TW201945671A - Air conditioner characterized in reducing heat loss of a four-way valve and improving COP by heating a gas-liquid two-phase refrigerant flowing out of an evaporator to a gas single phase before reaching the four-way valve - Google Patents

Abstract

Provided is an air conditioner which can reduce heat loss of a four-way valve and improve COP by heating a gas-liquid two-phase refrigerant flowing out of an evaporator to a gas single phase before reaching the four-way valve. A compressor (101), an indoor heat exchanger (111), a main expansion valve (104), an outdoor heat exchanger (103) and a four-way valve (102) are connected by pipes allowing a refrigerant to flow therein so as to constitute a refrigeration cycle. A first flow path (A) between an outlet of the indoor heat exchanger (111) and an inlet of the outdoor heat exchanger (103), and a second flow path (B) between an outlet of the outdoor heat exchanger (103) and an inlet of the four-way valve (102) are provided. The main expansion valve (104) is disposed in the first flow path (A) and provided with a heating part (40) for heating the refrigerant flowing in the second flow path (B) by the refrigerant which flows between the outlet of the indoor heat exchanger (111) in the first flow path (A) and an inlet of the main expansion valve (104).

Description

Air conditioner

The present invention relates to an air conditioner.

The air conditioner is a device that absorbs heat from outside the building during a heating operation that heats the inside of the building and releases heat to the outside of the building during a cooling operation that cools the inside of the building. Therefore, the air conditioner includes a heat exchanger for exchanging heat between the air and the refrigerant, a blower for generating air flow, a compression device for compressing the refrigerant to high temperature and high pressure, and expansion for decompressing the refrigerant Device.

As a method of improving the stability of the operation of an air-conditioning apparatus, there is a method of vaporizing a refrigerant at an outlet of an evaporator and flowing the refrigerant into a compressor. However, in this case, since the heat transfer surface becomes a gas phase region near the exit of the evaporator, there is a problem that the cooling capacity becomes low.

In response to the above-mentioned problem, in Patent Document 1, the refrigerant at the outlet of the evaporator is heated by the refrigerant at the outlet of the condenser to vaporize the refrigerant flowing into the compressor and simultaneously reduce the dryness of the refrigerant at the outlet of the evaporator. Increase cooling capacity. Further, in Patent Document 2, the refrigerant flowing out of the condenser is divided into two paths A and B, and after the pressure of the path A is reduced, it is evaporated by heat exchange with the path B, and It is combined with the refrigerant B in the path B flowing out from the evaporator in a gas-liquid two-phase state, thereby increasing the cooling capacity at the evaporator and vaporizing the suction refrigerant of the compressor. [Prior Art Literature] [Patent Literature]

[Patent Document 1] Japanese Patent Laid-Open No. 9-60989 [Patent Document 2] Japanese Patent Laid-Open No. 2002-156161

[Problems to be Solved by the Invention]

As mentioned above, the air conditioner operates in two modes: air-conditioning and heating. Therefore, it is equipped with a four-way valve that switches one of the condensers and the other of the evaporators in response to the functions of the two heat exchangers of the refrigeration cycle. At the four-way valve, heat exchange occurs because the high-temperature and high-pressure refrigerant flowing from the compressor and the low-temperature and low-pressure refrigerant flowing from the evaporator circulate next to each other. Because of this, since the high-temperature refrigerant is cooled by the low-temperature refrigerant, there is a loss in cycle performance.

When considering the application of the prior art to a refrigeration cycle where a four-way valve is present, in order to easily obtain the effect on both the air conditioner and the air heater, it is between the outlet of the four-way valve and the compressor suction port. Set the area where the refrigerant will be heated. However, in this case, since the low-temperature refrigerant system flowing through the four-way valve becomes a gas-liquid two-phase flow, the system becomes heat conduction accompanied by evaporation, and the heat conductivity becomes high. That is, the heat loss is increased due to the gas-liquid two-phase flow flowing through the four-way valve. Therefore, in order to increase the COP of the refrigeration cycle, it is necessary to set the outlet of the evaporator to a gas-liquid two-phase and also to set the low-pressure refrigerant flowing into the four-way valve to a gas-phase single-phase state.

Therefore, the object of the present invention is to provide a gas-liquid two-phase refrigerant flowing from an evaporator, which is heated to a single-phase gas phase before reaching the four-way valve, thereby reducing the heat loss of the four-way valve and Air conditioner capable of raising COP. [Means to solve the problem]

In order to achieve the above-mentioned problem, an air conditioner according to one aspect of the present invention is characterized in that a compressor, a condenser, an expansion valve, an evaporator, and a four-way valve are connected by pipes for flowing refrigerant. It forms a refrigeration cycle and has a first flow path between the outlet of the condenser and the inlet of the evaporator, and a second flow path between the outlet of the evaporator and the inlet of the four-way valve. The valve is disposed at the first flow path, and includes a refrigerant flowing through the second flow path through an outlet of the condenser in the first flow path and an inlet of the expansion valve. A heating section that heats the refrigerant flowing from time to time. [Effect of the invention]

According to the present invention, it is possible to provide a gas-liquid two-phase refrigerant flowing from an evaporator to a single-phase gas phase before it reaches the four-way valve, thereby reducing the heat loss of the four-way valve and enabling the Air conditioner that raises COP.

Hereinafter, embodiments of the present invention will be described based on the drawings. <First Embodiment> The air-conditioning apparatus 200 according to the first embodiment of the present invention will be described with reference to Figs. 1 to 4.

FIG. 1 is a diagram showing the structure of a refrigeration cycle of an air-conditioning apparatus 200 according to the first embodiment.空调 The air conditioner 200 shown in FIG. 1 is a household room air conditioner. The air-conditioning apparatus 200 is provided with an indoor unit 110 for temperature adjustment in a building, an outdoor unit 100 for receiving and releasing heat from air outside the building, and a liquid phase connecting the indoor unit 110 and the outdoor unit 100 The side connection pipe 113 and the gas phase side connection pipe 114. An indoor heat exchanger 111 and a cross-flow fan 112 are installed inside the indoor unit 110. Inside the outdoor unit 100, a compressor 101, a four-way valve 102, an outdoor heat exchanger 103, a propeller fan 105, a main expansion valve 104, a sub-expansion valve 3, and a first heat exchange are provided. Department 4.

This system passes the compressor 101, the four-way valve 102, the gas-phase connection pipe 114, the indoor heat exchanger 111, the liquid-phase connection pipe 113, the first heat exchange unit 4, and the main expansion valve 104. It is diverted between the main expansion valve 104 and the outdoor heat exchanger 103 via the main flow path 1 of the outdoor heat exchanger 103, and exchanges heat with the outdoor at the four-way valve 102 via the auxiliary expansion valve 3 and the first heat exchange unit 4. The secondary flow path 2 meeting between the devices 103 is constituted. The entire flow path is a closed circuit without an open portion. Inside the flow path, R32 refrigerant is enclosed. The refrigerant system may be other refrigerants such as R410a.

The valve body 26 of the four-way valve 102 can be moved in the left-right direction in FIG. 1 according to the operation setting. Specifically, in FIG. 1, the discharge pipe 20 and the indoor unit side pipe 22 and the suction pipe 21 and the outdoor unit side pipe 23 are connected to each other. However, the position of the valve body 26 is set as The switching can be performed in a state where the discharge pipe 20 and the outdoor unit side pipe 23 and the suction pipe 21 and the indoor unit side pipe 22 are in communication with each other.

The main expansion valve 104 and the auxiliary expansion valve 3 are electromagnetic expansion valves, respectively, and the opening degree of the flow path can be adjusted from fully closed to fully open by a control device other than the illustration. In addition, since the sub-expansion valve 3 needs to be capable of opening and closing the flow path as a minimum function, it is also possible to substitute an electromagnetic valve or the like.

The indoor heat exchanger 111 and the outdoor heat exchanger 103 are forms for exchanging heat between air and a refrigerant. Specifically, it is a fin-tube type heat exchanger which comprises the structure which penetrates the heat-conducting pipe which circulates a refrigerant | coolant to the fin which becomes a heat conduction surface of air.

The first heat exchanging part 4 makes partial contact between the flow path between the indoor heat exchanger 111 and the main expansion valve 104 and the flow path from the sub-expansion valve 3 to the flow path meeting point 5. The construction. Therefore, the first heat exchange unit 4 functions as a subcooling heat exchanger.

The flow path between the outlet of the indoor heat exchanger 111 and the inlet of the outdoor heat exchanger 103 is the first flow path A. The main flow path 1 forms part of the first flow path A. The flow path between the outlet of the outdoor heat exchanger 103 and the inlet of the four-way valve 102 is a second flow path B. The flow path branched from the flow path between the main expansion valve 104 and the inlet of the outdoor heat exchanger 103 in the first flow path A and connected to the second flow path B is the third flow path C The secondary flow path 2 corresponds to the third flow path C.

The air-conditioning apparatus 200 according to the first embodiment will be described with reference to the operation of the refrigeration cycle. In the air-conditioning apparatus 200 shown in FIG. 1, the connection relationship during heating operation is shown. The refrigerant that has been compressed into a high-temperature and high-pressure gas phase at the compressor 101 passes through the four-way valve 102 and flows into the indoor heat exchanger 111. At the indoor heat exchanger 111, the refrigerant system emits heat toward the air flow generated by the cross-flow fan 112, and the air system in the building is heated. At this time, the refrigerant system is changed to a liquid single-phase state through a gas-liquid two-phase state due to being cooled. The refrigerant whose heat release is completed at the indoor heat exchanger 111 is returned to the outdoor unit 100, cooled at the first heat exchange section 4, and then decompressed to the outside by passing through the main expansion valve 104. Gas-liquid two-phase state below air temperature.

The decompressed refrigerant is divided into the main flow path 1 and the sub flow path 2. The refrigerant in the main flow path 1 flows into the outdoor heat exchanger 103 and evaporates due to receiving heat from the air flow generated by the propeller fan 105. The refrigerant in the secondary flow path 2 is heated by the first heat exchange section 4 and meets with the refrigerant in the main flow path 1 at the flow path meeting point 5. In addition, the refrigerant flow rate ratio between the main flow path 1 and the auxiliary flow path 2 is adjusted by the opening degree of the auxiliary expansion valve 3. The refrigerant flow ratio of the main flow path 1 and the sub flow path 2 is, for example, 1: 95% of the main flow path and 2: 5% of the sub flow path. The combined refrigerant is returned to the suction side of the compressor 101 after passing through the four-way valve 102. With this closed cycle, the heating of the air in the building is continued.

In the case of air-conditioning operation, the valve body 26 is laterally moved to the right in FIG. 1, and the sub-expansion valve 3 is fully closed. As a result, since the refrigerant flows in a flow direction opposite to the heating operation, heat is released in the outdoor heat exchanger 103 and heat is received in the indoor heat exchanger 111, so the air system in the building is cooled. In the case of air-conditioning operation, since the auxiliary expansion valve 3 is fully closed, the refrigerant system of the auxiliary flow path 2 does not flow.

In order to explain the effect of the air-conditioning apparatus 200 according to the first embodiment, differences from the prior art will be described. As shown in FIG. 2, the structure diagram of the refrigeration cycle of the air conditioner 210 of the prior art is shown. The refrigeration cycle of the prior art is different from the air-conditioning apparatus 200 of FIG. 1 and does not include the first heat exchange unit 4, the auxiliary expansion valve 3, and the auxiliary flow path 2. In addition, since the sub-flow path 2 does not exist, there is no flow path convergence point 5 either. Therefore, in the case of heating operation, the refrigerant that has flowed out of the main expansion valve 104 receives heat from the outside air at the outdoor heat exchanger 103, and then flows in the order of the four-way valve 102 and the compressor 101.

FIG. 3 is a schematic diagram showing the relationship between the dryness of the refrigerant and the thermal conductivity when the outdoor heat exchanger 103 is used as an evaporator. During the evaporation process, the gas-liquid two-phase refrigerant increases the dryness from the inlet to the outlet. If it goes further downstream, the proportion of the gas phase area increases. At this time, the thermal conductivity of the refrigerant decreases sharply above the threshold x of the dryness. This is because, because the threshold value x is used as a boundary, the refrigerant flow behavior changes from a circular flow that is a liquid phase at the wall surface of the heat pipe and a gas phase at the center of the heat pipe to a gas phase. The flow of the liquid phase is distributed in the flow, and because of this, the evaporation of the refrigerant at the wall surface of the heat pipe becomes difficult to occur. In addition, the threshold value x does not have a fixed value because it varies depending on the shape of the groove on the inner surface of the heat transfer tube, but generally, the dryness is 0.9 to 1.0.

If the thermal conductivity of the refrigerant is reduced, the temperature difference between the air and the refrigerant required to obtain a certain amount of heat exchange will increase. However, because the temperature of the incoming air is constant, the evaporation temperature is reduced, that is, the evaporation pressure. Department is down. Therefore, as the degree of dryness at the outlet of the outdoor heat exchanger 103 increases, the evaporation pressure will decrease due to an increase in the proportion occupied by the thermally conductive surface having a low thermal conductivity. If the evaporation pressure decreases, the theoretical compression power system increases due to the increase in the pressure difference between it and the discharge pressure, and the COP system decreases due to the increase in the input power of the compressor.

Based on the above reasons, in the prior art, in order to maximize the COP, the dryness of the outlet of the outdoor heat exchanger 103 is set to less than 1, but in this case, the four-way valve 102 The subject of heat loss.

FIG. 4 is a diagram schematically showing a flow state inside the four-way valve 102 in the prior art. In FIG. 4, the high-temperature refrigerant discharged from the compressor 101 flows from the discharge pipe 20 to the indoor unit-side pipe 22 and flows through the two phases of gas and liquid after passing through the outdoor heat exchanger 103. The refrigerant flows from the outdoor unit-side pipe 23 to the suction pipe 21 and circulates.

Since the refrigerant after flowing out of the outdoor heat exchanger 103 is a two-phase gas-liquid phase, it is in a state where the liquid-phase refrigerant 24 is distributed inside the gas-phase refrigerant 25. Here, inside the four-way valve 102, a low-temperature refrigerant is bent in the valve body 26 to cause a 180-degree bending of the flow. However, the liquid-phase refrigerant 24 having a large density has a high inertial force. Therefore, It is attached to the wall surface of the valve body 26 to form a liquid film. When a liquid film is formed on the wall surface of the valve body 26, when a heat exchange is performed with a high-temperature refrigerant through the valve body 26, the liquid film system is evaporated, so that the thermal conductivity system is high. For this reason, in the case of a gas-liquid two-phase refrigerant, the amount of heat exchange becomes larger in the case of a gas-liquid two-phase refrigerant than in the case of a gas-phase single phase.

When the amount of heat exchange between the high-temperature refrigerant and the low-temperature refrigerant increases at the four-way valve 102, the temperature of the refrigerant at the inlet of the indoor heat exchanger 111 decreases during the heating operation. Because of this, the specific enthalpy of the refrigerant at the inlet of the indoor heat exchanger 111 is reduced, so the specific enthalpy difference at the inlet and outlet of the indoor heat exchanger 111 is reduced, and the COP system is reduced due to the decrease in heating capacity.

For the above reasons, in the prior art, although the outlet of the outdoor heat exchanger 103 was set to a gas-liquid two-phase state to maintain the evaporation pressure, on the other hand, the heat exchange amount at the four-way valve 102 Because it is high, there is a loss in the heating capacity, and the COP is reduced.

On the other hand, in the air-conditioning apparatus 200 of the first embodiment, the refrigerant branched to the sub-flow path 2 is heated to the vapor phase region by the first heat exchange section 4 and then exchanged with the outflow outdoor heat. Refrigerant rendezvous of the main stream 1 behind the device 103. This makes it possible to adjust the flow rate of the auxiliary flow path 2 by using the auxiliary expansion valve 3 to set the dryness of the refrigerant in the auxiliary flow path 2 after flowing out of the first heat exchange section 4 to 1 or more. The gas-liquid two-phase refrigerant flowing out of the outdoor heat exchanger 103 is heated by the refrigerant having a dryness of 1 or more. As such, in this embodiment, the first heat exchange section 4 and the auxiliary flow path 2 (the third flow path C) function as the heating section 40 that heats the refrigerant flowing in the second flow path B. .

Therefore, by setting the refrigerant dryness at the outlet of the secondary flow path 2 side of the first heat exchange unit 4 to 1 or more, the refrigerant dryness at the outlet of the outdoor heat exchanger 103 can be set to less than 1 and the inflow The refrigerant in the four-way valve 102 is a gas phase single phase. Therefore, the thermal conductivity of the low-temperature refrigerant at the four-way valve 102 is reduced to suppress heat loss, and the COP can be improved.

With the above configuration, the air-conditioning apparatus 200 according to the first embodiment can improve the COP compared to the air-conditioning apparatus of the prior art. In addition, although the present embodiment has a configuration for the purpose of obtaining an effect in the case of heating operation, it may also be a configuration for the purpose of obtaining an effect in the case of air-conditioning operation.

<Second Embodiment> The air-conditioning apparatus 220 according to the second embodiment of the present invention will be described with reference to Figs. 5 and 6.

FIG. 5 is a diagram showing the structure of a refrigeration cycle of the air-conditioning apparatus 220 according to the second embodiment. The air-conditioning apparatus 220 according to the second embodiment is different from the air-conditioning apparatus 200 according to the first embodiment in the following configuration. That is, the air-conditioning apparatus 220 between the first heat exchange unit 4 and the flow path meeting point 5 is different. Flow path 2 (second flow path B) passes through the second heat exchange section 6 connected to the compressor 101, and is provided with a liquid-phase-side distributor 30 and a gas-phase-side distributor before and after the outdoor heat exchanger 103. 31.

The second heat exchange section 6 has a shape in which the sub-flow path 2 is in contact with the surface of the compressor 101, and the refrigerant in the sub-flow path 2 is heated by the surface of the compressor 101 having a high temperature. However, as long as the purpose can be achieved, various configurations including a heat exchanger and the like around the compressor 101 may be adopted. In this embodiment, the first heat exchange section 4, the sub flow path 2 (the third flow path C), and the second heat exchange section 6 are heating sections 41 that heat the refrigerant flowing in the second flow path B. And it works.

In the case of heating operation, the refrigerant in the main flow path 1 is branched to the plurality of flow paths at the liquid-phase-side distributor 30, evaporates at the outdoor heat exchanger 103, and then is evaporated at the gas-phase-side distributor 31. Meet together. On the other hand, in the case of air-conditioning operation, the refrigerant after flowing out of the four-way valve 102 is branched to a plurality of flow paths at the gas-phase distributor 31 and condensed at the outdoor heat exchanger 103. Meet at the liquid-phase-side distributor 30.

FIG. 6 is a schematic diagram showing a cross section of the outdoor unit 100.

The outdoor heat exchanger 103 includes a fin 32 serving as a heat conducting surface on the air side, and a flat heat transfer tube 33 having a plurality of holes in a flat cross section. The upper and lower sides of the outdoor heat exchanger 103 are closed by the frame wall surface 34 of the outdoor unit 100, and the propeller fan 105 is rotated by driving a fan motor 35 provided inside the outdoor unit 100, and the following figure is generated. Air flow to the right and left. The refrigerant is inside the flat heat transfer tube 33, and flows in the direction in front of the drawing and deep. As a result, air and the refrigerant system perform heat exchange. The flat heat transfer tubes 33 are connected to the liquid-phase-side distributor 30 and the gas-phase-side distributor 31 shown in FIG. 5, but detailed paths are omitted from the illustration.

The heat exchanger using the flat heat transfer tube 33 shown in FIG. 6 has a small cross-sectional area of the flow path. Therefore, it is necessary to divide the refrigerant flow path and use a plurality of refrigerant paths to perform heat during use. exchange. Here, when the refrigerant flow path is divided into a plurality of refrigerant passages, the difference between the pressure loss of each flow path, the head difference at the inlet and the outlet of the flow path, and the distribution of the inflow wind speed will be different in each case. In the refrigerant passage, there is a difference in the flow rate or heat exchange amount of the refrigerant. Because of this, depending on the conditions in the evaporator in which the refrigerant flow path has multiple refrigerant paths, depending on the conditions, a refrigerant path with a dryness of the refrigerant of less than 1 and a refrigerant path of 1 or more are generated at the outlet of the flow path. In the refrigerant passages having a dryness of 1 or more, the thermal conductivity of the refrigerant becomes low, but after the meeting, the dryness is obtained by integrating all the refrigerant passages. Therefore, there may be a case where the outlet of the evaporator after the convergence becomes a gas-liquid two-phase state, but a dry surface is partially generated and the thermal conductivity is reduced. That is, when the dryness distribution at the outlet of the evaporator is uneven, even if the same dryness at the outlet, the evaporation pressure may be reduced.

Next, a case where the outdoor heat exchanger 103 of the second embodiment is applied to the air-conditioning apparatus 200 of the first embodiment will be considered. In the first embodiment, since the outlet side of the outdoor heat exchanger 103 and the four-way valve 102 are heated by the refrigerant in the sub-flow path 2, the inlet of the four-way valve 102 can be set. It is a gas phase single phase and also reduces the dryness of the outlet of the outdoor heat exchanger 103. Therefore, even if there is a slight difference in the dryness of each refrigerant passage at the outlet of the outdoor heat exchanger 103, it is possible to increase the maximum amount of heating caused by the secondary flow path 2 to The decrease in evaporation pressure is suppressed.

However, when the non-uniformity of the refrigerant distribution is high, the amount of heating becomes insufficient under the configuration of the sub-flow path 2 of the first embodiment, and it may be at the outlet of the outdoor heat exchanger 103 Generates a refrigerant path with reduced thermal conductivity of the refrigerant.

In contrast, in the air-conditioning apparatus 220 of the second embodiment, the refrigerant in the sub-flow path 2 heated by the first heat exchange section 4 passes through the second heat exchange section 6 and is compressed. The machine 101 receives heat and is heated to a higher temperature. Therefore, the heating amount of the refrigerant in the second flow path B at the flow path meeting point 5 can be increased. As a result, the dryness of each refrigerant path at the outlet of the outdoor heat exchanger 103 can be improved. The tolerance of the jitter.

With the above configuration, the air-conditioning apparatus 220 of the second embodiment can provide a system capable of increasing the COP even when the refrigerant distribution system becomes uneven.

<Third Embodiment> The air-conditioning apparatus 230 according to the third embodiment of the present invention will be described with reference to Fig. 7.

FIG. 7 is a diagram showing the configuration of a refrigeration cycle of the air-conditioning apparatus 230 according to the third embodiment. The air-conditioning apparatus 230 according to the third embodiment is a sub-expansion valve 3 and a sub-flow path 2 removed from the air-conditioning apparatus 220 according to the second embodiment, and the third heat-exchange section 10 is provided instead of the first heat-exchange section 4 Freezing cycle. The outlet of the gas-phase-side distributor 31 is connected to the four-way valve 102 after passing through the first check valve 11, the third heat exchange section 10, and the fourth heat exchange section 16. The flow path from the outlet of the gas-phase-side distributor 31 through the first check valve 11, the third heat exchange section 10, and the fourth heat exchange section 16 to the inlet of the four-way valve 102 is equivalent to the first 2 流 路 B。 2 flow path B. The outdoor heat exchanger 103 is connected to the first check valve 11 and the fourth heat exchange unit 16 is connected to the four-way valve 102 via a bypass flow path 13 via a second check valve 12. . The third heat exchange section 10 is an internal heat exchanger and functions as a heating section. The configuration and function of the fourth heat exchange section 16 are the same as those of the second heat exchange section 6 and function as a heating section.

In the case of heating operation, the refrigerant flows out of the gas-phase-side distributor 31 and then flows into the third heat exchange unit 10 through the first check valve 11 and passes through the indoor heat exchanger 111 and the main expansion valve 104. The refrigerant in between is heated. Further, the refrigerant after flowing out of the third heat exchange section 10 receives heat from the compressor 101 through the fourth heat exchange section 16 and is heated. As a result, as in the second embodiment, even when the variation in the dryness of the refrigerant passages at the outlet side of the outdoor heat exchanger 103 is large, the outlet of the outdoor heat exchanger 103 can be removed. The refrigerant in each refrigerant passage on the side is in a gas-liquid two-phase state, and the refrigerant flowing into the four-way valve 102 is a gas-phase single phase. In the case of heating operation, the refrigerant system in the bypass flow path 13 does not flow due to the action of the second check valve 12.

In the case of air-conditioning operation, the refrigerant flows out of the four-way valve 102, passes through the bypass flow path 13, and flows into the gas-phase-side distributor 31. At this time, the flow to the fourth heat exchange portion 16 and the third heat exchange portion 10 is blocked by the action of the first check valve 11. Accordingly, it is possible to prevent the heating of the compressor 101 itself caused by the high-temperature refrigerant discharged from the compressor 101 or to heat the refrigerant flowing into the indoor unit 110 by the third heat exchange unit 10. Reduced cooling capacity.

With the above-mentioned structure, during heating operation, the outlet of the outdoor heat exchanger 103 can be set as a gas-liquid two-phase flow, and the heat loss of the four-way valve 102 can be reduced. During air-conditioning operation, the loss can be increased. For suppression. The above-mentioned configuration is only an example, and the effect can be obtained even when the fourth heat exchange unit 16 does not exist. In addition, in this embodiment, as a method of switching the refrigerant path between heating operation and cooling operation, although two check valves are used, even at the entrance of the bypass flow path 13 A configuration in which a convection path such as a three-way valve is directly switched can also achieve the same effect.

In addition, this embodiment is not limited to the above-mentioned embodiment. As long as it is a trader, various additions or changes can be made within the scope of this embodiment.

1‧‧‧ mainstream road

2‧‧‧ secondary stream

4‧‧‧The first heat exchange department

6‧‧‧The second heat exchange department

10‧‧‧The third heat exchange department

13‧‧‧Bypass

16‧‧‧The fourth heat exchange department

30‧‧‧ liquid side distributor

31‧‧‧Gas side distributor

33‧‧‧ flat heat pipe

40、41‧‧‧Heating section

100‧‧‧ outdoor unit

101‧‧‧compressor

102‧‧‧Four Direction Valve

103‧‧‧outdoor heat exchanger

104‧‧‧Main expansion valve

110‧‧‧ indoor unit

111‧‧‧ indoor heat exchanger

200, 220, 230‧‧‧ air conditioning units

A‧‧‧The first flow path

B‧‧‧ 2nd flow path

C‧‧‧The third flow path

[Fig. 1] Fig. 1 is a configuration diagram of a refrigerating cycle of the air-conditioning apparatus according to the first embodiment. [Fig. 2] is a structural diagram of a refrigeration cycle of an air conditioner of the prior art.图 [Figure 3] is a schematic diagram showing the relationship between the dryness of the refrigerant inside the evaporator and the thermal conductivity. [Figure 4] is a schematic diagram of the flow inside the four-way valve in the refrigeration cycle of the prior art. [Fig. 5] is a configuration diagram of a refrigeration cycle of an air-conditioning apparatus according to a second embodiment. [Fig. 6] is a schematic cross-sectional view of an outdoor unit according to a second embodiment. [Fig. 7] is a configuration diagram of a refrigeration cycle of an air-conditioning apparatus according to a third embodiment.

Claims (10)

An air-conditioning device is characterized in that: it is connected to a compressor, a condenser, an expansion valve, an evaporator, and a four-way valve through a pipe for flowing refrigerant to form a refrigeration cycle; and it is provided with an outlet of the aforementioned condenser and The first flow path between the inlet of the evaporator and the second flow path between the outlet of the evaporator and the inlet of the four-way valve, the expansion valve is disposed at the first flow path, The heating unit includes a heating unit that heats the refrigerant flowing in the second flow path through the refrigerant flowing between the outlet of the condenser in the first flow path and the inlet of the expansion valve. The air-conditioning apparatus according to item 1 of the scope of patent application, wherein the air-conditioning apparatus is provided with a branch from a flow path between the expansion valve in the first flow path and an inlet of the evaporator, and is separated from the first flow path. A third flow path connected by two flow paths includes a refrigerant flowing between the outlet of the condenser in the first flow path and the inlet of the expansion valve, and a refrigerant flowing in the third flow path. The first heat exchange section that performs heat exchange between the flowing refrigerant, the first heat exchange section and the third flow path function as the heating section that heats the refrigerant flowing in the second flow path. . The air-conditioning apparatus according to item 2 of the scope of patent application, wherein the third flow path is located closer to the second flow path than the first heat exchange part, and is provided in the third flow path. The second heat exchange unit that performs heat exchange between the medium flowing refrigerant and the compressor, and the second heat exchange unit functions as the heating unit that heats the refrigerant flowing in the second flow path. . The air-conditioning apparatus according to item 1 of the scope of patent application, wherein the air-conditioning apparatus includes a refrigerant flowing in the second flow path, an outlet of the condenser in the first flow path, and an inlet of the expansion valve. A third heat exchange unit that performs heat exchange between the refrigerants flowing between the third heat exchange unit functions as the heating unit that heats the refrigerant flowing through the second flow path. The air-conditioning apparatus described in item 4 of the scope of the patent application, wherein is located closer to the four-way valve than the third heat exchange section in the second flow path, and is provided in the second flow path. A fourth heat exchange unit that performs heat exchange between the medium flowing refrigerant and the compressor, and the fourth heat exchange unit functions as the heating unit that heats the refrigerant flowing in the second flow path. . The air-conditioning apparatus according to item 4 of the scope of patent application, wherein the air-conditioning apparatus is provided with a branch from a flow path between an outlet of the evaporator in the second flow path and an inlet of the third heat exchange section. A bypass flow path that merges with the flow path between the outlet of the third heat exchange section in the second flow path and the inlet of the four-way valve. The air-conditioning apparatus according to any one of claims 1 to 6, in which the refrigerant at the outlet of the evaporator is set to a gas-liquid two-phase state, and the aforesaid heating unit is used to change the aforesaid The inlet of the four-way valve is set to the gas phase, and a refrigeration cycle is formed. The air-conditioning apparatus according to any one of claims 1 to 7, wherein the number of divergent refrigerant flow paths in the evaporator is plural. The air-conditioning apparatus according to item 8 of the scope of patent application, wherein the refrigerant flow path at the evaporator is a shape having a plurality of holes in a slightly flat cross section. The air-conditioning apparatus according to any one of claims 1 to 9, wherein: the condenser is an indoor heat exchanger installed at an indoor unit, and the evaporator is installed at an outdoor unit Outdoor heat exchanger.