrigerant discharged from the compressor 101 flows into the heat source machine side heat exchanger 103. In the relay B, the electromagnetic valve 108a, the electromagnetic valve 108c, and the electromagnetic valve 108f are opened in the first branching section 110, the electromagnetic valve 108b, the electromagnetic valve 108d, and the electromagnetic valve 108e are closed, and the opening degree of the second flow rate regulator 113 is the first. 2 Control is performed so that the differential pressure before and after the flow rate regulator 113 becomes a predetermined appropriate value.

  A low-temperature and low-pressure gaseous refrigerant is compressed by the compressor 101 and discharged as a high-temperature and high-pressure refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 101 passes through the four-way valve 102, passes through the refrigerant distributor 51, and the heat source machine side heat exchanger 103a, the heat source machine side heat exchanger 103b, and the heat source machine side. It flows into each of the heat exchangers 103c. This refrigerant is condensed and liquefied while dissipating heat to a heat medium such as air or water in the heat source apparatus side heat exchanger 103 to become a high-pressure gas-liquid two-phase refrigerant. At this time, a predetermined high pressure is maintained by appropriately opening and closing the switching valve 60a, the switching valve 60b, and the switching valve 60c.

  The high-pressure gas-liquid two-phase refrigerant that has flowed out of the heat source machine side heat exchanger 103a, the heat source machine side heat exchanger 103b, and the heat source machine side heat exchanger 103c passes through the check valve 118 and passes through the second extension pipe 107. And flows into the gas-liquid separator 112 of the relay B. The gas-liquid two-phase refrigerant flowing into the gas-liquid separator 112 is separated into a gaseous refrigerant and a liquid refrigerant by the gas-liquid separator 112.

  The separated gaseous refrigerant is guided to the first branch part 110. In the first branch 110, the gaseous refrigerant flows through the first extension pipe 106e via the electromagnetic valve 108f that is controlled to be in the open state. This gaseous refrigerant flows into the indoor unit E to be heated and dissipates heat to the use side heat medium such as air or water by the use side heat exchanger 105e, thereby condensing and liquefying to become a high pressure liquid refrigerant. . The refrigerant that has flowed out of the use side heat exchanger 105e passes through the first flow rate regulator 109e that is controlled by the degree of supercooling at the outlet of the use side heat exchanger 105e, is slightly reduced in pressure, and is intermediate between high pressure and low pressure. It becomes a pressure (intermediate pressure) and flows into the 2nd branch part 111 via the 2nd extension piping 107e.

  On the other hand, the liquid refrigerant separated by the gas-liquid separator 112 flows into the second branch portion 111 through the second flow rate regulator 113 which is controlled so as to make the difference between the high pressure and the intermediate pressure constant. And it flows in into the indoor unit C and the indoor unit D which are going to cool through the 2nd extension piping 107c and the 2nd extension piping 107d. This refrigerant flows into the first flow rate regulator 109c and the first flow rate regulator 109d controlled by the degree of superheat at the outlet of the use side heat exchanger 105c and the use side heat exchanger 105d, and the pressure is reduced to a low pressure. Then, it flows into the use side heat exchanger 105c and the use side heat exchanger 105d.

  The refrigerant flowing into the use side heat exchanger 105c and the use side heat exchanger 105d is evaporated and gasified by absorbing heat from the use side heat medium such as air or water. The gasified refrigerant flows through the first extension pipe 106c and the first extension pipe 106d and flows into the first branch portion 110. The refrigerant that has flowed into the first branch portion 110 flows through the electromagnetic valves 108a and 108d that are controlled to open, exits the first branch portion 110, and flows into the first extension pipe 106. Thereafter, the air is again sucked into the compressor 101 via the check valve 119, the four-way valve 102, and the accumulator 104.

  A part of the refrigerant flowing from the indoor unit E into the second branch unit 111 flows into the indoor unit D from the second branch unit 111, and the other refrigerant passes through the second flow rate regulator 113 from the second branch unit 111. The refrigerant merges with the refrigerant and flows into the indoor unit C and the indoor unit D from the second branch portion 111. At this time, since the first extension pipe 106 has a low pressure and the second extension pipe 107 has a high pressure, the refrigerant inevitably flows to the check valve 118 and the check valve 119. At this time, a part of the liquid refrigerant flows from the second extension pipe 107c and the second extension pipe 107d through the second branch portion 111 into the bypass pipe 114. The refrigerant that has flowed into the bypass pipe 114 is depressurized to a low pressure by the third flow rate regulator 115 and flows into and out of the second flow rate regulator 113 by the second heat exchanger 116 and the first heat exchanger 117. The refrigerant exchanges heat with the refrigerant to evaporate and flows into the first extension pipe 106.

[Heating main operation mode]
FIG. 9 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 is in the heating main operation mode. This heating main operation mode is a cooling / heating simultaneous operation mode in the case where the heating load is larger, for example, in which two indoor units perform a heating operation and one indoor unit performs a cooling operation. FIG. 9 illustrates an example in which the indoor unit C and the indoor unit D perform the heating operation, and the indoor unit E performs the cooling operation. Moreover, in FIG. 9, the flow direction of the refrigerant | coolant is shown with the solid line arrow.

  In the heat source device A, the four-way valve 102 is switched so that the refrigerant discharged from the compressor 101 flows into the relay device B. In the relay machine B, control is performed so that the electromagnetic valve 108a, the electromagnetic valve 108c, and the electromagnetic valve 108f are closed and the electromagnetic valve 108b, the electromagnetic valve 108d, and the electromagnetic valve 108e are opened in the first branch portion 110.

  A low-temperature and low-pressure gaseous refrigerant is compressed by the compressor 101 and discharged as a high-temperature and high-pressure refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 101 passes through the four-way valve 102, flows through the third connection pipe 72 and the second extension pipe 107 through the check valve 120, and the gas-liquid separator of the relay machine B 112 to the first branching unit 110. In the first branch 110, the gaseous refrigerant flows through the first extension pipe 106c and the first extension pipe 106d through the electromagnetic valve 108a and the electromagnetic valve 108d that are controlled to be in the open state.

  This gaseous refrigerant flows into the indoor unit C and the indoor unit D to be heated, and dissipates heat to the use side heat medium such as air or water by the use side heat exchanger 105c and the use side heat exchanger 105d. Condensed and liquefied to become a high-pressure liquid refrigerant. The refrigerant that has flowed out of the use side heat exchanger 105c and the use side heat exchanger 105d is further controlled by the degree of supercooling at the outlets of the use side heat exchanger 105c and the use side heat exchanger 105d. And the first flow rate regulator 109d, the pressure is slightly reduced to an intermediate pressure between the high pressure and the low pressure (intermediate pressure), and flows into the second branch portion 111 via the second extension pipe 107c and the second extension pipe 107d. .

  The refrigerant that has flowed into the second branch portion 111 flows into the indoor unit E that is going to be cooled through the second extension pipe 107e. The refrigerant that has flowed into the indoor unit E is depressurized to a low pressure by the first flow rate regulator 109e that is controlled by the degree of superheat at the outlet of the use side heat exchanger 105e, and then flows into the use side heat exchanger 105e. The refrigerant flowing into the use side heat exchanger 105e is evaporated and gasified by absorbing heat from the use side heat medium such as air or water. The gasified refrigerant flows through the first extension pipe 106e and flows into the first branch part 110. The refrigerant flowing into the first branch part 110 flows through the electromagnetic valve 108e that is controlled to open, exits the first branch part 110, and flows into the first extension pipe 106.

  A part of the refrigerant that flows out of the indoor unit C and the indoor unit D, flows into the second branch portion 111, and merges flows into the indoor unit E. On the other hand, the remaining other refrigerant that flows out of the indoor unit C and the indoor unit D, flows into the second branch portion 111, and merges flows into the bypass pipe 114. The refrigerant flowing into the bypass pipe 114 is depressurized to a low pressure by the third flow rate regulator 115 that is controlled so as to make the difference between the high pressure and the intermediate pressure constant. At this time, the refrigerant becomes a gas-liquid two-phase refrigerant, and the indoor unit E The refrigerant flowing out from the refrigerant flows into the first extension pipe 106 after joining.

  Thereafter, the refrigerant flows through the fourth connection pipe 73 via the check valve 121 and the first connection pipe 70 via the check valve 125, and the gas-liquid two-phase refrigerant in the refrigerant distributor 51 reaches a predetermined dryness. Are distributed evenly and flow into the heat source device side heat exchanger 103a, the heat source device side heat exchanger 103b, and the heat source device side heat exchanger 103c, respectively. At this time, if the refrigerant is biased to the refrigerant distributor 51, the heat source apparatus side heat exchanger 103 cannot evaporate, and the liquid is returned to the compressor 101 via the accumulator 104, resulting in the worst compressor damage. This gas-liquid two-phase refrigerant evaporates and gasifies while absorbing heat from a heat medium such as air or water in the heat source apparatus side heat exchanger 103. At this time, the switching valve 60a, the switching valve 60b, and the switching valve 60c are appropriately opened and closed to maintain a predetermined low pressure. Then, the air passes through the second connection pipe 71 via the check valve 126 and is again sucked into the compressor 101 via the four-way valve 102 and the accumulator 104. At this time, since the first extension pipe 106 has a low pressure and the second connection pipe 107 has a high pressure, the refrigerant inevitably flows to the check valve 120 and the check valve 121.

  As described above, in the air conditioning apparatus 100, by providing the refrigerant distributor 51 according to Embodiment 2, it is possible to easily control the predetermined high pressure and low pressure while suppressing the bias of the refrigerant. Also, by realizing such a refrigeration cycle, liquid back to the compressor 101 can be suppressed, stable quality can be maintained, and sufficient performance can be exhibited. That is, since the refrigerant distributor 51 is provided, the fluid can be distributed with high accuracy and uniformity with a simple structure, and the adjustment of the flow rate of the refrigerant flowing out can be easily realized.

  In this way, the refrigerant distributor 51 in which the distributor and the switching valve are integrated is incorporated into the air conditioner 100 that is a refrigeration cycle apparatus, and gas-liquid two-phase refrigerant is supplied to a plurality of evaporators (heat source side heat exchanger 103). In the case of distribution, since the amount of liquid distributed to each evaporator can be controlled, the pressure loss can be reduced at a high flow rate, and the manufacturing cost can be reduced while maintaining the performance of the entire refrigeration cycle. Further, with the simplification of the structure, the refrigerant distributor 51 can realize a reduction in processing man-hours and a reduction in size and weight.

  In the third embodiment, the cooling main operation mode and the heating main operation mode have been described. However, the same effect can be obtained in the cooling only mode and the heating only mode. Further, it goes without saying that the same effect can be obtained even if an ice heat storage tank or a water heat storage tank (including hot water) is installed in series or in parallel with the heat source device side heat exchanger 103. Moreover, although the case where the refrigerant | coolant which dissipates heat while liquefying with a condenser was used was demonstrated to the example, it is not limited to this, The refrigerant | coolant (for example, one of natural refrigerant | coolants) which dissipates heat while reducing temperature in a supercritical state Even if carbon dioxide or the like is used as a refrigerant, the same effect can be obtained. When such a refrigerant is used, the above-described condenser operates as a radiator.

  1 body, 1a body, 2 inflow part, 3 outflow part, 3a outflow part, 3b outflow part, 3c outflow part, 4 valve body mounting hole, 5 branch space part, 5a distribution hole, 5b distribution hole, 5c distribution hole, 6 Cross-sectional area of flow path, 6a cross-sectional area, 6b cross-sectional area, 6c cross-sectional area, 7 main valve chamber, 8 valve seat, 9 lid, 10 external opening, 11 main valve, 12 holes, 13 communication port, 13a communication port, 14 sub valve chamber, 15 electromagnetic coil, 16 lid port, 17 pilot hole, 18 sub valve, 19 communication port, 20 body port, 21 space, 21c space, 22 spring, 23 case, 24 ring, 25 space, 26 space, 27 Space, 50 Refrigerant distributor, 51 Refrigerant distributor, 60 switching valve, 60a switching valve, 60b switching valve, 60c switching valve, 70 1st connection piping, 71 1st 2 connection piping, 72 3rd connection piping, 73 4th connection piping, 100 air conditioner, 101 compressor, 102 four-way valve, 103 heat source side heat exchanger, 103a heat source side heat exchanger, 103b heat source side heat Exchanger, 103c Heat source side heat exchanger, 104 Accumulator, 105 User side heat exchanger, 105c User side heat exchanger, 105d User side heat exchanger, 105e User side heat exchanger, 106 First extension pipe, 106c First extension pipe, 106d First extension pipe, 106e First extension pipe, 107 Second extension pipe, 107c Second extension pipe, 107d Second extension pipe, 107e Second extension pipe, 108 solenoid valve, 108a solenoid valve, 108b Solenoid valve, 108c Solenoid valve, 108d Solenoid valve, 108e Solenoid valve, 108f Solenoid valve, 109 First flow regulator, 109 1st flow regulator, 109d 1st flow regulator, 109e 1st flow regulator, 110 1st branch part, 111 2nd branch part, 112 Gas-liquid separator, 113 2nd flow regulator, 114 Bypass piping, 115 3rd flow regulator, 116 2nd heat exchanger, 117 1st heat exchanger, 118 check valve, 119 check valve, 120 check valve, 121 check valve, 123a check valve, 123b check valve, 125 check valve, 126 check valve, A heat source machine, B relay machine, C indoor unit, D indoor unit, E indoor unit.

Claims (6)

A compressor, a refrigerant distributor, a plurality of heat source machine side heat exchangers, a flow rate regulator, and a refrigeration cycle in which a use side heat exchanger is connected by piping;
The refrigerant distributor is
Has a box-like shape,
An inflow portion for allowing the gas-liquid two-phase refrigerant to flow into the main body from below in the vertical direction;
A branch space for spreading the gas-liquid two-phase refrigerant flowing from the inflow portion;
A plurality of portions that are formed so as to open radially around the branch space portion at equal angles from the center of the cross section in the refrigerant inflow direction of the branch space portion and distribute the refrigerant spread in the branch space portion. Distribution holes,
A plurality of outflow portions that communicate with each of the distribution holes and allow the gas-liquid two-phase refrigerant to flow out of the main body;
Each of the plurality of outflow portions is connected to each of the plurality of heat source unit side heat exchangers. An air conditioner. The refrigerant distributor is
2. The air conditioner according to claim 1, wherein a distribution amount is variable depending on a ratio of flow path cross-sectional areas opened in the branch space portions of the plurality of distribution holes. In the refrigerant distributor,
The air conditioner according to claim 1 or 2, wherein a switching valve for individually communicating the plurality of distribution holes is provided according to the number of the plurality of distribution holes. The bypass pipe which bypasses a part of gas-liquid two-phase refrigerant | coolant which flowed into the said main body is attached to at least 1 of these some distribution holes. The air conditioning apparatus described in 1. In what mounts the refrigerant distributor in a heat source machine,
The refrigerant distributor is
The air conditioner according to any one of claims 1 to 4, wherein the air conditioner is disposed above the heat source unit with the inflow portion of the refrigerant distributor as a lower surface. The air conditioner according to claim 5, wherein the surface on which the inflow portion is formed and the surface on which the outflow portion is formed are arranged so as to have an angle of approximately 90 °.

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