阅读说明：本技术 换热器 (Heat exchanger ) 是由 仲田升平 渡边政利 前间庆成 高冈亮 岛野太贵 冈孝多郎 于 2020-01-29 设计创作，主要内容包括：一种换热器(23),其具备将使制冷剂从外部流入的第一列的换热模块(50a)、使制冷剂向外部流出的第二列的换热模块(50b)、使制冷剂向外部流出的第三列的换热模块(50c)、以及使制冷剂从第一列的换热模块(50a)向第二列的换热模块(50b)及第三列的换热模块(50c)分流的分流模块(40),第一列的换热模块(50a)构成制冷剂的去路(50aD)、第二列的换热模块(50b)及第三列的换热模块(50c)这两者分别构成制冷剂的回路(50bU、50cU),由此制冷剂的流路形成一个往返。(A heat exchanger (23) is provided with a first row of heat exchange modules (50a) for allowing a refrigerant to flow in from the outside, a second row of heat exchange modules (50b) for allowing the refrigerant to flow out to the outside, a third row of heat exchange modules (50c) for allowing the refrigerant to flow out to the outside, and a flow dividing module (40) for dividing the refrigerant from the first row of heat exchange modules (50a) to the second row of heat exchange modules (50b) and the third row of heat exchange modules (50c), wherein the first row of heat exchange modules (50a) constitute refrigerant outgoing paths (50aD), the second row of heat exchange modules (50b) and the third row of heat exchange modules (50c) constitute refrigerant circuits (50bU, 50cU), respectively, and thereby the refrigerant flow paths form one round trip.)

1. A heat exchanger is configured by stacking in a ventilation direction: a heat exchanger including a heat exchange module in a first row for allowing a refrigerant to flow in from the outside, a heat exchange module in a second row for allowing the refrigerant to flow out to the outside, and a heat exchange module in a third row for allowing the refrigerant to flow out to the outside, and a flow-dividing module for dividing the refrigerant flowing in from the heat exchange module in the first row into the heat exchange modules in the second row and the heat exchange modules in the third row,

the heat exchange modules in the first row constitute an outgoing path of the refrigerant, and the heat exchange modules in the second row and the heat exchange modules in the third row constitute respective refrigerant circuits, so that a refrigerant flow path forms one round trip between an inlet of the heat exchanger, into which the refrigerant flows, and an outlet, from which the refrigerant flows out.

2. The heat exchanger of claim 1,

the flow dividing module divides the refrigerant so that the amount of the refrigerant flowing into the heat exchange modules of the second row on the windward side in the ventilation direction is larger than the amount of the refrigerant flowing into the heat exchange modules of the third row on the leeward side in the ventilation direction.

3. The heat exchanger of claim 2,

the flow splitting module includes a first flow splitting chamber, a second flow splitting chamber, and a third flow splitting chamber that are respectively communicated with the heat exchange modules in the first row, the heat exchange modules in the second row, and the heat exchange modules in the third row, and a diameter of a first inlet port connecting the first flow splitting chamber and the second flow splitting chamber is larger than a diameter of a second inlet port connecting the first flow splitting chamber and the third flow splitting chamber.

4. The heat exchanger of claim 3,

the flow dividing module is provided with a fourth flow dividing chamber for communicating the heat exchange modules in the first row with the heat exchange modules in the second row and a fifth flow dividing chamber for communicating the heat exchange modules in the first row with the heat exchange modules in the third row, and the diameter of a third inflow port for connecting the heat exchange modules in the first row with the third flow dividing chamber is larger than the diameter of a fourth inflow port for connecting the heat exchange modules in the first row with the fifth flow dividing chamber.

Technical Field

The present invention relates to a heat exchanger.

Background

Conventionally, there is known an outdoor unit of an air conditioner in which heat exchange modules having flat tubes are connected in three rows (see, for example, patent document 1).

As shown in fig. 8, in patent document 1, in order to achieve uniformity of the temperature of the blown air, the heat exchange modules in the first row constitute a first outward path of the refrigerant, the heat exchange modules in the second row constitute a first circuit and a second outward path in accordance with the branched refrigerant, and the heat exchange modules in the third row constitute a second circuit of the merged refrigerant. In addition, in order to shorten the length of the piping connected to the inlet pipe or the outlet pipe while saving space, the refrigerant inlet pipe connected to the heat exchange module in the first row and the refrigerant outlet pipe connected to the heat exchange module in the third row are drawn out from the header on the same side.

However, in the control according to the conventional art, since the flow path of the refrigerant is configured to make two reciprocations with respect to the heat exchange modules arranged in three rows, there is a problem that the flow path length becomes long and the pressure loss becomes large. In addition, a first loop and a second outgoing loop are included in the heat exchange modules of the second row. The difference in the state or temperature of the refrigerant flowing through the first circuit and the second outgoing path causes a deviation in the amount of heat exchange with air, resulting in a problem of a decrease in the heat exchange function of the heat exchanger.

Patent document 1 Japanese patent laid-open No. 2016-125671

Disclosure of Invention

The present invention has been made in view of the above problems, and an object of the present invention is to provide a heat exchanger in which even a heat exchanger in which heat exchange modules are arranged in three rows, pressure loss is suppressed, and the state of refrigerant at the outlet side of each row is made uniform.

In order to achieve the above object, the present invention can be understood as follows. (1) The first aspect of the present invention is: a heat exchanger is configured by stacking in a ventilation direction: the heat exchanger includes a first row of heat exchange modules for flowing a refrigerant from outside, a second row of heat exchange modules for flowing the refrigerant to outside, and a third row of heat exchange modules for flowing the refrigerant to outside, and a flow-dividing module for dividing the refrigerant flowing in from the first row of heat exchange modules into the second row of heat exchange modules and the third row of heat exchange modules, wherein the first row of heat exchange modules constitute a refrigerant circuit, and the second row of heat exchange modules and the third row of heat exchange modules constitute a refrigerant circuit, respectively, and a refrigerant flow path is formed between an inlet of the heat exchanger into which the refrigerant flows and an outlet of the heat exchanger from which the refrigerant flows out.

(2) In the above (1), the flow dividing module divides the refrigerant so that an amount of the refrigerant flowing into the heat exchange modules in the second row on the windward side in the ventilation direction is larger than an amount of the refrigerant flowing into the heat exchange modules in the third row on the leeward side in the ventilation direction.

(3) In the above (2), the flow dividing module includes a first flow dividing chamber communicating with the heat exchange modules in the first row, a second flow dividing chamber communicating with the heat exchange modules in the second row, and a third flow dividing chamber communicating with the heat exchange modules in the third row, and a diameter of a first inflow port connecting the first flow dividing chamber and the second flow dividing chamber is larger than a diameter of a second inflow port connecting the first flow dividing chamber and the third flow dividing chamber.

(4) In the above (3), the flow dividing module includes a fourth flow dividing chamber which communicates the heat exchange modules in the first row with the heat exchange modules in the second row, and a fifth flow dividing chamber which communicates the heat exchange modules in the first row with the heat exchange modules in the third row, and a diameter of a third inlet port which connects the heat exchange modules in the first row with the third flow dividing chamber is larger than a diameter of a fourth inlet port which connects the heat exchange modules in the first row with the fifth flow dividing chamber.

According to the present invention, it is possible to provide a heat exchanger in which pressure loss is suppressed even in a heat exchanger in which heat exchange modules are arranged in three rows, and the state of refrigerant in the outlet side of each row is made uniform.

Drawings

Fig. 1A is a diagram illustrating an air conditioner according to an embodiment of the present invention, and is a refrigerant circuit diagram showing a refrigerant circuit of the air conditioner.

Fig. 1B is a block diagram showing an outdoor unit control unit.

Fig. 2 is a perspective view showing a heat exchanger according to an embodiment of the present invention.

Fig. 3 is a perspective view schematically showing two reciprocating refrigerant flow paths in a three-row heat exchanger.

Fig. 4 is a perspective view schematically showing a flow path of refrigerant that reciprocates in one of the three rows of heat exchangers.

Fig. 5 is a diagram showing an embodiment of the shunt module.

Fig. 6 is a diagram showing another form of the shunt module.

Fig. 7 is a diagram showing still another embodiment of the shunt module.

Fig. 8 is a perspective view showing a three-row heat exchanger according to the prior art.

Detailed Description

Detailed description of the preferred embodiments

Embodiments of the present invention will be described in detail below with reference to the drawings. The present invention is not limited to the following embodiments, and various modifications may be made without departing from the spirit of the present invention.

Structure of refrigerant circuit

First, a refrigerant circuit of an air conditioner 1 including an outdoor unit 2 will be described with reference to fig. 1A. As shown in fig. 1A, an air conditioner 1 of the present embodiment includes an outdoor unit 2 installed outdoors, and an indoor unit 3 installed indoors and connected to the outdoor unit 2 by a liquid pipe 4 and a gas pipe 5. Specifically, the liquid-side closing valve 25 of the outdoor unit 2 and the liquid pipe connection portion 33 of the indoor unit 3 are connected by the liquid pipe 4. The gas side shutoff valve 26 of the outdoor unit 2 and the gas pipe connection 34 of the indoor unit 3 are connected by the gas pipe 5. Thereby forming the refrigerant circuit 10 of the air conditioner 1.

Refrigerant circuit of outdoor unit

First, the outdoor unit 2 will be explained. The outdoor unit 2 includes: a compressor 21, a four-way valve 22, an outdoor heat exchanger 23, an expansion valve 24, a liquid-side shutoff valve 25 to which the liquid pipe 4 is connected, a gas-side shutoff valve 26 to which the gas pipe 5 is connected, and an outdoor fan 27. These devices other than the outdoor fan 27 are connected to each other by refrigerant pipes described later, thereby forming an outdoor unit refrigerant circuit 10a constituting a part of the refrigerant circuit 10. An accumulator (not shown) may be provided at the refrigerant suction side of the compressor 21.

The compressor 21 is a variable-capacity compressor, and the operating load can be changed by controlling the rotation speed thereof by an inverter, not shown. The refrigerant discharge side of the compressor 21 is connected to a port a of the four-way valve 22 via a discharge pipe 61. The refrigerant suction side of the compressor 21 and the port c of the four-way valve 22 are connected by a suction pipe 66.

The four-way valve 22 is a valve for switching the flow direction of the refrigerant, and includes four ports a, b, c, and d. As described above, the port a is connected to the refrigerant discharge side of the compressor 21 via the discharge pipe 61. The port b is connected to one of the refrigerant inlet and outlet of the outdoor heat exchanger 23 via a refrigerant pipe 62. As described above, the port c is connected to the refrigerant suction side of the compressor 21 via the suction pipe 66. The port d and the gas-side shutoff valve 26 are connected by a refrigerant pipe 64.

The outdoor heat exchanger 23 is for exchanging heat between the refrigerant and outside air sucked into the outdoor unit 2 by rotation of an outdoor fan 27, which will be described later. As described above, one of the refrigerant inlet and outlet of the outdoor heat exchanger 23 is connected to the port b of the four-way valve 22 via the refrigerant pipe 62, and the other refrigerant inlet and outlet is connected to the liquid-side shutoff valve 25 via the refrigerant pipe 63. The outdoor heat exchanger 23 functions as a condenser during the cooling operation and as an evaporator during the heating operation by switching the four-way valve 22 described later.

The expansion valve 24 is an electronic expansion valve driven by a pulse motor, not shown. Specifically, the opening degree thereof is adjusted according to the number of pulses applied to the pulse motor. The opening degree of the expansion valve 24 is adjusted so that the temperature of the refrigerant discharged from the compressor 21 during the heating operation, that is, the discharge temperature, becomes a predetermined target temperature.

The outdoor fan 27 is formed of a resin material and is disposed in the vicinity of the outdoor heat exchanger 23. The center of the outdoor fan 27 is connected to a rotating shaft of a fan motor, not shown. The outdoor fan 27 is rotated by the fan motor rotation. By the rotation of the outdoor fan 27, outside air is sucked into the outdoor unit 2 from a suction port, not shown, of the outdoor unit 2, and outside air having exchanged heat with the refrigerant in the outdoor heat exchanger 23 is discharged to the outside of the outdoor unit 2 from a discharge port, not shown, of the outdoor unit 2.

In addition to the above-described configuration, various sensors are provided in the outdoor unit 2. As shown in fig. 1A, the discharge pipe 61 is provided with: a discharge pressure sensor 71 that detects the pressure of the refrigerant discharged from the compressor 21; and a discharge temperature sensor 73 that detects the temperature of the refrigerant discharged from the compressor 21 (the discharge temperature described above). The suction pipe 66 is provided with: a suction pressure sensor 72 that detects the pressure of the refrigerant sucked into the compressor 21; and a suction temperature sensor 74 that detects the temperature of the refrigerant sucked into the compressor 21.

A heat exchange temperature sensor 75 is provided in a substantially middle portion of the refrigerant passage, not shown, of the outdoor heat exchanger 23, and detects the temperature of the outdoor heat exchanger 23, that is, the outdoor heat exchange temperature. An outdoor air temperature sensor 76 is provided near a suction port, not shown, of the outdoor unit 2, and detects the temperature of the outdoor air flowing into the outdoor unit 2, that is, the outside air temperature.

The outdoor unit 2 includes an outdoor unit control unit 200. The outdoor unit control unit 200 is mounted on a control board housed in an electrical equipment box, not shown, of the outdoor unit 2. As shown in fig. 1B, the outdoor unit control unit 200 (in this specification, the outdoor unit control unit 200 is sometimes simply referred to as a control unit) includes a CPU210, a storage unit 220, a communication unit 230, and a sensor input unit 240.

The storage unit 220 is composed of a flash memory, and stores a control program of the outdoor unit 2, detection values corresponding to detection signals from various sensors, control states of the compressor 21, the outdoor fan 27, and the like. Although not shown, a rotation speed table in which the rotation speed of the compressor 21 is defined in accordance with the required capacity received from the indoor unit 3 is stored in the storage unit 220 in advance.

The communication unit 230 is an interface for communicating with the indoor unit 3. The sensor input unit 240 acquires detection results of various sensors of the outdoor unit 2 and outputs the detection results to the CPU 210.

The CPU210 acquires the detection results of the sensors of the outdoor unit 2 through the sensor input unit 240. Further, the CPU210 acquires the control signal transmitted from the indoor unit 3 through the communication unit 230. The CPU210 performs drive control of the compressor 21 or the outdoor fan 27 based on the acquired detection result, control signal, or the like. Further, the CPU210 performs switching control of the four-way valve 22 based on the acquired detection result or control signal. Further, the CPU210 adjusts the opening degree of the expansion valve 24 based on the acquired detection result or control signal.

Refrigerant circuit of indoor unit

Next, the indoor unit 3 will be described with reference to fig. 1A. The indoor unit 3 includes: an indoor heat exchanger 31, an indoor fan 32, a liquid pipe connection 33 to which the other end of the liquid pipe 4 is connected, and a gas pipe connection 34 to which the other end of the gas pipe 5 is connected. The devices other than the indoor fan 32 are connected to each other by refrigerant pipes described in detail below, thereby forming an indoor unit refrigerant circuit 10b that constitutes a part of the refrigerant circuit 10.

The indoor heat exchanger 31 is for exchanging heat between the refrigerant and indoor air sucked into the indoor unit 3 from an unillustrated suction port of the indoor unit 3 by rotation of an indoor fan 32 described later. One of the refrigerant inlet and outlet of the indoor heat exchanger 31 is connected to the liquid pipe connection portion 33 via an indoor unit liquid pipe 67. The other refrigerant inlet and outlet of the indoor heat exchanger 31 is connected to the gas pipe connection 34 via an indoor unit gas pipe 68. The indoor heat exchanger 31 functions as an evaporator when the indoor unit 3 performs a cooling operation, and functions as a condenser when the indoor unit 3 performs a heating operation.

The indoor fan 32 is formed of a resin material and is disposed in the vicinity of the indoor heat exchanger 31. The indoor fan 32 sucks indoor air into the indoor unit 3 from an unillustrated suction port of the indoor unit 3 by rotation of an unillustrated fan motor, and blows out the indoor air heat-exchanged with the refrigerant in the indoor heat exchanger 31 into the room from an unillustrated discharge port of the indoor unit 3.

In addition to the above-described configuration, various sensors are provided in the indoor unit 3. The indoor-unit liquid pipe 67 is provided with a liquid-side temperature sensor 77 that detects the temperature of the refrigerant flowing into the indoor heat exchanger 31 or flowing out from the indoor heat exchanger 31. The indoor unit gas pipe 68 is provided with a gas side temperature sensor 78 that detects the temperature of the refrigerant flowing out of the indoor heat exchanger 31 or flowing into the indoor heat exchanger 31. An indoor temperature sensor 79 is provided near an unillustrated inlet of the indoor unit 3, and detects the temperature of the indoor air flowing into the indoor unit 3, that is, the indoor temperature.

Operation of refrigerant circuit

Next, referring to fig. 1A, the flow of the refrigerant and the operation of each component in the refrigerant circuit 10 during air-conditioning operation of the air conditioner 1 according to the present embodiment will be described. Hereinafter, a case where the indoor unit 3 performs the heating operation based on the flow of the refrigerant shown by the solid line in the drawing will be described. In addition, the flow of the refrigerant shown by the dotted line indicates the cooling operation.

When the indoor unit 3 performs a heating operation, the CPU210 switches the four-way valve 22 so that the state indicated by the solid line shown in fig. 1A is achieved, that is, the port a and the port d of the four-way valve 22 communicate with each other, and the port b and the port c communicate with each other. Thereby, the refrigerant circulates in the direction indicated by the solid arrows in the refrigerant circuit 10, thereby forming a heating cycle in which the outdoor heat exchanger 23 serves as an evaporator and the indoor heat exchanger 31 serves as a condenser.

The high-pressure refrigerant discharged from the compressor 21 flows through the discharge pipe 61 and into the four-way valve 22. The refrigerant flowing into the port a of the four-way valve 22 flows from the port d of the four-way valve 22 through the refrigerant pipe 64, and flows into the gas pipe 5 via the gas side closing valve 26. The refrigerant flowing through the gas pipe 5 flows into the indoor unit 3 via the gas pipe connection 34.

The refrigerant flowing into the indoor unit 3 flows through the indoor unit gas pipe 68 and into the indoor heat exchanger 31, and is subjected to heat exchange with the indoor air drawn into the indoor unit 3 by the rotation of the indoor fan 32, thereby being condensed. As described above, the indoor heat exchanger 31 is used as a condenser, and the indoor air having exchanged heat with the refrigerant in the indoor heat exchanger 31 is blown out from the air outlet not shown into the room, whereby the room in which the indoor unit 3 is installed is heated.

The refrigerant flowing out of the indoor heat exchanger 31 flows through the indoor unit liquid pipe 67, and flows into the liquid pipe 4 via the liquid pipe connection part 33. The refrigerant flowing through the liquid pipe 4 and flowing into the outdoor unit 2 via the liquid side closing valve 25 flows through the refrigerant pipe 63 and is decompressed while passing through the expansion valve 24. As described above, the opening degree of the expansion valve 24 during the heating operation is adjusted so that the discharge temperature of the compressor 21 becomes the predetermined target temperature.

The refrigerant passing through the expansion valve 24 and flowing into the outdoor heat exchanger 23 exchanges heat with the outdoor air sucked into the outdoor unit 2 by the rotation of the outdoor fan 27, thereby evaporating the outdoor air. The refrigerant flowing out of the outdoor heat exchanger 23 to the refrigerant pipe 62 flows through the ports b and c of the four-way valve 22 and the suction pipe 66, is sucked into the compressor 21, and is compressed again.

Heat exchanger and flow path of refrigerant

In the outdoor heat exchanger 23 according to the present embodiment (hereinafter, referred to as the heat exchanger 23), the heat exchange modules 50 including flat tubes (heat transfer tubes) are arranged in three rows.

Next, the heat exchanger 23 and the flow path of the refrigerant inside the heat exchanger will be described in comparison with a conventional heat exchanger with reference to fig. 2 to 8.

First, a conventional heat exchanger 23 will be described with reference to fig. 8. As shown in fig. 8, the heat exchanger 23 includes three rows of heat exchange modules 50(50a, 50b, 50 c). Upper headers 81(81a, 81b, 81c) and lower headers 82(82a, 82b, 82c) are provided at both ends of each row. A refrigerant pipe 63 (hereinafter, referred to as an inlet pipe 63) into which the refrigerant flows from the outside is connected to the first upper header 81c, and a refrigerant pipe 62 (hereinafter, referred to as an outlet pipe 62) through which the refrigerant flows out to the outside is provided to the third upper header 81 a. The upwind side in the ventilation direction is set to the heat exchange module 50a side of the first row. On the leeward side of the first row of heat exchange modules 50a, the second row of heat exchange modules 50b is in turn juxtaposed to the third row of heat exchange modules 50 c. The suffix "a", b, and c "is given in the order of the two viewed from the windward side in the ventilation direction.

Fig. 7 schematically shows a flow path of the refrigerant in the conventional heat exchanger 23 of fig. 8 (the headers 81 and 82 at both ends in fig. 8 are omitted). That is, the refrigerant flowing from the inlet pipe 63 into the heat exchange module 50c of the third row flows through the first outward route 50cD from the first upper header 81c toward the first lower header 82 c. The refrigerant flowing into the first lower header 82c flows into the second lower header 82b, and then flows through the first circuit 50bU disposed in the center of the heat exchange module 50b in the second row toward the second upper header 81 b. The refrigerant branched by the second upper header 81b flows through the second outward route 50bD disposed on both sides of the first circuit 50bU of the heat exchange module 50b in the second row toward the second lower header 82 b. The refrigerant merged in the third lower header 82a flows through the second circuit 50aU in the heat exchange module 50a in the first row toward the third upper header 81a, and flows out from the third upper header 81a to the outside via the outlet pipe 62.

As described above, by branching the refrigerant in the interior of the heat exchange module 50b in the second row, that is, in one heat exchange module 50, the flow path of the refrigerant existing in the heat exchanger 23 is formed to two round trips in the entire heat exchange modules 50c, 50b, and 50a in the three rows. Therefore, the number of refrigerant turns increases, and the pressure loss cannot be reduced.

Therefore, in the heat exchanger 23 according to the present embodiment, the pressure loss is reduced by one round trip between the inlet through which the refrigerant of the heat exchanger 23 flows and the outlet through which the refrigerant flows out in the entire three rows of the heat exchange modules 50c, 50b, and 50a by the flow dividing module 40 described later. First, the heat exchanger 23 according to the present embodiment will be described with reference to fig. 2. The same reference numerals are given to the same structure as that of the conventional heat exchanger 23 in fig. 8. As shown in fig. 2, in the heat exchanger 23, three rows of heat exchange modules 50(50a, 50b, 50c) are arranged in a stacked manner in the ventilation direction. The far side headers 83(83a, 83b, 83c) and the near side headers 84 (the flow dividing modules 40 described later) are provided at both ends of each row. An inlet pipe 63 through which the refrigerant flows from the outside is connected to the first distal header 83a, and outlet pipes 62 through which the refrigerant flows out to the outside are provided to the second distal header 83b and the third distal header 83 c. The upwind side in the ventilation direction is set to the heat exchange module 50a side of the first row. The suffix "a", b, and c "is given in the order of the two viewed from the windward side in the ventilation direction.

In the heat exchanger 23 of the present embodiment, as shown in fig. 3 (the headers 83 and 84 at both ends are omitted, and refer to fig. 2), the refrigerant flows through the heat exchange modules 50a, 50b, and 50c arranged in three rows one by one. That is, the refrigerant flowing into the heat exchange module 50a of the first row from the inlet pipe 63 flows through the outward route 50aD from the first far-side header 83a toward the near side. The refrigerant branched by the later-described branching module 40 in the near-side header 84 flows through the first circuit 50bU corresponding to the heat exchange module 50b of the second row toward the second far-side header 83b, and flows through the second circuit 50cU corresponding to the heat exchange module 50c of the third row toward the third far-side header 83 c. The former flows out from the second distal header 83b to the outside via the outlet pipe 62, and the latter flows out from the third distal header 83c to the outside via the other outlet pipe 62.

As described above, by branching the refrigerant between the heat exchange module 50a in the first row, the heat exchange module 50b in the second row, and the heat exchange module 50c in the third row, the flow path of the refrigerant according to the present embodiment in the heat exchanger 23 is formed to make one round trip in the entire heat exchange modules 50a, 50b, and 50c in the three rows. Therefore, the number of turns of the refrigerant is reduced, and the flow path length is shortened, so that the pressure loss can be suppressed.

In addition, when the refrigerant is made to flow in one round trip, the length of the flow path is shortened, but the amount of heat exchange is not reduced, as compared with the conventional two round trips. This is because, compared to the prior art in which the refrigerant is branched by the heat exchange modules 50 in one row, the flow velocity of the refrigerant is reduced by causing the refrigerant to flow in parallel in the heat exchange modules 50 in two rows as a circuit, and therefore, the time for the refrigerant to contact the air, that is, the time for the refrigerant to flow in the flat tubes (heat transfer tubes) is the same as that in the prior art, and does not affect the amount of heat exchange.

Shunting module

Next, a method of branching the refrigerant in the near-side header 84 and turning it back with respect to the heat exchange modules 50b and 50c of the two rows as the circuit will be described. When the number of rows of the heat exchange modules 50 is three in order to increase the amount of heat exchange, the temperatures of the air passing through the heat exchange modules 50b in the second row and the heat exchange modules 50c in the third row, which are arranged in parallel, are different. Specifically, the air having passed through the heat exchange module 50b of the second row passes through the heat exchange module 50c of the third row located on the downwind side in the ventilation direction. Therefore, the temperature difference between the air and the refrigerant becomes smaller in the heat exchange module 50c of the third row, thereby generating a difference in the amount of heat exchange.

When the same amount of refrigerant is made to flow through the heat exchange modules 50b in the second row and the heat exchange modules 50c in the third row, which have different heat exchange amounts, the states of the refrigerant on the outlet sides of the two heat exchange modules are deviated. Hereinafter, the case where the present heat exchanger 23 is used as a condenser will be described as an example. The refrigerant flowing through the heat exchange module 50b in the second row located on the windward side has a large temperature difference with the air, so that the heat exchange amount increases, and the supercooling degree of the refrigerant on the outlet side increases. On the other hand, the refrigerant flowing through the heat exchange module 50c in the third row located on the leeward side exchanges heat with the air having passed through the heat exchange module 50b in the second row. That is, since the temperature difference with the air is small, the heat exchange amount becomes small, and thus the degree of supercooling of the refrigerant at the outlet side becomes small or the refrigerant becomes a gas-liquid two-phase state without being supercooled. As a result, in the heat exchange module 50b in the second row, the liquid single-phase region having a small contribution degree to the heat exchange between the refrigerant and the air becomes large, and the heat exchange function of the heat exchanger 23 is deteriorated. Therefore, in order to make the refrigerant state on the outlet side between the heat exchange module 50b in the second row and the heat exchange module 50c in the third row uniform, in the present embodiment, the flow dividing module 40 is provided in the near-side header 84, and the amount of the refrigerant distributed to flow is adjusted so as to be larger on the upstream side than on the downstream side.

Fig. 4 shows an example of the splitter module 40. The flow dividing module 40 includes a first flow dividing chamber 40a, a second flow dividing chamber 40b, and a third flow dividing chamber 40c that communicate with the heat exchange module 50a of the first example, the heat exchange module 50b of the second row, and the heat exchange module 50c of the third row, respectively. Further, the diameter W1 of the first inflow port 41 connecting the first branch chamber 40a and the second branch chamber 40b is set larger than the diameter W2 of the second inflow port 42 connecting the first branch chamber 40a and the third branch chamber 40 c. Thus, the refrigerant flowing through the outward passage 50aD is split into a larger amount of refrigerant that flows into the first circuit 50bU than into the second circuit 50 cU.

Fig. 5 shows another example of the splitter module 40. The flow dividing module 40 includes a fourth flow dividing chamber 40b2 for communicating the heat exchange module 50a in the first row with the heat exchange module 50b in the second row, and a fifth flow dividing chamber 40c2 for communicating the heat exchange module 50a in the first example with the heat exchange module 50c in the third row. The diameter W3 of the third inlet 43 connecting the heat exchange module 50a in the first row and the fourth diverging chamber 40b2 is set to be larger than the diameter W4 of the fourth inlet 44 connecting the heat exchange module 50a in the first row and the fifth diverging chamber 40c 2. Thus, the refrigerant flowing through the outward passage 50aD is split into a larger amount of refrigerant that flows into the first circuit 50bU than into the second circuit 50 cU.

In fig. 4 and 5, the flow distribution module 40 is shown as one housing, but the form is not limited thereto. For example, as schematically shown in fig. 6, first, second, and third flow-dividing chambers 40a, 40b, and 40c may be provided in the first, second, and third near-side headers 84a, 84b, and 84c corresponding to the heat exchange modules 50a, 50b, and 50c of the first, second, and third rows, respectively, and the diameter of the tube connecting the first flow-dividing chamber 40a to the second flow-dividing chamber 40b may be set larger than the diameter of the tube connecting the first flow-dividing chamber 40a to the third flow-dividing chamber 40 c.

Description of the symbols

1 air conditioner

2 outdoor machine

3 indoor machine

4 liquid pipe

5 gas pipe

10 refrigerant circuit

10a outdoor machine refrigerant circuit

10b indoor unit refrigerant circuit

21 compressor

22 four-way valve

23 outdoor heat exchanger

24 expansion valve

25 liquid side shut-off valve

26 gas side closing valve

27 outdoor fan

31 indoor heat exchanger

32 indoor fan

33 liquid pipe connection part

34 gas pipe connection

40 shunting module

50 heat exchange module

61 discharge pipe

62 refrigerant pipe (outlet pipe)

63 refrigerant pipe (inlet pipe)

64 refrigerant pipe

66 suction pipe

67 liquid pipe of indoor unit

68 indoor unit gas pipe

71 discharge pressure sensor

72 suction pressure sensor

73 discharge temperature sensor

74 suction temperature sensor

75 heat exchange temperature sensor

76 outside air temperature sensor

77 liquid side temperature sensor

78 gas side temperature sensor

79 indoor temperature sensor

81 upper header

82 lower header

200 outdoor unit control unit

210 CPU

220 storage part

230 communication unit

240 sensor input unit